JP6252411B2 - Hydraulic control device - Google Patents

Description

  The present invention relates to a hydraulic control device that controls the hydraulic pressure supplied to an automatic transmission.

2. Description of the Related Art Conventionally, for example, a hydraulic control apparatus that includes a mechanical pump, a solenoid valve, and a control unit (hereinafter sometimes referred to as TCU) as described below and controls the hydraulic pressure applied to a transmission element of an automatic transmission is well known. is there.
The mechanical pump is driven by an internal combustion engine to generate hydraulic pressure, and the electromagnetic valve controls the hydraulic pressure supplied by adjusting the hydraulic pressure generated by the mechanical pump and outputting it to the transmission element.

The TCU detects the state of the vehicle by various sensors, and controls various devices (including electromagnetic valves) related to the operation of the automatic transmission based on the information, and is composed of a microcomputer or the like. .
Then, the TCU obtains a command value for the hydraulic pressure to be applied to the speed change element, obtains a command value for the current to be given to the solenoid valve based on the command value for the hydraulic pressure, and gives the command value for the current to the solenoid valve, thereby providing the solenoid valve with the command value. The hydraulic pressure is adjusted. Here, the TCU obtains a command value of current based on a pressure regulation characteristic created in advance.
The pressure regulation characteristic is a correlation between the hydraulic pressure applied to the speed change element and the current applied to the solenoid valve.

  In Patent Document 1, in the initial state before shipment, the command value of the current applied to the solenoid valve is changed and the hydraulic pressure after pressure adjustment is detected to obtain necessary data and create the pressure regulation characteristics. Is disclosed. Based on this pressure regulation characteristic, the oil pressure applied to the speed change element is changed over time according to a predetermined pattern (hereinafter sometimes referred to as a hydraulic pressure pattern), thereby suppressing a so-called speed change shock. Yes.

By the way, in order to produce an accurate pressure regulation characteristic, it is necessary to acquire detected values of hydraulic pressure after pressure regulation for a plurality of current command values.
However, in this case, even if the current command value is increased or decreased due to the viscosity of the hydraulic oil, etc., and the valve opening of the solenoid valve is changed, the detected value of the hydraulic pressure is accompanied by a delay in response, and an accurate value is obtained. It may not be obtained. For this reason, when the detected value of the hydraulic pressure is accurately acquired, it is necessary to allow sufficient time after the increase / decrease of the current command value, or to increase / decrease the current command value slowly enough that no response delay occurs. . As a result, there is a problem that it takes time to acquire data for producing the pressure regulation characteristics. These problems are particularly remarkable when there are a plurality of solenoid valves, because the pressure regulating characteristics must be created for each of the plurality of solenoid valves.

JP 2001-116130 A

  The present invention has been made to solve the above-described problems, and an object of the present invention is to shorten the time spent for producing (updating) pressure regulation characteristics for a plurality of solenoid valves.

According to the present invention, the hydraulic control device includes a mechanical pump that is driven by an internal combustion engine to generate hydraulic pressure, and adjusts the hydraulic pressure generated by the mechanical pump by the electromagnetic valve and supplies the hydraulic pressure to a plurality of transmission elements of the automatic transmission. To do.
A hydraulic circuit, a solenoid valve, a control unit, another hydraulic pressure generation source, and a hydraulic pressure detection unit described below are provided.
The hydraulic circuit is formed between the mechanical pump and each transmission element, and an oil passage continuing from the mechanical pump is branched into a plurality of parts in the middle to reach each transmission element.
A plurality of solenoid valves are arranged and assembled for each oil passage after branching.
The control means has, for each solenoid valve, a pressure regulation characteristic that is a correlation between the hydraulic pressure applied to the transmission element and the current applied to the electromagnetic valve, and applies the command value of the hydraulic pressure applied to the transmission element to the pressure regulation characteristic. The command value of the current to be given to is obtained.

Another hydraulic pressure generation source can generate hydraulic pressure and supply the hydraulic pressure to the hydraulic circuit without being driven by the internal combustion engine.
The oil pressure detecting hand is arranged for each oil path after branching, and can detect the oil pressure on the output side of the solenoid valve.
Then, for each branched oil passage, when the internal combustion engine is stopped, a hydraulic pressure is generated by another hydraulic pressure generation source to apply the hydraulic pressure to the electromagnetic valve, and to provide a current command value to the electromagnetic valve to regulate the hydraulic pressure. Each of the hydraulic pressure detection means detects the detected hydraulic pressure value, and updates the pressure regulation characteristics using the current command value and the detected hydraulic pressure value.

Thereby, since each hydraulic valve has a hydraulic pressure detecting means, it is possible to acquire data for creating pressure regulation characteristics for a plurality of electromagnetic valves in parallel in time.
For this reason, the pressure regulation characteristics of the plurality of solenoid valves can be updated in parallel in time.
As a result, the time spent for updating the pressure regulation characteristics for the plurality of electromagnetic valves can be shortened.

It is a block diagram of the automatic transmission using a hydraulic control apparatus (Example). It is explanatory drawing of the update specific example of a pressure regulation characteristic (Example). It is a specific example of the curve approximation of the hydraulic pressure command value and the hydraulic pressure detection value (modified example).

  Hereinafter, modes for carrying out the invention will be described based on examples.

An automatic transmission 2 using a hydraulic control apparatus 1 according to an embodiment of the present invention is shown in FIG. An idling stop system is employed in a vehicle equipped with this automatic transmission.
Here, the idling stop system controls the internal combustion engine (not shown) to stop when the shift range is in the forward travel range and the vehicle speed is a predetermined value or less.
In this embodiment, the idling stop system includes a control that stops the internal combustion engine when the shift range is in the reverse travel range and the vehicle speed is equal to or less than a predetermined value.

The automatic transmission 2 includes a torque converter (not shown) coupled to a crankshaft (not shown) of an internal combustion engine, a planetary gear type transmission mechanism (not shown), and a gear for shifting the transmission mechanism. This is a stepped transmission including hydraulic transmission elements 5 a to 5 e and a hydraulic control device 1.
The speed change mechanism has a plurality of planetary gears (not shown), and the speed change elements 5a to 5e use the torque of the rotation elements such as the sun gear, the carrier, and the ring gear of the planetary gears as the rotation elements of the other planetary gears. Alternatively, it is transmitted to a transmission case or the like.

  The transmission elements 5a to 5e are, for example, a wet multi-plate clutch or a wet multi-plate brake. The automatic transmission 2 controls engagement and disengagement of the transmission elements 5a to 5e, and switches a power transmission path between a turbine shaft (not shown) and an output shaft (not shown) of the torque converter. Thus, any one of the plurality of shift speeds is established.

The hydraulic control device 1 includes a hydraulic pressure supply device 1 a for supplying hydraulic pressure to each member constituting the automatic transmission 2.
The hydraulic pressure supply device 1a supplies the hydraulic oil pumped from the oil pan 7 to the pistons 8 and the torque converters of the transmission elements 5a to 5e.
The hydraulic pressure supply device 1 a includes a mechanical pump 10, an electric pump 11 as “another hydraulic pressure generation source”, a line pressure control valve 12, a manual valve 13, and the like.

The mechanical pump 10 is driven as the internal combustion engine rotates. The mechanical pump 10 sucks the hydraulic oil stored in the oil pan 7 through the oil passage 14. The mechanical pump 10 pressurizes the hydraulic oil sucked from the suction port connected to the oil passage 14 in the mechanical pump 10 and discharges it to the oil passage 15 from the discharge port.
The oil passage 15 connects the discharge port of the mechanical pump 10 and the introduction port 13 a of the manual valve 13. The hydraulic oil discharged from the mechanical pump 10 passes through the oil passage 15 and is supplied to the inlet 13 a of the manual valve 13.
The check valve 16 provided in the oil passage 15 allows the flow of hydraulic oil from the mechanical pump 10 to the manual valve 13 and prohibits the flow of hydraulic oil from the manual valve 13 to the mechanical pump 10.

  The electric pump 11 is a hydraulic pressure generation source different from the mechanical pump 10 and is driven by a motor that generates hydraulic pressure without depending on the internal combustion engine and rotates when energized. The electric pump 11 sucks the hydraulic oil stored in the oil pan 7 through the oil passage 18. The electric pump 11 pressurizes the hydraulic oil sucked from the suction port connected to the oil passage 18 in the electric pump 11 and discharges the hydraulic oil to the oil passage 19 from the discharge port.

The oil passage 19 connects the discharge port of the electric pump 11 and the oil passage 15 on the manual valve 13 side from the check valve 16 of the oil passage 15. The hydraulic oil discharged from the electric pump 11 is supplied from the oil passage 19 through the oil passage 15 to the inlet 13 a of the manual valve 13.
The check valve 20 provided in the oil passage 19 allows the flow of hydraulic oil flowing from the electric pump 11 to the manual valve 13 and prohibits the flow of hydraulic oil from the manual valve 13 to the electric pump 11.

The line pressure control valve 12 is a pilot-type pressure regulating valve, and is connected to a branch path 22 that branches from the check valve 16 of the oil path 15 from the mechanical pump 10 side. The line pressure control valve 12 adjusts the line pressure that is the pressure of the hydraulic oil supplied to the manual valve 13.
The spool of the line pressure control valve 12 is based on the hydraulic pressure controlled by the solenoid valve (not shown) controlled according to the urging force of the spring, the force received from the hydraulic oil in the shunt 22, and the load of the automatic transmission 2. It moves by balancing with the force received, and opens and closes the relief port 12a.

When the hydraulic pressure discharged from the mechanical pump 10 or the electric pump 11 is higher than the target value, surplus hydraulic fluid is returned from the relief port 12a to the oil pan 7 through the oil passage 25.
The hydraulic oil discharged from the relief port 12b of the line pressure control valve 12 is supplied to a lockup circuit of the torque converter.
Further, a shunt 26 that further branches from the shunt 22 is provided, and this shunt 26 is connected to a lubricating portion that supplies hydraulic oil to each member as lubricating oil. Note that a check valve 27 is provided in the shunt 26 to suppress the backflow of hydraulic oil from the lubrication part to the shunt 22.

The select bar 30 is operated to, for example, four operation positions by the driver of the vehicle.
Here, the four operation positions are a D range for traveling forward, a P range for parking, an R range for traveling backward, and an N range for interrupting power transmission. The spool 13 b of the manual valve 13 is mechanically or electrically connected to the select bar 30 and operates according to the operation position of the select bar 30.

When the operation position of the select bar 30 is in the D range, the manual valve 13 causes the oil passage 15 and the forward oil passage 32 to communicate with each other, and the oil passage 15 and the reverse oil passage 33 are blocked. At this time, the hydraulic oil in the oil passage 15 and the oil passage 19 can be supplied to the electromagnetic valves 35b, 35c, and 35d corresponding to the forward shift elements 5b, 5c, and 5d through the forward oil passage 32.
The forward shift elements 5b, 5c, and 5d are shift elements that are supplied with hydraulic pressure through the forward oil passage 32 and are involved in the establishment of the forward shift speed.

When the operation position of the select bar 30 is in the R range, the manual valve 13 communicates the oil passage 15 and the reverse oil passage 33 and blocks the oil passage 15 and the forward oil passage 32. At this time, the hydraulic oil in the oil passage 15 and the oil passage 19 can be supplied to the electromagnetic valve 35e corresponding to the reverse transmission speed element 5e through the reverse oil passage 33.
The reverse speed change element 5 e is a speed change element to which hydraulic pressure is supplied through the reverse oil passage 33.

When the operation position of the select bar 30 is in the P range or the N range, the manual valve 13 blocks the forward oil passage 32, the reverse oil passage 33, and the oil passage 15.
Note that there is a speed change element 5a to which hydraulic oil is directly supplied from the oil passage 15 without passing through the manual valve 13, but this speed change element 5a is a wet multi-plate brake, and the operation position of the select bar 30 is in the D range. In this case, the engine brake is applied by operating in cooperation with the speed change element 5d which is a part of the forward speed change element. Then, when the operation position of the select bar 30 is in the R range, it operates in cooperation with the reverse shift element 5e to form reverse (hereinafter, this shift element 5a may be referred to as a brake shift element). ).

Electromagnetic valves 35b, 35c, 35d are provided corresponding to the forward shifting elements 5b, 5c, 5d. Which of the forward shifting elements 5b, 5c, 5d is engaged is determined for each of a plurality of forward shift speeds. An electromagnetic valve 35e is provided corresponding to the reverse speed change element 5e, and an electromagnetic valve 35a is provided corresponding to the brake speed change element 5a.
That is, electromagnetic valves 35a to 35e are provided via oil passages 40 to 44, respectively, for the plurality of speed change elements 5a to 5e.

The solenoid valves 35a to 35e are spool valve type hydraulic control valves capable of continuously changing the output hydraulic pressure. The electromagnetic valves 35a to 35e control the output hydraulic pressure by balancing the electromagnetic thrust corresponding to the given current command value and the static hydraulic pressure introduced from the output hydraulic pressure.
The electromagnetic valves 35 a to 35 e can adjust the pressure of the hydraulic oil supplied directly from the oil passage 15 or from the manual valve 13 via the forward oil passage 32 or the reverse oil passage 33, and can be supplied to the piston 8. .
Then, the piston 8 is operated by the hydraulic oil supplied from the electromagnetic valves 35a to 35e, and presses the plurality of friction elements 47a and 47b of the transmission elements 5a to 5e in the engaging direction. Further, a biasing force is applied to the piston 8 by a return spring 48 that biases the piston 8 in a direction in which the plurality of friction elements 47a and 47b are disengaged. Thereby, the engagement and release of the speed change elements 5a to 5e can be controlled by adjusting the output hydraulic pressure from the electromagnetic valves 35a to 35e.

The “control unit” TCU 50 includes a hydraulic pressure command unit 50a, a current command unit 50b, and the like.
In the automatic transmission 2, the hydraulic pressure applied to the speed change elements 5 a to 5 e in order to suppress the speed change shock when the speed change elements 5 a to 5 e are shifted is changed according to a predetermined hydraulic pattern.
Therefore, the hydraulic pressure command unit 50a obtains a hydraulic pressure command value to be applied to the speed change elements 5a to 5e based on the hydraulic pressure pattern.
Then, the current command unit 50 b applies a hydraulic pressure command value to the pressure regulation characteristic, obtains a current command value, and gives this current command value to the driver 51.

Here, the driver 51 is individually fixed to each of the electromagnetic valves 35a to 35e.
The driver 51 has an electric circuit including a transistor and the like, and applies an actual current corresponding to the command value of the current from the current command unit 50b to the solenoid valves 35a to 35e. The driver 51 operates so as to supply an actual current to the solenoid valves 35a to 35e. However, the current command value and the actual current value given to the solenoid valve are not necessarily the same due to a change with time of an electric circuit or the like. They do not match.
The driver 51 corresponds to each of the solenoid valves 35a to 35e, and the TCU 50 gives different command values for the current to the driver 51, that is, gives different current values to the solenoid valves 35a to 35e. Can do.

Here, the pressure regulation characteristic is the correlation between the command value of the current and the command value of the hydraulic pressure given to each of the solenoid valves 35a to 35e, that is, the respective drivers 51, and for each solenoid valve 35a to 35e. It has been demanded.
The pressure regulation characteristic in the initial state can be produced by detecting the command value of the current applied to a plurality of drivers and the hydraulic pressure applied to the speed change element, and using the detected average value of the hydraulic pressure.
However, the pressure regulation characteristics in the initial state are not limited to those produced by this method. For example, in the initial state before shipment, the command value of the current given to each of the drivers 51 is changed and the speed change elements 5a to 5a are changed. It may be prepared by obtaining necessary data by detecting the hydraulic pressure given to 5e.

A hydraulic circuit 52 is formed between the mechanical pump 10 and the speed change elements 5a to 5e, and the oil passage 15 continuing from the mechanical pump 10 is branched into a plurality of parts on the way and passes through the manual valve 13 and the like. The transmission elements 5a to 5e are reached via the oil passages 40 to 44.
The electric pump 11 can supply hydraulic pressure to the hydraulic circuit 52 via the oil passage 19.
Moreover, the oil pressure detection means 54 is provided in the output side of the solenoid valves 35a-35e in each of the oil paths 40-44 after a branch.
The oil pressure detecting means 54 is a known pressure sensor having a pressure sensitive element or the like.

[Effects of Examples]
In the hydraulic pressure supply device 1 of the present embodiment, the hydraulic pressure detecting hand 54 is arranged for each of the branched oil passages 40 to 44, and can detect the hydraulic pressure on the output side of the electromagnetic valves 35a to 35e.
Then, for each of the branched oil passages 40 to 44, when the internal combustion engine is stopped, hydraulic pressure is generated by the electric pump 11 to apply the hydraulic pressure to the electromagnetic valves 35a to 35e, and the current to the electromagnetic valves 35a to 35e. Is provided to adjust the hydraulic pressure, and the hydraulic pressure applied to the speed change elements 5a to 5e is detected by the respective hydraulic pressure detection means 54 to obtain the detected hydraulic pressure value.
And each pressure regulation characteristic is updated using the command value of electric current and the detected value of oil pressure.

Thereby, since each of the electromagnetic valves 35a to 35e has the hydraulic pressure detecting means 54, the acquisition of data for creating the pressure regulation characteristics is performed in parallel in time for the plurality of electromagnetic valves 35a to 35e. Can do.
For this reason, the pressure regulation characteristics of the plurality of electromagnetic valves 35a to 35e can be updated in parallel in time.
As a result, the time spent for updating the pressure regulation characteristics for the plurality of electromagnetic valves 35a to 35e can be shortened.

  More specifically, for example, when the select bar 30 is in the D range, the hydraulic pressure can be supplied to the brake transmission element 5a and the forward transmission elements 5b, 5c, 5d by the electric pump 11 in the idling stop state. The data for updating the pressure regulation characteristics of these transmission elements 5a to 5d can be collected in parallel.

In this embodiment, the idling stop system includes a control that controls the internal combustion engine to stop when the select bar 30 is in the R range and the vehicle speed is a predetermined value or less.
For this reason, even when the select bar 30 is in the R range, the vehicle can be shifted to the idling stop state. As a result, the hydraulic pressure can be supplied to the brake transmission element 5a and the reverse transmission element 5e by the electric pump 11, and data for updating the pressure regulation characteristics of these transmission elements 5a and 5e is collected in parallel. be able to.

Here, a specific example of updating the respective pressure regulation characteristics is shown in FIG.
In this embodiment, as shown in FIGS. 2A and 2B, there are a hydraulic pressure command value and a hydraulic pressure detection value for each of a plurality of current command values, and a plurality of hydraulic pressure command values. And a plurality of hydraulic pressure detection values are approximated by a curve and stored in the TCU 50 or the like.

  In this embodiment, the current command value and the hydraulic pressure detection value can be collected using the electric pump 11 and the hydraulic pressure detection means 54 while the internal combustion engine is stopped, and the collected data is used. The pressure regulation characteristics can be updated. In addition, since the data collected while the internal combustion engine is stopped is data collected in a static state, by updating the pressure regulation characteristics based on such data, the reliability of the updated pressure regulation characteristics can be improved. Can be increased.

For this reason, in the hydraulic control device 1 that controls the hydraulic pressure supplied to the speed change elements 5a to 5e of the automatic transmission 2, even if an inevitable change with time occurs, data is collected when the internal combustion engine is stopped and the pressure regulation characteristics are obtained. By updating, the shift shock can be suppressed without increasing the difference between the hydraulic pressure command value and the actual value.
Here, the inevitable change with time is the correlation between the thrust of the spool and the valve opening in the solenoid valve, and the change in the characteristics of the electrical circuit including the coil and driver of the solenoid valve. It is. And even if the difference between the hydraulic pressure command value and the actual value becomes about several tens of kPa due to the change with time, it becomes a cause of the shift shock, so that the pressure regulation characteristic needs to be updated.
Since data collection is performed while the internal combustion engine is stopped, unintentional power transmission does not occur in the automatic transmission 2 during data collection, and data collection can be performed safely.

Further, since the relationship between the command values of the plurality of hydraulic pressures and the detected values of the plurality of hydraulic pressures is approximated by a curve and stored in the TCU 50 or the like, for example, compared to the case where these relationships are approximated by a straight line, It is possible to interpolate between measurement points with higher accuracy.
The updated pressure regulation characteristic can be obtained based on the approximate curve, and the current command value can be obtained accurately from the updated pressure regulation characteristic.

Further, in the hydraulic pressure supply device 1 of the present embodiment, the drivers 51 that drive the respective electromagnetic valves 35a to 35e are individually fixed to the respective electromagnetic valves 35a to 35e.
As a result, even when the pressure regulating characteristics are respectively produced in the set of the solenoid valves 35a to 35e and the driver 51, the set of the solenoid valves 35a to 35e and the driver 51 is not separated even during movement. It is possible to prevent the set of ~ 35e and the driver 51 from being disturbed.
For this reason, the monitoring burden for maintaining the set of the solenoid valves 35a to 35e and the driver 51 can be reduced.

  In this case, the driver 51 is not provided on the TCU 50 side. For this reason, even when only one of the electromagnetic valves 35a to 35e fails, all the electromagnetic valves 35a to 35e and TCU 50 (each of the electromagnetic valves 35a to 35e) that have previously obtained pressure regulation characteristics as in the prior art. Since it is not necessary to deal with it by exchanging a set with a corresponding driver 51), it becomes easy to deal with repair in the event of a solenoid valve failure.

[Modification]
Various modifications can be considered for the present invention without departing from the gist thereof.
For example, according to the embodiment, the electric pump 11 is used as another hydraulic pressure generation source, but an accumulator may be used as another hydraulic pressure generation source.

  In the embodiment, the relationship between the command values of the plurality of hydraulic pressures and the detection values of the plurality of hydraulic pressures is approximated by a single curve, but the pressure range of the use region is divided into a plurality of pressure range portions, Curve approximation may be performed within each pressure range portion, and each approximate curve may be stored in the TCU 50 or the like.

  Specifically, for example, as shown in FIG. 3, a plurality of times (1st, 2nd, 3rd 3rd in the drawing) in the pressure range of the use region so that the command value of the hydraulic pressure is slightly different in each pressure range portion. Times), a plurality of oil pressure command values and a plurality of oil pressure detection values are acquired. That is, the acquisition of one hydraulic pressure command value and one hydraulic pressure detection value in each pressure range portion is repeated three times.

Then, each approximate curve in each pressure range portion is calculated from a plurality of hydraulic pressure command values and a plurality of detected hydraulic pressure values in each pressure range portion, and stored in the TCU 50 or the like.
Thereby, in each pressure range part, since an approximate curve can be calculated | required separately, the deviation (deviation) of an approximate curve and a measurement point can be suppressed, and a more exact pressure regulation characteristic can be produced. it can.

The storage destination of these approximate curves is not limited to the TCU 50, and may be stored in each of the electromagnetic valves 35a to 35e.
In FIG. 3, the pressure ranges do not overlap each other, but the pressure ranges may overlap with respect to the hydraulic pressure command value. In this case, for the overlapping portion, either one of the approximate curves may be used, or a new approximate curve may be generated using both approximate curves of the overlapping portion.

DESCRIPTION OF SYMBOLS 1 Hydraulic control apparatus 2 Automatic transmission 5a-5e Transmission element 10 Mechanical pump 11 Electric pump (Another hydraulic pressure generation source) 15 Oil path 35a-35e Solenoid valve
40 to 44 Oil passage (oil passage after branching) 50 TCU (control means) 52 Hydraulic circuit
54 Oil pressure detection means

Claims (3)

A mechanical pump (10) that is driven by an internal combustion engine to generate hydraulic pressure is provided. The hydraulic pressure generated by the mechanical pump (10) is regulated by electromagnetic valves (35a to 35e), and a plurality of shifts of the automatic transmission (2) are performed. To the elements (5a-5e),
In a hydraulic circuit (52) formed between the mechanical pump (10) and each of the transmission elements (5a to 5e), an oil passage (15) continuing from the mechanical pump (10) is branched into a plurality of parts on the way. And each of the shifting elements (5a to 5e) has been reached,
The electromagnetic valves (35a to 35e) are arranged for each of the branched oil passages (40 to 44), and in a plurality of assembled hydraulic control devices (1),
Each of the electromagnetic valves (35a to 35e) has a pressure regulation characteristic that is a correlation between the hydraulic pressure applied to the transmission elements (5a to 5e) and the current applied to the electromagnetic valves (35a to 35e), and the transmission element (5a To a control means (50) for obtaining a command value of a current to be applied to the solenoid valves (35a to 35e) by applying a command value of a hydraulic pressure to be applied to
Another hydraulic pressure generation source (11) capable of generating hydraulic pressure and supplying the hydraulic pressure to the hydraulic circuit (52) without being driven by the internal combustion engine;
A plurality of oil pressure detecting means (54) arranged for each of the branched oil passages (40 to 44) and capable of detecting oil pressure on the output side of the electromagnetic valves (35a to 35e),
For each of the branched oil passages (40 to 44), when the internal combustion engine is stopped, the other hydraulic pressure generation source (11) generates hydraulic pressure to apply the hydraulic pressure to the electromagnetic valves (35a to 35e). In addition, the current command value is applied to the solenoid valves (35a to 35e) to adjust the oil pressure, and the oil pressure detection means (54) detects the oil pressure detection value to obtain the current command value. And the pressure control characteristic is updated using the detected value of the hydraulic pressure. In the hydraulic control device (1) according to claim 1,
The solenoid valve (35a to 35e) is driven, and has a driver (51) that outputs a current based on the command value of the current to the solenoid valve (35a to 35e),
The hydraulic control device (1), wherein the driver (51) is fixed for each of the electromagnetic valves (35a to 35e). In the hydraulic control device (1) according to claim 1 or 2,
There are a plurality of current command values given to the solenoid valves (35a to 35e) when the internal combustion engine is stopped, and a hydraulic pressure command value and a detected hydraulic pressure value correspond to each of the plurality of current command values. And
A hydraulic control device (1), wherein the relationship between a plurality of hydraulic pressure command values and a plurality of hydraulic pressure detection values is approximated by a curve and stored.

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