JP2016148397A - Hydraulic control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce power consumption occurring in a control valve when a friction element is in a stationary state, in a hydraulic control device of an automatic transmission.SOLUTION: In a hydraulic control device 1, opening/closing valves 21B1, 21C1 are disposed in supply passages 9B1, 9C1 and controlled by energization to open and close the supply passages 9B1, 9C1 according to an energization state. Further hydraulic sensors 22B1, 22C1 detect a hydraulic pressure at a downstream side of the opening/closing valves 21B1, 21C1 in each of the supply passages 9B1, 9C1. Furthermore an ECU 3 controls energization of the opening/closing valves 21B1, 21C1 on the basis of detection values of the hydraulic pressure detected by the hydraulic sensors 22B1, 22C1 in each of the supply passages 9B1, 9C1. Thus power consumption occurring in a control valve 8 when a friction element 2 is in a stationary state, can be reduced in the hydraulic control device 1.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a hydraulic control device that controls the hydraulic pressure supplied to each of a plurality of friction elements of an automatic transmission mounted on a vehicle to operate engagement and release of engagement plates in the friction elements.

Conventionally, in the hydraulic control device described above, there is an increasing demand for reducing power consumption in order to contribute to reduction in fuel consumption. In response to this request, the present inventors paid attention to the power consumption of the solenoid in the hydraulic pressure adjusting means among the power consumption of the hydraulic control device.
Here, the hydraulic pressure adjusting means includes a solenoid that is energized and controlled based on a command value of the hydraulic pressure, and a valve portion that is adjusted in opening according to the energization amount of the solenoid, and is provided for each friction element, and has a predetermined hydraulic pressure. The hydraulic pressure generated at the source is adjusted and supplied to the friction element.

  The hydraulic pressure command value is a command value for the hydraulic pressure to be supplied to the friction element. Then, when a shift request is generated, the hydraulic pressure command value is changed with time for each hydraulic pressure adjusting means related to the shift in order to operate engagement and release of the engagement plates in the friction element related to the shift. As a result, the energization amount is changed over time in the solenoid of the hydraulic pressure adjusting means, the electric power is consumed and the hydraulic pressure is adjusted, and in each friction element, the engagement plates go through a transient state between engagement and release. And finally the required engagement or release state is reached.

  By the way, in the solenoid of the hydraulic pressure adjusting means, power consumption is generated even in a steady state where there is no shift request and the engagement plates are kept engaged or disengaged by the respective friction elements as in high-speed running. That is, the hydraulic pressure adjusting means is a normal low pressure type that outputs a low pressure when the solenoid is not energized (hereinafter referred to as N / L type), or a normal high pressure that outputs a high pressure when the solenoid is not energized. One of the molds (hereinafter referred to as N / H type).

Therefore, when the N / L type is adopted as the hydraulic pressure adjusting means, when the engagement is maintained by the friction element supplied with the hydraulic pressure from the N / L type hydraulic pressure adjusting means, the solenoid is energized to open the opening of the valve portion. Needs to be maintained on the high voltage side, and power consumption occurs. Even when the N / H type is adopted, when the release is maintained by the friction element supplied with the hydraulic pressure from the N / H type hydraulic pressure adjusting means, the solenoid is energized and the opening degree of the valve portion is set to the low pressure side. It must be maintained and power consumption occurs.
Therefore, the present inventors have intensively studied for the purpose of reducing the power consumption generated by the hydraulic pressure adjusting means when the friction element is in a steady state.

  Note that Patent Document 1 discloses a configuration in which power consumption is reduced in a specific steady state by making all hydraulic pressure adjusting means N / L type. Further, in Patent Document 2, an oil passage for introducing hydraulic pressure is provided at the end of the valve body, and the opening and closing of the oil passage is controlled separately from the solenoid so that the solenoid is not energized (consumed to the solenoid). The valve section can be maintained on the high pressure side or the low pressure side even if no electric power is generated.

  However, according to the configurations of Patent Documents 1 and 2, the generation of power consumption in the solenoid can be suppressed only when the valve portion is maintained on either the high pressure side or the low pressure side, and maintained on the other side. In the solenoid, power consumption occurs in the solenoid. For this reason, the configurations of Patent Documents 1 and 2 are not sufficient to achieve the object aimed by the present inventors (reducing power consumption generated by the hydraulic pressure adjusting means when the friction element is in a steady state). is there.

JP 2010-084855 A JP 2007-139181 A

  The present invention has been made to solve the above-described problems, and an object of the present invention is to reduce power consumption generated by the hydraulic pressure adjusting means when the friction element is in a steady state in a hydraulic control device for an automatic transmission. It is to reduce.

  According to the first invention of the present application, the hydraulic control device controls the hydraulic pressure supplied to each of the plurality of friction elements of the automatic transmission mounted on the vehicle to engage and release the engagement plates between the friction elements. To operate. The hydraulic control device includes the following hydraulic pressure command means, hydraulic pressure adjustment means, supply path, supply path opening / closing means, hydraulic pressure detection means, and opening / closing control means.

  First, the hydraulic pressure command means calculates a hydraulic pressure command value to be supplied for each friction element. The hydraulic pressure adjusting means includes a first solenoid that is energized and controlled based on a hydraulic pressure command value, and a first valve portion that is adjusted in opening according to the energization amount of the first solenoid, and is provided for each friction element. The hydraulic pressure generated by a predetermined hydraulic pressure generation source is adjusted and supplied to the friction element.

  The supply path is provided for each friction element, connects the hydraulic pressure adjusting means and the friction element, and supplies the hydraulic pressure adjusted by the hydraulic pressure adjusting means from the hydraulic pressure adjusting means to the friction element. The supply path opening / closing means is provided in at least one of the supply paths and is energized to open and close the supply path according to the energized state. The oil pressure detecting means detects the oil pressure downstream of the supply path opening / closing means in the supply path. Furthermore, the opening / closing control means controls energization of the supply path opening / closing means based on the detected value of the oil pressure detected by the oil pressure detecting means.

  Thereby, when the friction element is in a steady state, the supply path is closed by the supply path opening / closing means, so that the hydraulic pressure in the friction element can be maintained regardless of the low pressure or the high pressure. Further, since the hydraulic pressure in the friction element can be monitored by the hydraulic pressure detection means, it is possible to detect that the hydraulic pressure cannot be maintained at the low pressure or the high pressure in the friction element while the supply path is closed.

When it is detected that the hydraulic pressure cannot be maintained at the low pressure or the high pressure in the friction element, the supply path opening / closing means is energized by the opening / closing control means to open the supply path, and the oil pressure adjusting means is energized to be controlled. The hydraulic pressure in the friction element can be restored to a low pressure or a high pressure.
For this reason, in the hydraulic control device of the automatic transmission, it is possible to reduce power consumption generated by the hydraulic pressure adjusting means when the friction element is in a steady state.

According to the hydraulic control apparatus of the second invention of the present application, the supply path opening / closing means closes the supply path when there is no energization.
Thereby, the power consumption generated by the supply path opening / closing means when the friction element is in a steady state can also be reduced.

According to the hydraulic control apparatus of the third invention of the present application, the supply path opening / closing means includes a second solenoid that is energized and controlled by the opening / closing control means, and a second valve portion that is opened and closed according to the magnetic force generated by the second solenoid. The supply path is opened and closed by opening and closing the second valve portion. The second valve portion opens and closes the supply path using a poppet valve.
Thereby, compared with the case where other valve structures (for example, spool valves) are used, leakage in the supply path opening / closing means can be suppressed. For this reason, since the frequency of operating the hydraulic pressure adjusting means and the supply path opening / closing means can be reduced when the friction element is in a steady state, the power consumption generated in the hydraulic pressure adjusting means and the supply path opening / closing means can be further reduced. Can do.

  According to the hydraulic control device of the fourth invention of the present application, the second valve portion has a hydraulic chamber that applies hydraulic pressure to the poppet valve on the closed side. The supply path opening / closing means has a secondary second valve portion that supplies high hydraulic pressure equal to or higher than the hydraulic pressure before adjustment by the hydraulic pressure adjusting means to the hydraulic chamber, and extracts from the hydraulic chamber. The valve body of the sub second valve portion is driven to a side where high hydraulic pressure is supplied to the hydraulic chamber or a side where it is extracted from the hydraulic chamber by a magnetic force generated by the second solenoid, and a predetermined spring is generated. Driven by the force in the direction opposite to the direction of drive by magnetic force.

  Accordingly, the poppet valve can be driven to the closed side or the open side by raising or lowering the hydraulic pressure in the hydraulic chamber by increasing or decreasing the magnetic force of the second solenoid. For this reason, since the poppet valve can be driven to the open side or the close side without being driven directly by the magnetic force of the second solenoid, there is no need to employ a very powerful second solenoid or spring, The size of the second solenoid and the spring can be reduced.

According to the hydraulic control device of the fifth invention of the present application, it is connected to the hydraulic pressure adjusting means that needs to energize the first solenoid in order to engage or release the engagement plates in the supply path during high speed running. Supply path opening / closing means is provided only in the supply path.
The frequency of steady state is high when traveling at high speed. For this reason, the supply path opening / closing means is provided only in the supply path connected to the hydraulic pressure adjustment means that needs to energize the first solenoid in order to engage and release the engagement plates during high-speed traveling. An increase in device cost due to the addition of the road opening / closing means can be suppressed.

According to the hydraulic control apparatus of the sixth invention of the present application, the accumulator is connected to the supply path provided with the supply path opening / closing means on the downstream side of the supply path opening / closing means.
Thus, the hydraulic pressure in the friction element can be maintained by the accumulator without opening the supply path by the supply path opening / closing means. For this reason, since the frequency of operating the hydraulic pressure adjusting means and the supply path opening / closing means can be reduced when the friction element is in a steady state, the power consumption generated in the hydraulic pressure adjusting means and the supply path opening / closing means can be further reduced. Can do.

According to the hydraulic control device of the seventh invention of the present application, the second valve portion is provided in each of the plurality of supply passages, and the supply and extraction of high hydraulic pressure to each hydraulic chamber is performed by one sub second valve portion, And one second solenoid.
Thereby, the increase in apparatus cost by addition of a supply path opening / closing means can be suppressed.

According to the hydraulic control device of the eighth invention of the present application, the opening / closing control means has a first threshold value for the detection value by the hydraulic pressure detection means, and when the detection value is larger than the first threshold value, the supply path opening / closing means When the supply path is closed and the detected value becomes smaller than the first threshold, the supply path is opened by the supply path opening / closing means.
According to the hydraulic control device of the ninth invention of the present application, the friction element is driven by the supplied hydraulic pressure to come into contact with one of the engagement plates, press one of the engagement plates and contact the other, and the piston Has a spring that urges the motor in a direction opposite to the direction of hydraulic drive. And the 1st threshold value is set to the numerical value which does not slip between engagement plates.
Thereby, the engagement of the friction element can be reliably maintained in the steady state.

According to the hydraulic control apparatus of the tenth invention of the present application, the opening / closing control means has a second threshold value for the detection value by the hydraulic pressure detection means, and when the detection value is smaller than the second threshold value, the supply path opening / closing means When the supply path is closed and the detected value becomes larger than the second threshold, the supply path is opened by the supply path opening / closing means.
According to the hydraulic control apparatus of the eleventh aspect of the present application, the second threshold value is set to a numerical value at which the piston does not contact one of the engagement plates.
Thereby, the opening of the friction element can be reliably maintained in a steady state.

1 is an overall configuration diagram of a hydraulic control device (Example 1). FIG. (Example 1) which shows the structure of a friction element, and the electricity supply path | route to a hydraulic-pressure adjustment means. (A) is an engagement table showing the engagement and release states of the friction elements in various shift ranges, and (b) shows whether the hydraulic pressure adjusting means is N / L type or N / H type. (Example 1) which is a polarity table | surface which shows. 3 is a time chart illustrating the operation of the hydraulic control device (Example 1). It is a block diagram of a supply path opening / closing means (Example 1). (Example 1) which is a block diagram of the 2nd solenoid and sub 2nd valve | bulb part which make a part of supply path opening / closing means. FIG. 2 is an overall configuration diagram of a hydraulic control device (Example 2). FIG. 3 is an overall configuration diagram of a hydraulic control device (Example 3). (Example 4) which is a whole block diagram of a hydraulic control apparatus. (A) is an engagement table showing the engagement and release states of the friction elements in various shift ranges, and (b) shows whether the hydraulic pressure adjusting means is N / L type or N / H type. (Example 4) which is a polarity table | surface which shows.

  Hereinafter, the form for inventing is demonstrated using an Example. In addition, an Example discloses a specific example, and it cannot be overemphasized that this invention is not limited to an Example.

[Configuration of Example 1]
The configuration of the hydraulic control device 1 according to the first embodiment will be described with reference to FIGS.
As shown in FIG. 1, the hydraulic control device 1 controls the hydraulic pressure supplied to each friction element 2 of an automatic transmission mounted on a vehicle, and includes an electronic control unit (ECU) 3. Has been.
Here, the ECU 3 is an input circuit that processes an input signal, a CPU that performs control processing and arithmetic processing based on the input signal, and various types of data that are stored and held such as data and programs necessary for control processing and arithmetic processing. And a microcomputer 3a having an output circuit for outputting necessary signals based on the processing result of the CPU (see FIG. 2).

  Further, as shown in FIG. 2, the friction element 2 includes engaging plates 4a and 4b that are engaged with each other and released, a piston 5 that is driven by the supplied hydraulic pressure, and a direction in which the piston 5 is driven by the hydraulic pressure. And a spring 6 biased in the opposite direction. Then, the hydraulic control device 1 moves the piston 5 by changing the magnitude of the hydraulic pressure supplied to the friction element 2 according to a command from the ECU 3, and operates the engagement and release of the engagement plates 4a and 4b. .

  That is, when the friction element 2 is shifted from the open state to the engaged state, the hydraulic pressure is increased and the piston 5 is moved in a direction approaching the engagement plate 4a. Then, the piston 5 is brought into contact with the engagement plate 4a, the engagement plates 4a and 4b are brought into contact with each other, and the hydraulic pressure is increased to such an extent that no slip occurs between the engagement plates 4a and 4b. Conversely, when the friction element 2 is shifted from the engaged state to the released state, the hydraulic pressure is decreased and the piston 5 is moved in a direction away from the engagement plate 4a. Then, the engagement plates 4a and 4b are separated from each other, and the hydraulic pressure is reduced to such an extent that the piston 5 does not contact the engagement plate 4a.

In addition, the automatic transmission of Example 1 is 4th speed, and five friction elements B1, B2, and C1-C3 are provided as the friction elements 2. Further, the engagement and release states of the friction elements B1, B2, and C1 to C3 in each shift range are as shown in FIG.
Hereinafter, when it is necessary to specify and call the friction elements 2 individually, they may be called the friction elements B1, B2, C1 to C3.

The hydraulic control device 1 includes the following hydraulic command means, hydraulic pressure adjusting means 8 and supply path 9 as a basic configuration.
First, the hydraulic pressure command means is a means for calculating a hydraulic pressure command value to be supplied for each of the friction elements B1, B2, C1 to C3, and is realized by the microcomputer 3a of the ECU 3. Here, the microcomputer 3a, for example, changes the command value of the hydraulic pressure with time according to the process as shown by the dotted line in FIG. 4 when the friction element 2 is shifted from the open state to the engaged state or from the engaged state to the open state.

  Next, the hydraulic pressure adjusting means 8 includes a solenoid 10 that is energized and controlled based on a hydraulic pressure command value, and a valve portion 11 that is adjusted in opening according to the energization amount of the solenoid 10 (hereinafter, the hydraulic pressure adjusting means 8 is Sometimes referred to as control valve 8). The control valve 8 is provided for each of the friction elements B1, B2, and C1 to C3, adjusts the hydraulic pressure generated by a predetermined hydraulic pressure generation source 13, and supplies the adjusted hydraulic pressure to each of the friction elements B1, B2, and C1 to C3. The control valve 8 has a feedback function that stabilizes the output hydraulic pressure by feeding back the output hydraulic pressure to the F / B chamber, for example, as in the electromagnetic spool valve described in Patent Document 2.

  Hereinafter, the solenoid 10 and the valve part 11 of the control valve 8 are referred to as a first solenoid 10 and a first valve part 11, respectively. Further, when it is necessary to distinguish the control valve 8 for each of the friction elements B1, B2, C1 to C3, the control valves 8 for the friction elements B1, B2, C1 to C3 are respectively controlled by the control valves 8B1, 8B2, 8C1 to 8C3. Sometimes called.

The hydraulic pressure generation source 13 has a known structure having a mechanical hydraulic pump (not shown) driven by an internal combustion engine, an electromagnetic valve (not shown) for adjusting the output hydraulic pressure, and the like.
Further, the amount of energization to the first solenoid 10 is feedback controlled in the ECU 3, for example.

  That is, as shown in FIG. 2, the ECU 3 has a driver circuit 14 that increases or decreases the energization amount to the first solenoid 10 in accordance with a control signal output from the microcomputer 3 a, and the energization amount to the first solenoid 10. A current sensor 15 for detection is provided. For example, the microcomputer 3a obtains a command value for the energization amount based on the command value for the hydraulic pressure, and synthesizes and outputs a control signal to be given to the driver circuit 14 according to the command value for the energization amount.

Further, the microcomputer 3a receives the detection signal of the current sensor 15 to grasp the detected value of the energization amount, compares the command value with the detected value with respect to the energization amount, and, for example, according to the comparison result, for example, the control signal Change the duty ratio.
Whether each of the control valves 8 is an N / L type or an N / H type is as shown in FIG.

  Next, the supply path 9 is an oil path that forms a part of the hydraulic circuit from the hydraulic pressure generation source 13 to the friction element 2, and is provided for each of the friction elements B1, B2, C1 to C3, and the control valve 8 and the friction element. B1, B2, and C1 to C3 are connected to each other. That is, the supply path 9 is an oil path for supplying the hydraulic pressure adjusted by the control valve 8 from the control valve 8 to each of the friction elements B1, B2, C1 to C3. Further, the supply path 9 is provided with an orifice 16 for suppressing the sudden supply of hydraulic pressure to the friction element 2 (see FIG. 1).

  Hereinafter, when it is necessary to distinguish the supply path 9 for each of the friction elements B1, B2, and C1 to C3, the supply paths 9 for the friction elements B1, B2, and C1 to C3 are respectively referred to as the supply paths 9B1, 9B2, and 9C1 to 9C3. Sometimes called.

  Here, the hydraulic circuit is provided with a manual valve 17 for switching the supply system of the hydraulic pressure output from the hydraulic pressure generation source 13 between the forward system and the reverse system (see FIG. 1). . That is, the manual valve 17 includes a hydraulic pressure input port 17a output from the hydraulic pressure generation source 13, a forward side port 17b for supplying hydraulic pressure to the friction element 2 to be engaged in the D range and L range, and R There is a reverse port 17c for supplying hydraulic pressure to the friction element 2 to be engaged in the range.

The manual valve 17 is driven by, for example, an operation of the shift lever 18 by the occupant, and the input port 17a and the forward port 17b communicate with each other, the input port 17a and the reverse port 17c communicate with each other, and the like. Realize various states.
Hereinafter, the hydraulic pressure output from the manual valve 17 is referred to as a source pressure. Moreover, when distinguishing the hydraulic pressure output from the forward side port 17b and the hydraulic pressure output from the reverse side port 17c, the hydraulic pressure output from the reverse side port 17c may be referred to as the forward side source pressure and the reverse side source pressure, respectively.

  Since the friction element B2 is engaged in both the forward-side L range and the reverse-side R range, a shuttle valve 19 is provided in the supply path 9B2. The shuttle valve 19 supplies the hydraulic pressure adjusted by the control valve 8B2 at the forward side original pressure in the L range to the friction element B2, and the reverse side original pressure is supplied to the friction element B2 in the R range.

Subsequently, the operation of the basic configuration of the hydraulic control device 1 will be described with reference to FIG. 4 together with the control by the ECU 3.
First, the ECU 3 roughly divides the state of the friction element 2 into two states, a non-shift state and a shift state, in the process.

  The non-shift state is a steady state where there is no shift request and the engagement plates 4a and 4b are kept engaged or released, and the hydraulic pressure in the friction element 2 is maintained at one of high pressure and low pressure. The shift state is a transitional state where the engagement plates 4a and 4b are released from engagement to each other or from release to engagement according to a shift request, and the hydraulic pressure in the friction element 2 is changed from high pressure to low pressure or low pressure. Change to high pressure.

  In the time chart shown in FIG. 4, the engine speed and output torque when shifting from the third speed to the fourth speed, on / off of energization to the first solenoid 10, the hydraulic pressure in the friction elements B1 and C1, and the friction The change over time of the command value of the hydraulic pressure to be supplied to the elements B1 and C1 is illustrated (hereinafter, the hydraulic pressure to be supplied to the friction element 2 may be referred to as supply pressure).

  Further, according to the engagement table of FIG. 3, in the shift from the third speed to the fourth speed, the state of the friction element B1 changes from the release to the engagement, and the hydraulic pressure in the friction element B1 changes from the low pressure Lo to the high pressure Hi. . Further, the state of the friction element C1 changes from engagement to release, and the hydraulic pressure in the friction element C1 changes from the high pressure Hi to the low pressure Lo.

Next, the ECU 3 divides the gear shift state from the release to the engagement into three phases, a filling phase, a standby phase, and a hydraulic control phase, and the gear shift state from the engagement to the release is hydraulic control phase and discharge. Divide into phases.
First, the filling phase is a process of filling the friction element 2 with hydraulic pressure in response to the occurrence of a shift request. That is, when a shift request is generated, the ECU 3 raises the command value of the supply pressure for the friction element B1 from the low pressure Lo to the first intermediate pressure M1 in a stepped manner, and the command value is set to the first intermediate pressure during the period determined as the filling phase. Maintain at M1.

  As a result, in the control valve 8B1, the first solenoid 10 is energized and the first valve unit 11 is controlled to have an opening degree corresponding to the first intermediate pressure M1, and the hydraulic pressure in the friction element B1 is relaxed by the orifice 16. It will be filled. Then, the filling is completed in the middle of the filling phase (see time t1 in FIG. 4), the hydraulic pressure in the friction element B1 is slightly higher than the low pressure Lo, and the piston 5 moves toward the engagement plate 4a. To start.

Next, the standby phase is a step of waiting at a predetermined standby pressure Wa before starting to raise the supply pressure command value.
That is, when the period of the filling phase ends, the ECU 3 reduces the command value of the supply pressure for the friction element B1 from the first intermediate pressure M1 to the standby pressure Wa stepwise, and waits for the command value during the period set as the standby phase. The pressure Wa is maintained. Thereby, in the control valve 8B1, the opening degree of the first valve portion 11 is controlled according to the standby pressure Wa, and in the friction element B1, the piston 5 gently contacts the engagement plate 4a (at the time t2 in FIG. 4). Further, the engagement plate 4a is pushed by the piston 5 and starts moving toward the engagement plate 4b.

Next, the hydraulic control phase when releasing to engagement is a step of controlling the supply pressure so as to gently realize engagement between the engagement plates 4a and 4b.
That is, when the period of the standby phase ends, the ECU 3 raises the command value of the supply pressure for the friction element B1 from the standby pressure Wa to the second intermediate pressure M2 in a linear function, and then increases the command value of the supply pressure to the second value. Maintain at intermediate pressure M2. As a result, in the control valve 8B1, the first solenoid 10 is energized and controlled, and the first valve unit 11 is controlled to an opening corresponding to the command value that sequentially increases, and then the opening corresponding to the second intermediate pressure M2. Controlled.

  During this time, in the friction element B1, the engagement plates 4a and 4b rotate relative to each other and continue to transmit torque while sliding, and the sliding gradually stops. Then, the ECU 3 raises the command value of the supply pressure stepwise to the high pressure Hi at the end of the hydraulic control phase. As a result, the first solenoid 10 is energized and controlled in the control valve 8B1, the opening of the first valve unit 11 is controlled according to the high pressure Hi, and the hydraulic pressure in the friction element B1 increases to the high pressure Hi.

In addition, the hydraulic control phase at the time of engagement to release is a step of controlling the supply pressure in order to gently release the engagement plates 4a and 4b.
That is, the ECU 3 starts the hydraulic control phase in the friction element C1 simultaneously with the start of the filling phase in the friction element B1, and reduces the command value of the supply pressure to the friction element C1 from the high pressure Hi to the third intermediate pressure M3 in a stepped manner. The third intermediate pressure M3 is maintained, and then the command value of the supply pressure is reduced from the third intermediate pressure M3 to the low pressure Lo in a substantially linear function.

  As a result, the first solenoid 10 is energized and controlled in the control valve 8C1, and the first valve unit 11 is controlled to an opening corresponding to the third intermediate pressure M3, and then the opening corresponding to the command value that sequentially decreases. To be controlled. During this time, in the friction element C1, the engagement plates 4a and 4b rotate relative to each other and continue to transmit torque while sliding, and the torque is not transmitted gradually.

Finally, the discharge phase is a process of discharging hydraulic pressure from the friction element 2.
That is, the ECU 3 maintains the command value of the supply pressure for the friction element C1 at the low pressure Lo. As a result, in the control valve 8C1, the first solenoid 10 is energized and the first valve portion 11 is controlled to an opening corresponding to the low pressure Lo, and the hydraulic pressure is discharged from the friction element C1. During this time, in the friction element C1, the oil pressure is kept slightly higher than the low pressure Lo, and the discharge of the oil pressure from the friction element C1 is completed during the discharge phase (see time t3 in FIG. 4). Thus, the hydraulic pressure is lowered to the low pressure Lo.

[Features of Example 1]
A characteristic configuration of the hydraulic control apparatus 1 according to the first embodiment will be described.
The hydraulic control apparatus 1 includes the following supply path opening / closing means 21, hydraulic pressure detection means 22, and opening / closing control means as characteristic features (see FIGS. 1, 5, 6, etc.).

  First, the supply path opening / closing means 21 is provided in each of the supply paths 9B1 and 9C1 and is energized and controlled to open and close the supply paths 9B1 and 9C1 according to the energized state (hereinafter referred to as opening and closing the supply path opening and closing means 21). Sometimes referred to as valve 21).

The on-off valve 21 includes a solenoid 23 that is energized and controlled by the ECU 3 and a valve portion 24 that is opened and closed according to the magnetic force generated by the solenoid 23, and opens and closes the supply path 9 by opening and closing the valve portion 24. The on-off valve 21 is a normally closed type that closes the supply path 9 when there is no energization.
Hereinafter, the solenoid 23 and the valve portion 24 of the on-off valve 21 are referred to as a second solenoid 23 and a second valve portion 24, respectively.

  As shown in FIG. 5, the second valve portion 24 includes a poppet valve 26 as a valve body, and a housing 27 that forms a part of the supply passage 9 and supports the poppet valve 26 slidably. The supply path 9 is closed by sitting on a valve seat 28 provided in the housing 27, and the supply path 9 is opened by separating from the valve seat 28. Here, the valve seat 28 is provided in an annular shape, and the inner periphery of the valve seat 28 forms a part of the supply path 9, and the hydraulic pressure of the supply path 9 acts on the open side with respect to the poppet valve 26. Further, the second valve portion 24 is provided with a hydraulic chamber 29 that applies a hydraulic pressure to the poppet valve 26 on the closed side.

The on-off valve 21 drives the poppet valve 26 to the closed side or the open side by supplying the hydraulic pressure before adjustment by the control valves 8B1 and 8C1 to the hydraulic pressure chamber 29 and extracting it from the hydraulic pressure chamber 29.
Here, the on-off valve 21 has a secondary second valve portion 31 that supplies the original pressure to the hydraulic chamber 29 and extracts it from the hydraulic chamber 29. As shown in FIG. 6, the valve body 32 of the sub second valve portion 31 is driven to the side where the original pressure is extracted from the hydraulic chamber 29 by the magnetic force generated by the second solenoid 23, and the spring 33 is The generated pressure is driven to supply the original pressure to the hydraulic chamber 29.

  That is, the second solenoid 23 and the sub second valve portion 31 constitute an electromagnetic valve 34. The solenoid valve 34 opens the hydraulic chamber 29 with respect to the source pressure extraction side by energizing the second solenoid 23 and closes it with respect to the supply side, and stops the energization of the second solenoid 23 with the hydraulic chamber. 29 is closed to the outlet side of the original pressure and opened to the supply side.

  More specifically, the second solenoid 23 includes a fixed core 37 and a movable core 38 that are arranged on the inner peripheral side of the coil 36 and allow the magnetic flux to pass through, as well as a rod 39 that is moved by the magnetically attracted movable core 38, and a movable core. And a spring 33 that urges the rod 39 and the movable core 38 in a direction opposite to the moving direction of the magnetic valve 38 (hereinafter, the axial direction of the electromagnetic valve 34 is the axis on which the movable core 38 is moved by the magnetic attractive force). One side in the direction, and the side on which the movable core 38 is moved by the spring 33 is defined as the other side in the axial direction.)

  Here, the fixed core 37 is provided as a metal part 41 made of a magnetic body integrated with the housing 40 of the sub second valve portion 31, and the metal part 41 is provided with an inner peripheral hole 43 penetrating in the axial direction. Yes. The rod 39 is slidably accommodated in the inner peripheral hole 43, and the movable core 38 abuts against the other end of the rod 39 with the abutting member 44 fixed to itself, thereby causing the rod 39 to move to one end side in the axial direction. Move to. Further, the spring 33 is, for example, a coil spring, and is between a spring seat 33 a on one end side in the axial direction provided on the wall of the inner peripheral hole 43 and a spring seat 33 b on the other end side in the axial direction provided on the rod 39. Is set.

The sub second valve portion 31 includes a housing 40 that is a part of the metal part 41 and a spherical valve body 32 that is accommodated in a flow path provided in the housing 40.
Here, the housing 40 has an input port 45 that communicates with the supply side of the source pressure, an output port 46 that communicates with the hydraulic chamber 29, and a discharge port 47 that communicates with the extraction side of the source pressure. Are lined up. The three ports 45 to 47 communicate with the inner peripheral hole 43 to form a flow path in the housing 40.

  Further, the valve body 32 is detached from the valve seat 48 provided in the inner peripheral hole 43 to extract the original pressure from the hydraulic chamber 29 (that is, the poppet valve 26 is driven to the open side), and the hydraulic chamber. 29 is switched to a state in which the original pressure is supplied to 29 (that is, the poppet valve 26 is driven to the closed side).

  That is, the valve seat 48 is provided between the output port 46 and the discharge port 47, and the input port 45 and the output port 46 are always open. When the valve body 32 is separated from the valve seat 48, the space between the output port 46 and the discharge port 47 is opened, the original pressure is extracted from the hydraulic chamber 29, and the poppet valve 26 is driven to the open side. Further, when the valve body 32 is seated on the valve seat 48 b, the opening between the output port 46 and the discharge port 47 is closed while maintaining the opening between the input port 45 and the output port 46, and the original pressure is applied to the hydraulic chamber 29. Is supplied and the poppet valve 26 is driven to the closing side.

  As described above, when the sub-second valve portion 31 communicates the source pressure extraction side and the hydraulic chamber 29 with the start of energization of the second solenoid 23, the source pressure is extracted from the hydraulic chamber 29 and the poppet valve 26. Is driven to the open side, and the on-off valve 21 is opened. Further, when the supply of the original pressure and the hydraulic chamber 29 are communicated with each other by the sub-second valve portion 31 as the energization of the second solenoid 23 is stopped, the original pressure is supplied to the hydraulic chamber 29 and the poppet valve 26 is closed. And the on-off valve 21 is closed.

The on-off valve 21 is provided between the control valve 8 and the orifice 16 in the supply path 9 (see FIG. 1). Moreover, the accumulator 50 is connected between all the supply paths 9 between the friction element 2 and the orifice 16 (refer FIG. 1).
In addition, when it is necessary to distinguish the on-off valve 21 for each of the friction elements B1, B2, C1 to C3, the on-off valves 21 for the friction elements B1, B2, C1 to C3 are respectively on-off valves 21B1, 21B2, 21C1 to 21C3. Sometimes called.

The oil pressure detecting means 22 detects the oil pressure downstream of the on-off valve 21 in each of the supply passages 9B1 and 9C1, and is provided downstream of the orifice 16 in each of the supply passages 9B1 and 9C1 ( (See FIG. 1).
Here, in the 4-speed automatic transmission, at the fourth speed, which is the high speed stage, the engagement between the engagement plates 4a, 4b is maintained by the friction element B1, and the engagement plates 4a, 4b are opened by the friction element C1. It is necessary to maintain (refer to the 4th speed row in FIG. 3A). Further, in order to maintain the engagement by the friction element B1 and to maintain the release by the friction element C1, it is necessary to energize the first solenoid 10 of the control valves 8B1 and 8C1 (for B1 in FIG. 3B). (See line for C1).

  Therefore, in the hydraulic control apparatus 1 according to the first embodiment, only the supply passages 9B1 and 9C1 connected to the control valves 8B1 and 8C1 that need to energize the first solenoid 10 at the fourth speed, which is the high speed stage, of the supply passage 9 are provided. On-off valves 21B1 and 21C1 are provided.

  Hereinafter, the hydraulic pressure detection means 22 may be referred to as a hydraulic pressure sensor 22. Further, when it is necessary to distinguish the hydraulic sensor 22 for each of the friction elements B1, B2, and C1 to C3, the hydraulic sensor 22 provided in each of the supply paths 9B1, 9B2, and 9C1 to 9C3 is replaced with the hydraulic sensors 22B1, 22B2, Called 22C1-22C3.

Further, the opening / closing control means is means for controlling energization of the opening / closing valve 21 based on the detected value of the hydraulic pressure detected by the hydraulic sensor 22, and is realized by the microcomputer 3a of the ECU 3.
Here, the ECU 3 has a first threshold value X1 with respect to the detected value of the hydraulic pressure sensor 22B1 in the fourth speed non-shift state. And ECU3 performs the following control with respect to on-off valve 21B1 as a function of an on-off control means.

  That is, the ECU 3 closes the supply passage 9B1 by the on-off valve 21B1 when the detected value of the hydraulic pressure sensor 22B1 is larger than the first threshold value X1 in the non-shift state of the fourth speed, and the detected value is the first threshold value X1. When it becomes smaller than this, the supply passage 9B1 is opened by the on-off valve 21B1. Further, the ECU 3 opens the supply passage 9B1, controls the energization of the first solenoid 10 of the control valve 8B1, opens the first valve portion 11, and continues until the detected value of the hydraulic sensor 22B1 reaches the high pressure Hi. Continue energization control.

Then, after the detected value of the hydraulic sensor 22B1 reaches the high pressure Hi, the ECU 3 stops the energization control of the first solenoid 10 and closes the on-off valve 21B1.
The first threshold value X1 is set to a numerical value that does not cause slippage between the engagement plates 4a and 4b in the friction element B1.

  Further, the ECU 3 has a second threshold value X2 with respect to the detected value of the hydraulic pressure sensor 22C1 in the fourth speed non-shift state. The ECU 3 performs the following control on the on-off valve 21C1 as a function of the on-off control means.

  That is, the ECU 3 closes the supply path 9C1 by the on-off valve 21C1 when the detected value of the hydraulic sensor 22C1 is smaller than the second threshold value X2 when the ECU 3 is in the fourth speed non-shift state, and the detected value is the second threshold value X2. When it becomes larger, the supply passage 9C1 is opened by the on-off valve 21C1. Further, the ECU 3 opens the supply passage 9C1, controls the energization of the first solenoid 10 of the control valve 8C1, opens the first valve portion 11, and continues until the detected value of the hydraulic sensor 22C1 reaches the low pressure Lo. Continue energization control.

Then, after the detected value of the hydraulic sensor 22C1 reaches the low pressure Lo, the ECU 3 stops the energization control of the first solenoid 10 and closes the on-off valve 21C1.
The second threshold value X2 is set to a numerical value at which the piston 5 does not contact the engagement plate 4a in the friction element C1.
Further, in the shift state, the ECU 3 maintains the energization of the second solenoid 23 regardless of the detection values of the hydraulic sensors 22B1 and 22C1, and opens the on-off valves 21B1 and 21C1 (see FIG. 4).

[Effect of Example 1]
According to the hydraulic control apparatus 1 of the first embodiment, the on-off valves 21B1 and 21C1 as supply path opening / closing means are provided in the supply paths 9B1 and 9C1, respectively, and are energized and controlled according to the energized state. Open and close. The hydraulic pressure sensors 22B1 and 22C1 as the hydraulic pressure detection means detect the hydraulic pressure downstream of the on-off valves 21B1 and 21C1 in the supply passages 9B1 and 9C1, respectively. Further, as a function of the opening / closing control means, the ECU 3 controls energization of the opening / closing valve 21B1 based on the detected value of the oil pressure detected by the oil pressure sensor 22B1, and controls the opening / closing valve 21C1 based on the detected value of the oil pressure detected by the oil pressure sensor 22C1. Energize control.

  Thus, when the friction elements B1 and C1 are in the non-shifting state, the supply passages 9B1 and 9C1 are closed by the on-off valves 21B1 and 21C1, respectively, so that the hydraulic pressures in the friction elements B1 and C1 are increased to high pressure Hi and low pressure Lo, respectively. Can be maintained. Further, since the hydraulic pressures in the friction elements B1 and C1 can be monitored by the hydraulic pressure sensors 22B1 and 22C1, respectively, the hydraulic pressure is high in each of the friction elements B1 and C1 while the supply paths 9B1 and 9C1 are closed. It can be detected that Hi or low pressure Lo cannot be maintained.

When it is detected that the hydraulic pressures in the friction elements B1 and C1 cannot be maintained at the high pressure Hi and the low pressure Lo, respectively, the on / off valves 21B1 and 21C1 are energized and controlled by the function of the on / off control means, respectively. 9C1 can be opened and the control valves 8B1 and 8C1 can be energized to restore the hydraulic pressure in the friction elements B1 and C1 to high pressure Hi and low pressure Lo, respectively.
For this reason, in the hydraulic control apparatus 1, it is possible to reduce the power consumption generated in the control valves 8B1 and 8C1 when the friction element 2 is in the non-shifting state (steady state).

The on-off valves 21B1 and 21C1 are normally closed types that close the supply passages 9B1 and 9C1 when there is no energization.
Thereby, it is possible to reduce the power consumption generated in the on-off valves 21B1 and 21C1 when the friction elements B1 and C1 are in a steady state.

Further, the second valve portion 24 as the valve portion of the on-off valves 21B1 and 21C1 opens and closes the supply paths 9B1 and 9C1 by the poppet valve 26.
Thereby, compared with the case where another valve structure (for example, spool valve) is used, the leakage in the on-off valves 21B1 and 21C1 can be suppressed. For this reason, since the frequency with which the control valves 8B1, 8C1 and the on-off valves 21B1, 21C1 are operated when the friction elements B1, C1 are in the non-shifting state can be reduced, the control valves 8B1, 8C1 and the on-off valves 21B1, 21C1 Can further reduce power consumption.

  The second valve portion 24 has a hydraulic chamber 29 that exerts hydraulic pressure on the closed side with respect to the poppet valve 26. In addition, the on-off valve 21 has a secondary second valve portion 31 that supplies the hydraulic pressure (original pressure) before adjustment by the control valve 8 to the hydraulic chamber 29 and extracts it from the hydraulic chamber 29. Then, the valve body 32 of the sub second valve portion 31 is driven to the side that supplies the original pressure to the hydraulic chamber 29 by the magnetic force generated by the second solenoid 23, and by the biasing force generated by the spring 33, Driven to the side where the original pressure is extracted from the hydraulic chamber 29.

  Accordingly, the poppet valve 26 can be driven to the closed side or the open side by raising or lowering the hydraulic pressure of the hydraulic chamber 29 by increasing or decreasing the magnetic force of the second solenoid 23. For this reason, the poppet valve 26 does not have to be driven directly by the magnetic force of the second solenoid 23, so that it is not necessary to employ a strong force for the second solenoid 23 and the spring 33. The second solenoid 23 and the spring The physique of 33 can be reduced.

In addition, the on / off valves 21B1 and 21C1 and the hydraulic sensor 22B1 are provided only in the supply passages 9B1 and 9C1 connected to the control valves 8B1 and 8C1 that are required to energize the first solenoid 10 in the fourth speed of the high speed stage. , 22C1 is provided.
The frequency of steady state is high when traveling at high speed. For this reason, the on / off valves 21B1, 21C1 and the hydraulic sensors 22B1, 22C1 are provided only in the supply passages 9B1, 9C1 connected to the control valves 8B1, 8C1, thereby increasing the cost of the apparatus due to the addition of the on / off valves 21 and the hydraulic sensors 22. Can be suppressed.

An accumulator 50 is connected to each of the supply passages 9B1 and 9C1 on the downstream side of the on-off valves 21B1 and 21C1.
Thereby, the hydraulic pressure in the friction elements B1 and C1 can be maintained by the accumulator 50 without opening the on-off valves 21B1 and 21C1. For this reason, since the frequency with which the control valves 8B1, 8C1 and the on-off valves 21B1, 21C1 are operated when the friction elements B1, C1 are in the non-shifting state can be reduced, the control valves 8B1, 8C1 and the on-off valves 21B1, 21C1 Can further reduce power consumption.

The ECU 3 has a first threshold value X1 for the detection value by the hydraulic sensor 22B1 as a function of the opening / closing control means. When the detection value is larger than the first threshold value X1, the opening / closing valve 21B1 is closed and supplied. When the path 9B1 is closed and the detected value becomes smaller than the first threshold value X1, the on-off valve 21B1 is opened to open the supply path 9B1. The first threshold value X1 is set to a numerical value that does not cause slippage between the engagement plates 4a and 4b in the friction element B1.
Thus, the engagement of the friction element B1 can be reliably maintained in the fourth speed non-shift state.

Further, the ECU 3 has a second threshold value X2 for the detection value by the hydraulic sensor 22C1 as a function of the opening / closing control means. When the detection value is smaller than the second threshold value X2, the ECU 3 closes and supplies the opening / closing valve 21C1. When the path 9C1 is closed and the detected value becomes larger than the second threshold value X2, the on-off valve 21C1 is opened to open the supply path 9C1. Further, the second threshold value X2 is set to a numerical value at which the piston 5 does not contact the engagement plate 4a in the friction element C1.
Thus, the opening of the friction element C1 can be reliably maintained in the fourth speed non-shift state.

[Example 2]
A hydraulic control device 1 according to the second embodiment will be described with reference to FIG. 7 based on differences from the hydraulic control device 1 according to the first embodiment.
According to the hydraulic control device 1 of the second embodiment, the supply passage 9C2 that connects the friction element C2 and the control valve 8C2 is also provided with the on-off valve 21C2, and further, the hydraulic sensor is provided downstream of the orifice 16 in the supply passage 9C2. 22C2 is provided.

  Further, for example, the ECU 3 has a second threshold value X2 that is the same as the detected value of the hydraulic sensor 22C1 in the first embodiment with respect to the detected value of the hydraulic sensor 22C2 in the second speed non-shift state. Then, the ECU 3 controls the on-off valve 21C2 as a function of the on-off control means in the same manner as the on-off valve 21C1 in the first embodiment.

Example 3
A hydraulic control device 1 according to the third embodiment will be described with reference to FIG. 8 based on differences from the hydraulic control device 1 according to the second embodiment.
According to the hydraulic control device 1 of the third embodiment, the on-off valves 21B1, 21C1, and 21C2 have the same solenoid valve 34, and all the hydraulic chambers of the on-off valves 21B1, 21C1, and 21C2 are provided by one solenoid valve 34. The supply of the original pressure to 29 is operated. For this reason, the increase in apparatus cost by addition of the on-off valve 21 can be suppressed.

Example 4
A hydraulic control device 1 according to the fourth embodiment will be described with reference to FIGS. 9 and 10 based on differences from the hydraulic control device 1 according to the first embodiment.
The automatic transmission according to the fourth embodiment has six speeds, and five friction elements B1 to B3, C1, and C2 are provided as the friction elements 2. Further, the engagement and release states of the friction elements B1 to B3, C1, and C2 in each shift range are as shown in FIG.

Moreover, ECU3 calculates the command value of supply pressure for every friction element B1-B3, C1, and C2 as a function of a hydraulic pressure command means. The control valve 8 is provided for each of the friction elements B1 to B3, C1, and C2, and adjusts the hydraulic pressure generated by the hydraulic pressure generation source 13 to supply the friction elements B1 to B3, C1, and C2. The supply path 9 is provided for each of the friction elements B1 to B3, C1, and C2, and connects the control valve 8 and each of the friction elements B1 to B3, C1, and C2.
Whether each of the control valves 8 is an N / L type or an N / H type is as shown in FIG.

The supply passage 9B2 is also provided with an on-off valve 21B2, and a hydraulic pressure sensor 22B2 is further provided downstream of the orifice 16 in the supply passage 9B2.
Further, since the friction element B2 is engaged in both the third speed, the fifth speed, and the R range of the D range, the shuttle valve 52 is provided on the upstream side of the control valve 8B2. The forward side original pressure is supplied to the control valve 8B2 to be adjusted and supplied to the friction element B2 by the shuttle valve 52 at the third speed and fifth speed in the D range. In the R range, the reverse side original pressure is supplied to the control valve 8B2, adjusted, and supplied to the friction element B2.

  Further, since the friction element B3 is engaged when the engine brake is generated at the first speed in the D range and in the R range, the shuttle valve 53 is also provided on the upstream side of the control valve 8B3. ing. When the engine brake of the first speed in the D range is generated by the shuttle valve 53, the forward side original pressure is supplied to the control valve 8B3, adjusted, and supplied to the friction element B3. In the R range, the reverse side original pressure is supplied to the control valve 8B3, adjusted, and supplied to the friction element B3.

  Here, in the sixth speed automatic transmission, at the fifth speed, which is the high speed stage, the engagement between the engagement plates 4a and 4b is maintained by the friction element B2, and the engagement plates 4a and 4b are released by the friction element C1. Need to be maintained (see the 5th speed row in FIG. 10 (a)). Further, in order to maintain the engagement by the friction element B2 and to maintain the release by the friction element C1, it is necessary to energize the first solenoid 10 of the control valves 8B2 and 8C1 (for B2 in FIG. 10B). (See line for C1).

  Similarly, at the sixth speed, which is the high speed stage, it is necessary to maintain the engagement between the engagement plates 4a and 4b by the friction element B1 and to maintain the release of the engagement plates 4a and 4b by the friction element C1 (FIG. 10). (See the 6th speed line in (a)). Further, in order to maintain the engagement by the friction element B1 and to maintain the release by the friction element C1, it is necessary to energize the first solenoid 10 of the control valves 8B1 and 8C1 (for B1 in FIG. 10B). (See line for C1).

Therefore, in the hydraulic control apparatus 1 according to the fourth embodiment, the supply path connected to the control valves 8B1, 8B2, and 8C1 that needs to energize the first solenoid 10 at the high speed 5th and 6th speeds in the supply path 9. Only 9B1, 9B2, and 9C1 are provided with on-off valves 21B1, 21B2, and 21C1, and hydraulic sensors 22B1, 22B2, and 22C1, respectively.
The ECU 3 has threshold values similar to those in the first embodiment for the detected values of the hydraulic sensors 22B1, 22B2, and 22C1 in the fifth speed and sixth speed non-shift states. The control similar to that of the first embodiment is performed when the speed is not changed.

[Modification]
The aspect of the present invention is not limited to the embodiments, and various modifications can be considered.
For example, according to the hydraulic control apparatus 1 of the embodiment, the on-off valve 21 is a normally closed type that closes the supply path 9 when the second solenoid 23 is not energized. You may provide in the normally open type which opens the supply path 9 when there is no electricity supply to the solenoid 23.
Further, according to the hydraulic control apparatus 1 of the embodiment, the on-off valve 21 opens and closes the supply path 9 by the poppet valve 26. For example, the on-off valve 21 assumes that the supply path 9 is opened and closed by a spool valve. May be provided.

Further, according to the hydraulic control device 1 of the embodiment, the on-off valve 21 drives the poppet valve 26 to the closed side and the open side by increasing or decreasing the hydraulic pressure of the hydraulic chamber 29. Instead, the poppet valve 26 may be directly driven by the magnetic force of the second solenoid 23 or the biasing force of the spring 33.
Further, according to the on-off valve 21 of the hydraulic control apparatus 1 of the embodiment, the forward pressure is supplied to the hydraulic chamber 29. For example, the hydraulic pressure before the input to the manual valve 17 (that is, the hydraulic pressure generation) The hydraulic pressure output from the source 13 may be supplied to the hydraulic chamber 29.

DESCRIPTION OF SYMBOLS 1 Hydraulic control device 2, B1-B3, C1-C3 Friction element 3 ECU (hydraulic command means, opening / closing control means) 3a Microcomputer (hydraulic command means, opening / closing control means) 4a, 4b Engaging plate 8, 8B1-8B3, 8C1 8C3 Control valve (hydraulic pressure adjusting means) 9, 9B1 to 9B3, 9C1 to 9C3 supply path 10 First solenoid 11 First valve portion 13 Oil pressure generating source 21, 21B1, 21B2, 21C1, 21C2 Open / close valve (supply path opening / closing means) 22 , 22B1, 22B2, 22C1, 22C2 Hydraulic pressure sensor (hydraulic pressure detecting means)

Claims (11)

The friction elements (2, B1-B3, C1-C3) are controlled by controlling the hydraulic pressure supplied to each of the plurality of friction elements (2, B1-B3, C1-C3) of the automatic transmission mounted on the vehicle. In the hydraulic control device (1) for operating engagement and release between the engagement plates (4a, 4b) in
Hydraulic command means (3, 3a) for calculating a command value of the hydraulic pressure to be supplied for each of the friction elements (2, B1 to B3, C1 to C3);
A first solenoid (10) that is energized and controlled based on the hydraulic pressure command value; and a first valve portion (11) whose opening is adjusted according to the amount of energization in the first solenoid (10), Provided for each friction element (2, B1 to B3, C1 to C3), and adjusts the hydraulic pressure generated by a predetermined hydraulic pressure generation source (13) to be supplied to the friction elements (2, B1 to B3, C1 to C3) Hydraulic pressure adjusting means (8, 8B1-8B3, 8C1-8C3),
Provided for each of the friction elements (2, B1 to B3, C1 to C3), the hydraulic pressure adjusting means (8, 8B1 to 8B3, 8C1 to 8C3) and the friction elements (2, B1 to B3, C1 to C3), And the oil pressure adjusted by the oil pressure adjusting means (8, 8B1 to 8B3, 8C1 to 8C3) is supplied from the oil pressure adjusting means (8, 8B1 to 8B3, 8C1 to 8C3) to the friction element (2, B1 to B3). , C1 to C3) supply paths (9, 9B1 to 9B3, 9C1 to 9C3),
A supply path that is provided in at least one of the supply paths (9, 9B1 to 9B3, 9C1 to 9C3), is energized and controlled to open and close the supply paths (9, 9B1 to 9B3, 9C1 to 9C3) according to the energized state. Opening and closing means (21, 21B1, 21B2, 21C1, 21C2);
Oil pressure detecting means (22, 22B1, 22B2,...) For detecting oil pressure downstream of the supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2) in the supply paths (9, 9B1 to 9B3, 9C1 to 9C3). 22C1, 22C2),
Opening / closing control means for controlling energization of the supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2) based on the detected value of the hydraulic pressure detected by the oil pressure detecting means (22, 22B1, 22B2, 22C1, 22C2). 3, 3a). In the hydraulic control device (1) according to claim 1,
The supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2) closes the supply path (9, 9B1, 9B2, 9C1, 9C2) when there is no energization. ). In the hydraulic control device (1) according to claim 1 or 2,
The supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2) is generated by a second solenoid (23) energized and controlled by the opening / closing control means (3, 3a) and the second solenoid (23). A second valve portion (24) that is opened and closed according to the magnetic force, and opening and closing the supply path (9, 9B1, 9B2, 9C1, 9C2) by opening and closing the second valve portion (24),
The hydraulic control device (1), wherein the second valve portion (24) opens and closes the supply passage (9, 9B1, 9B2, 9C1, 9C2) by a poppet valve (26). In the hydraulic control device (1) according to claim 3,
The second valve portion (24) has a hydraulic chamber (29) that exerts hydraulic pressure on the closed side with respect to the poppet valve (26),
The supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2) has a high hydraulic pressure equal to or higher than the hydraulic pressure before adjustment by the hydraulic pressure adjusting means (8, 8B1 to 8B3, 8C1 to 8C3). 29) having a secondary second valve part (31) for supplying to or extracting from the hydraulic chamber (29),
The valve body (32) of the sub second valve portion (31) is provided on the side where the high hydraulic pressure is supplied to the hydraulic chamber (29) or the hydraulic chamber (29) by the magnetic force generated by the second solenoid (23). 29) The hydraulic control device (1), which is driven to the side extracted from 29) and is driven in a direction opposite to the direction of driving by the magnetic force by an urging force generated by a predetermined spring (33). . In the hydraulic control device (1) according to any one of claims 1 to 4,
Among the supply passages (9, 9B1 to 9B3, 9C1 to 9C3), the first solenoid (10) is energized to engage and release the engagement plates (4a, 4b) during high speed traveling. The supply path opening / closing means (21, 21B1, 21B2, 21C1) only to the supply paths (9, 9B1, 9B2, 9C1, 9C2) connected to the hydraulic pressure adjusting means (8, 8B1, 8B2, 8C1, 8C2) that need to be performed. , 21C2). A hydraulic control device (1). In the hydraulic control device (1) according to any one of claims 1 to 5,
In the supply path (9, 9B1, 9B2, 9C1, 9C2) provided with the supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2), the supply path opening / closing means (21, 21B1, 21B2, 21C1, The hydraulic control device (1), wherein an accumulator (50) is connected to the downstream side of 21C2). In the hydraulic control device (1) according to any one of claims 1 to 6,
The supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2) is generated by a second solenoid (23) energized and controlled by the opening / closing control means (3, 3a) and the second solenoid (23). A second valve portion (24) that is opened and closed according to the magnetic force, and opening and closing the supply path (9, 9B1, 9B2, 9C1, 9C2) by opening and closing the second valve portion (24),
The second valve part (24) opens and closes the supply path (9, 9B1, 9B2, 9C1, 9C2) by a poppet valve (26),
The second valve portion (24) has a hydraulic chamber (29) that applies hydraulic pressure to the poppet valve (26) on the closed side,
The supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2) has a high hydraulic pressure equal to or higher than the hydraulic pressure before adjustment by the hydraulic pressure adjusting means (8, 8B1 to 8B3, 8C1 to 8C3). 29) having a secondary second valve part (31) for supplying to or extracting from the hydraulic chamber (29),
The valve body (32) of the sub second valve portion (31) is driven to the side supplying the high hydraulic pressure to the hydraulic chamber (29) by the magnetic force generated by the second solenoid (23). , Driven by the biasing force generated by the predetermined spring (33), the high hydraulic pressure is pulled out from the hydraulic chamber (29),
The second valve portion (24) is provided in each of the plurality of supply paths (9, 9B1, 9B2, 9C1, 9C2),
Supply and extraction of the high hydraulic pressure to and from each of the hydraulic chambers (29) is performed by one sub second valve portion (31) and one second solenoid (23). Device (1). In the hydraulic control device (1) according to any one of claims 1 to 7,
The opening / closing control means (3, 3a) has a first threshold value (X1) for a detection value by the oil pressure detection means (22, 22B1, 22B2, 22C1, 22C2), and the detection value is the first threshold value. When larger than (X1), the supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2) closes the supply path (9, 9B1, 9B2, 9C1, 9C2), and the detected value is the first value. The supply path (9, 9B1, 9B2, 9C1, 9C2) is opened by the supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2) when the threshold value (X1) becomes smaller. Hydraulic control device (1) to perform. In the hydraulic control device (1) according to claim 8,
The friction elements (2, B1 to B3, C1 to C3) are driven by the supplied hydraulic pressure to contact one of the engagement plates (4a, 4b) and press one of the engagement plates (4a, 4b). A piston (5) to be brought into contact with the other, and a spring (6) for urging the piston (5) in a direction opposite to the direction of hydraulic drive,
The hydraulic control device (1), wherein the first threshold value (X1) is set to a numerical value that does not cause slippage between the engagement plates (4a, 4b). In the hydraulic control device (1) according to any one of claims 1 to 9,
The opening / closing control means (3, 3a) has a second threshold value (X2) for the detection value by the oil pressure detection means (22, 22B1, 22B2, 22C1, 22C2), and the detection value is the second threshold value. When smaller than (X2), the supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2) closes the supply path (9, 9B1, 9B2, 9C1, 9C2), and the detected value is the second value. The supply path (9, 9B1, 9B2, 9C1, 9C2) is opened by the supply path opening / closing means (21, 21B1, 21B2, 21C1, 21C2) when the threshold value (X2) is exceeded. Hydraulic control device (1) to perform. In the hydraulic control device (1) according to claim 10,
The friction elements (2, B1 to B3, C1 to C3) are driven by the supplied hydraulic pressure to contact one of the engagement plates (4a, 4b) and press one of the engagement plates (4a, 4b). A piston (5) to be brought into contact with the other, and a spring (6) for urging the piston (5) in a direction opposite to the direction of hydraulic drive,
The hydraulic control device (1), wherein the second threshold value (X2) is set to a numerical value at which the piston (5) does not contact one of the engagement plates (4a, 4b).

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