JP2017187079A - Hydraulic control device and controlling method thereof - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hydraulic control device capable of storing pressure of a large quantity of oil to an accumulator and discharging it even if an effective sectional area of a solenoid valve is not increased, and to provide its controlling method.SOLUTION: This invention relates to a hydraulic control device having an oil pump, a main oil passage connecting the oil pump with a transmission, a branch passage branched from the main oil passage and an accumulator 22 connected to the branch passage. The prescribed problem is solved by the hydraulic control device comprising: a control solenoid 21; and a balance valve unit 4B comprising a reference hydraulic chamber 41B, a control hydraulic chamber 42B and a balance valve body 43B. Oil flow-in passages 121a, 121b for the accumulator 22 in the branch passage are provided with a check valve 5 for preventing inverse flow and oil discharging passages 122a, 122b from the accumulator 22 are provided with the balance valve unit 4B.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a hydraulic control device applied to an automobile and a control method thereof.

  The hydraulic pressure necessary for the clutch operation of the automobile is supplied by an electric pump or an oil pump derived from engine rotation. In recent years, an increasing number of automobiles have an idling stop function in order to improve fuel efficiency and preserve the environment. However, when the engine is stopped due to idling stop, the oil pump that has been operated by the engine rotation is also stopped, and the hydraulic pressure is lowered. Then, when the engine was restarted, the clutch could not be engaged immediately, and there was a problem that hindered the start of the automobile.

  In the engine automatic stop and start device described in Patent Document 1, a check valve (63 in the same document) is provided between the oil pump and the AT hydraulic unit (clutch hydraulic unit) in order to prevent a decrease in hydraulic pressure due to the stop of the oil pump. Thus, even if the oil pump is stopped and the hydraulic pressure is lowered, the oil is prevented from being removed from the AT hydraulic unit. Further, an accumulator or an electric oil pump is provided between the oil pump and the AT hydraulic unit to maintain the hydraulic pressure.

  In the vehicle engine restart control device described in Patent Document 2, an accumulator (53 of the same document) with a solenoid switching valve (57 of the same document) is provided with an oil pump (9 of the same document) and a clutch (C1 of the same document). , C2) (see FIG. 4 of the same document). When the engine is stopped, the oil pump 9 using the engine rotation is also stopped, and the oil pressure in the oil passage is lowered. However, when the oil pump 9 is stopped, the switching valve 57 is closed to close the accumulator 53 and the oil passage, whereby the hydraulic pressure accumulated in the accumulator 53 can be maintained.

JP-A-8-14076 JP 2000-313252 A

  The engine automatic stop / start device described in Patent Document 1 is provided with a check valve so that oil does not return to the oil pump even when the oil pump is stopped, but an AT hydraulic unit (clutch hydraulic unit) is provided. Insufficient oil pressure is maintained in the oil path. In order to compensate for this, an accumulator is provided, but there is a problem that the efficiency of pressure accumulation is poor because there is no closing valve between the accumulator and the oil passage.

  The document also describes a configuration in which an electric oil pump that operates on battery power is provided instead of the accumulator. However, when an electric oil pump is provided in addition to the oil pump, there is a problem that the apparatus becomes large and heavy and the manufacturing cost increases. Furthermore, since the electric oil pump is driven, there is a problem that fuel consumption deteriorates.

  A solenoid-type switching valve is provided between the accumulator and the oil passage of the vehicle engine restart control device described in Patent Document 2. Thus, when the oil pump is stopped (when the engine is stopped), the accumulator can efficiently accumulate pressure by closing the branch path to the accumulator with the switching valve. However, in order to increase the flow rate to the accumulator with this configuration, a switching valve having a large effective area is required. When the switching valve having a large effective cross-sectional area is thus solenoidally operated, there is a problem that a large and expensive solenoid valve is required. In particular, this is a serious problem for medium-sized and larger vehicles that require a large amount of accumulated oil.

  FIG. 9 is a conceptual diagram of a pressure accumulation configuration using an accumulator described in Patent Document 2. An accumulator is provided that branches off along the oil path from the oil pump to the mission. FIG. 9A shows the oil pressure state during the steady operation of the oil pump, that is, the period during which the oil pump is operating due to engine rotation. A solenoid valve is provided on the branch path to the accumulator. Since the valve is open, the hydraulic pressure from the oil pump is accumulated in the accumulator.

  When the engine is stopped due to idling stop, the oil pump is also stopped, and the oil pressure of the oil passage to the mission is lowered. However, since the solenoid valve is closed when the engine or the oil pump is stopped, high-hydraulic oil is held in the accumulator.

  When the engine restarts, the oil pump also restarts, and the oil pressure in the oil passage toward the mission begins to recover. However, it takes several hundred milliseconds to reach a hydraulic pressure sufficient to operate the mission. Therefore, the solenoid valve is opened according to the engine restart timing, and the accumulated high-pressure oil is supplied to the oil passage to the mission. By this operation, the clutch is connected simultaneously with the engine start, and the operation of the mission is possible.

  As described above, in the method of controlling the discharge of the oil in the accumulator by opening / closing the solenoid valve, all the oil in the accumulator is discharged through the solenoid valve. Therefore, when discharging a large amount of oil in a short time, there is a problem that a solenoid valve having a large effective area must be applied.

  Therefore, an object of the present invention, that is, a technical problem to be solved, is a hydraulic control device capable of accumulating and discharging a large volume of oil to an accumulator without increasing the effective cross-sectional area of the solenoid valve, and its control It is to provide a method.

Accordingly, the invention of claim 1 is connected to an oil pump that operates as the engine rotates, a main oil passage that connects the oil pump and the transmission, a branch passage that branches from the main oil passage, and the branch passage. The hydraulic control apparatus having the accumulator includes a control solenoid, a balance valve unit including a reference hydraulic chamber, a control hydraulic chamber, and a balance valve body, and a backflow is provided in the oil inflow path to the accumulator in the branch path. Check valve is provided, and the balance valve unit is provided in the oil discharge path from the accumulator, and the control solenoid is operated to introduce and discharge high-pressure oil into the control hydraulic chamber. The balance valve body is moved by increasing / decreasing a hydraulic pressure difference between the reference hydraulic chamber and the control hydraulic chamber, and the balance valve By the hydraulic control apparatus characterized by opening and closing operations of the knit, the above-mentioned problems are eliminated.

  According to a second aspect of the present invention, in the hydraulic control device according to the first aspect, the control solenoid has three oil inlets / outlets of an A path, a B path, and a C path, and the B path and the A path. The A mode that communicates between the B road and the C road and the C mode that communicates between the B road and the C road and blocks between the B road and the A road can be switched. An electromagnetic control valve, wherein the control solenoid A path, the reference hydraulic chamber, and the downstream side of the check valve of the oil inflow channel are connected directly or via the accumulator, the control hydraulic chamber and the control When the B path of the solenoid is connected and the oil pump is in a pressurizing operation and is stopped, the control solenoid is set to the A mode, and the hydraulic pressure in the control hydraulic chamber and the reference hydraulic chamber is set. By bringing them close together, While the oil discharge passage is closed by positioning the control valve body on the closing side, immediately after the restart command to the engine, the control solenoid is set to C mode to reduce the hydraulic pressure in the control hydraulic chamber, The above-described problem has been solved by providing a hydraulic control device that opens the oil discharge passage by positioning the balance valve body on the open side.

  According to a third aspect of the present invention, in the hydraulic control device according to the first aspect, the control solenoid has three oil inlets / outlets of an A path, a B path, and a C path, and the B path and the A path The A mode that communicates between the B road and the C road and the C mode that communicates between the B road and the C road and blocks between the B road and the A road can be switched. An electromagnetic control valve, wherein the control solenoid A path, the reference hydraulic chamber, and the downstream side of the check valve of the oil inflow channel are connected directly or via the accumulator, the control hydraulic chamber and the control By configuring the solenoid B path to be connected, when the oil pump is in a pressurizing operation and when it is stopped, the control solenoid is set to C mode to reduce the hydraulic pressure in the control hydraulic chamber. , The balance valve body on the closed side The oil discharge path is closed and immediately after the restart command to the engine, the control solenoid is set to the A mode, and the hydraulic pressures in the control hydraulic pressure chamber and the reference hydraulic pressure chamber are brought close to each other, The above-described problem has been solved by providing a hydraulic control device in which the oil discharge passage is opened by positioning the balance valve body on the open side.

  According to a fourth aspect of the present invention, in the hydraulic control device according to the second aspect, the downstream flow path of the oil discharge path is sandwiched between the reference hydraulic chamber and the control hydraulic chamber, and the reference hydraulic chamber and the control hydraulic chamber A partition having a communication port to the downstream flow path is provided between the downstream flow paths of the oil discharge path, and the balance valve is provided between the downstream flow path of the oil discharge path and the control hydraulic chamber. An insertion hole is provided through which the body is inserted, the balance valve body is movably inserted through the insertion hole, an O-ring is provided on a side of the balance valve body, and the control hydraulic chamber of the balance valve body is provided. A disc-shaped piston is fixed to the balance valve body, and a conical or columnar communication closing portion is provided on the reference hydraulic chamber side of the balance valve body, and the communication closing portion flows downstream of the oil discharge passage. By inserting into the communication port to the road, the balance bar In the balance valve body, the oil pump is pressurized and configured so that the effective cross-sectional area on the communication closing part side is smaller than the effective cross-sectional area on the piston side. When the control valve is in the A mode and the control solenoid is in the A mode, the oil pressure in the control hydraulic chamber and the reference hydraulic chamber are brought close to each other so that the balance valve body is positioned on the closed side and the oil While closing the discharge passage, immediately after the restart command to the engine, the control solenoid is set to C mode to lower the hydraulic pressure in the control hydraulic chamber, thereby positioning the balance valve body on the open side and The above problems have been solved by employing a hydraulic control device characterized by opening the oil discharge passage.

  According to a fifth aspect of the present invention, in the hydraulic control device according to the second aspect, the oil inflow path is defined as an inflow upper flow path near the main oil path with the check valve provided between the oil inflow paths as a boundary. The accumulator side is referred to as an inflow lower flow path, and the oil discharge path is referred to as the discharge upper flow path with the balance valve unit provided between the oil discharge paths as a boundary. This is called a discharge lower flow path, and the inflow lower flow path and the discharge upper flow path are shared by one oil path and connected to the accumulator, and the balance valve body is movable between the reference hydraulic pressure chamber and the control hydraulic pressure chamber. The reference hydraulic chamber is connected to the inflow lower flow path and the discharge upper flow path, the inflow upper flow path and the discharge lower flow path that are shared by one oil path, and the balun The oil inflow passage having the check valve structure is formed inside the valve body, and an inflow passage outlet is formed at an end of the balance valve body on the side of the reference hydraulic pressure chamber so as to communicate with the lower inflow passage. In addition, an inflow passage inlet is provided at a side portion of the balance valve body and is connected to the inflow upper flow path. In the balance valve body, an effective disconnection formed by the end portion on the reference hydraulic chamber side and the check valve is formed. By forming the area smaller than the effective cross-sectional area of the end of the balance valve body in the control hydraulic chamber, the control solenoid is operated when the oil pump is in a pressurizing operation and stopped. As the A mode, by bringing the hydraulic pressures of the control hydraulic chamber and the reference hydraulic chamber close to each other, the balance valve element is moved to the reference hydraulic chamber side to close the oil discharge path, while Immediately after the restart command The hydraulic control is characterized in that the control solenoid is set to the C mode, and the oil pressure in the control hydraulic chamber is lowered to move the balance valve body closer to the control hydraulic chamber to open the oil discharge path. By using the apparatus, the above-mentioned problems have been solved.

  According to a sixth aspect of the present invention, in the hydraulic control apparatus according to the third aspect, the oil inflow path is defined as an inflow upper flow path near the main oil path with the check valve provided between the oil inflow paths as a boundary. The accumulator side is referred to as an inflow lower flow path, and the oil discharge path is referred to as the discharge upper flow path with the balance valve unit provided between the oil discharge paths as a boundary. Referred to as a discharge lower flow path, the inflow lower flow path and the discharge upper flow path are shared by one oil passage, the inflow upper flow path and the discharge lower flow path are shared by one oil passage, and the check valve structure is provided. An oil inflow path is formed in the reference hydraulic chamber, the balance valve body is configured to pass through an insertion hole between the reference hydraulic chamber and the control hydraulic chamber, and an O-ring is provided on a side portion of the balance valve body. Establishment A piston is provided at the end of the balance valve body and at the end of the control hydraulic chamber, and the balance valve body moves to the reference hydraulic chamber side by receiving hydraulic pressure from the piston. When the oil pump is in a pressurizing operation by configuring the check valve to be open and forming an effective cross-sectional area where the piston receives hydraulic pressure larger than an effective cross-sectional area of the check valve. When stopped, the control solenoid is set to C mode to reduce the hydraulic pressure in the control hydraulic chamber, thereby reducing the force with which the balance valve body opens the check valve and closing the oil discharge passage. On the other hand, immediately after the restart command to the engine, the control solenoid is set to the A mode, and a part of the oil accumulated in the accumulator is introduced into the control hydraulic chamber to perform the control. By increasing the hydraulic pressure of the pressure chamber, the hydraulic pressure of the control hydraulic chamber is a force pushing the piston, and the hydraulic control device is configured to open the check valve and open the oil discharge path. Solved the above problem.

  According to a seventh aspect of the present invention, in the hydraulic control device according to the third or sixth aspect, the check valve includes a push-back valve body, and the push-back valve body is opposite to an oil inflow direction to the accumulator. It is composed of a compression urging spring that urges in the direction. On the other hand, the end of the balance valve body, the end on the side of the reference hydraulic chamber is formed as a protrusion, and contacts the push-back valve body. The above-mentioned problem has been solved by employing a hydraulic control device having a configuration in which the push-back valve body has a higher hardness than the projecting portion.

The invention according to claim 8 is connected to the oil pump that operates as the engine rotates, a main oil passage that connects the oil pump and the transmission, a branch passage that branches from the main oil passage, and the branch passage A hydraulic control apparatus having an accumulator includes a control solenoid, a reference hydraulic chamber, a control hydraulic chamber, and a balance valve unit including a balance valve body, and prevents backflow in an oil inflow path to the accumulator in the branch path. A check valve is provided, and the balance valve unit is provided in the oil discharge path from the accumulator. The control solenoid is operated to introduce and discharge high-pressure oil into the control hydraulic chamber. The balance valve body is moved by increasing / decreasing the hydraulic pressure difference between the reference hydraulic chamber and the control hydraulic chamber, and the balance valve By the hydraulic control method characterized by opening and closing the knit, the above-mentioned problems are eliminated.

  The invention according to claim 9 is the hydraulic control method according to claim 8, wherein the control solenoid has three oil inlets / outlets of A path, B path and C path, and between the B path and the A path. Electromagnetic control capable of switching between the A mode for communicating and blocking between the B path and the C path, and the C mode for communicating between the B path and the C path and blocking between the B path and the A path A valve A, the reference hydraulic chamber, and the downstream side of the check valve of the oil inflow passage are connected directly or via the accumulator, and the control hydraulic chamber and the control solenoid In the configuration in which the B path is connected, when the oil pump is in a pressurizing operation and when it is stopped, the control solenoid is set to the A mode, and the hydraulic pressures in the control hydraulic chamber and the reference hydraulic chamber are set to each other. By bringing them close together, the balance While the body is positioned on the closed side and the oil discharge passage is closed, immediately after the restart command to the engine, the control solenoid is set to C mode to reduce the hydraulic pressure in the control hydraulic chamber, thereby reducing the balance. The above problem has been solved by employing a hydraulic control method in which the oil discharge passage is opened by positioning the valve body on the open side.

  The invention according to claim 10 is the hydraulic control method according to claim 8, wherein the control solenoid has three oil inlets / outlets of A path, B path and C path, and between the B path and the A path. Electromagnetic control capable of switching between the A mode for communicating and blocking between the B path and the C path, and the C mode for communicating between the B path and the C path and blocking between the B path and the A path A valve A, the reference hydraulic chamber, and the downstream side of the check valve of the oil inflow passage are connected directly or via the accumulator, and the control hydraulic chamber and the control solenoid When the oil pump is in a pressurizing operation and stopped when the path B is connected, the control solenoid is set to C mode to reduce the hydraulic pressure in the control hydraulic chamber, thereby Position the balance valve on the closed side While closing the oil discharge passage, immediately after the restart command to the engine, the control solenoid is set to the A mode, and a part of the oil accumulated in the accumulator is introduced into the control hydraulic chamber. By making the oil pressure in the control hydraulic chamber and the reference hydraulic chamber close to each other, the hydraulic pressure control method is characterized in that the balance valve body is positioned on the open side and the oil discharge path is opened. Solved the problem.

  According to an eleventh aspect of the present invention, in the hydraulic control method according to the ninth aspect, the controller includes a controller that controls the control solenoid, and the operation and stop states of the engine or the oil pump are recorded in a memory of the controller. A current flag and a past flag are provided, the past flag is set in advance, and the control solenoid is set to the A mode in advance, and the current flag is set every time the operation of the engine or the oil pump is confirmed. If the engine or the oil pump is operating, the current flag is bit-set and if stopped, the bit is reset, if the past flag is bit-reset and the current flag is bit-set , While setting the control solenoid to C mode to open the discharge path, If the past flag is not reset and the current flag is not set, the control solenoid is set to A mode, the discharge passage is closed, and the operation of the engine or the oil pump is confirmed again. Previously, the above problem was solved by adopting a hydraulic control method characterized by updating the past flag with the contents of the current flag.

  According to a twelfth aspect of the present invention, in the hydraulic control method according to the tenth aspect, the controller includes a controller that controls the control solenoid, and the operation and stop states of the engine or the oil pump are recorded in a memory of the controller. A current flag and a past flag are provided, the past flag is set in advance, and the control solenoid is set in the C mode in advance, and the current flag is set every time the operation of the engine or the oil pump is confirmed. If the engine or the oil pump is operating, the current flag is bit-set and if stopped, the bit is reset, if the past flag is bit-reset and the current flag is bit-set While setting the control solenoid to A mode and opening the discharge passage, If the past flag is not bit reset and the current flag is not set, the control solenoid is set to C mode, the discharge passage is closed, and the operation of the engine or the oil pump is confirmed again. Previously, the above problem was solved by adopting a hydraulic control method characterized by updating the past flag with the contents of the current flag.

  According to the first aspect of the present invention, the oil pressure in the accumulator is controlled by opening and closing the balance valve unit by controlling the hydraulic pressure in the control hydraulic chamber via the control solenoid. Therefore, a solenoid valve having an effective area smaller than that in which the oil in the accumulator is directly controlled by the solenoid valve can be applied as the control solenoid. Therefore, there is an effect that the hydraulic control device can be manufactured in a compact and low cost by downsizing the solenoid valve.

  According to the invention of claim 2, there is an effect that the hydraulic pressure can be controlled by a simple control method in which the solenoid is configured to have an A mode and a C mode, and the both modes are interlocked with the operation state of the oil pump. In the invention of claim 3, the solenoid is configured to have an A mode and a C mode, and there is an effect that the hydraulic pressure can be controlled by a simple control method in which both modes are linked with the operation state of the oil pump.

  In the invention of claim 4, since the simple balance valve body structure is used, the effective cross-sectional area on the control hydraulic chamber side is easily made larger than the effective cross-sectional area on the reference hydraulic chamber side. The balance valve unit can be opened / closed. According to the invention of claim 5, since the check valve structure of the oil inflow passage is built in the balance valve body, there is an effect that a compact hydraulic control device can be obtained.

  According to the sixth aspect of the invention, the simple balance valve body structure can be used to make the effective sectional area on the control hydraulic chamber side larger than the effective sectional area on the reference hydraulic chamber side. The balance valve unit can be opened / closed. In the seventh aspect of the invention, the durability and reliability of the sealing performance of the check valve can be improved by forming the push-back valve body with higher hardness than at least the protruding portion of the balance valve body. . As a result, it has the effect of improving the durability and reliability of the hydraulic control device.

  According to the eighth aspect of the invention, there is an effect that the large-capacity high-pressure oil accumulated in the accumulator can be controlled by introducing and discharging the high-pressure oil into the control hydraulic chamber. According to the ninth aspect of the present invention, it is possible to control the large-capacity high-pressure oil accumulated in the accumulator only by switching the mode of the control solenoid. In the invention of claim 10, there is an effect that the large-capacity high-pressure oil accumulated in the accumulator can be controlled only by switching the mode of the control solenoid.

  The invention according to claim 11 is advantageous in that the mode of the control solenoid can be appropriately switched and controlled by managing the current flag and the past flag that record the operation and stop state of the engine or the oil pump. In the twelfth aspect of the present invention, there is an effect that the mode of the control solenoid can be appropriately switched and controlled by managing the current flag and the past flag that record the operation and stop state of the engine or the oil pump.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a first embodiment of a hydraulic control apparatus according to the present invention, where (A) is a diagram illustrating a state of hydraulic pressure during steady operation of an oil pump, (B) is a diagram illustrating a hydraulic pressure state when idling is stopped, C) is a diagram showing a state of hydraulic pressure immediately after a restart command to the engine. FIG. 2 is a block diagram of a hydraulic control device of the present invention. Fig. 4 shows the relationship between the engine operating state, the control solenoid mode, the control solenoid communication / cutoff state, the hydraulic pressure difference between the reference hydraulic chamber and the control hydraulic chamber, and the discharge path closing / opening state according to the BBU according to the hydraulic control device of the present invention. FIG. These are examples of the flow which CPU which comprises the controller which concerns on the hydraulic control apparatus of this invention processes. (A) is a figure which shows the state of the hydraulic pressure in the steady operation of an oil pump, (B) is a figure which shows the state of the hydraulic pressure at the time of idling stop, (C) is a view showing the state of hydraulic pressure immediately after a restart command to the engine, and (D) is an enlarged view of the downstream flow path. (A) is a figure which shows the state of the oil_pressure | hydraulic in the steady operation of an oil pump, (B) is a figure which shows the state of the oil_pressure | hydraulic at the time of idling stop, FIG. C) is a diagram showing a state of hydraulic pressure immediately after a restart command to the engine. (A) is a figure which shows the state of the oil_pressure | hydraulic in the steady operation of an oil pump, (B) is a figure which shows the state of the oil_pressure | hydraulic at the time of idling stop, C) is a diagram showing a state of hydraulic pressure immediately after a restart command to the engine. These are the examples of the flow which CPU which comprises a controller processes in 4th Embodiment which concerns on the hydraulic control apparatus of this invention. FIG. 4A is an example of a conventional hydraulic control device, FIG. 3A is a diagram illustrating a state of hydraulic pressure during steady operation of an oil pump, FIG. 4B is a diagram illustrating a state of hydraulic pressure when idling is stopped, and FIG. It is a figure which shows the state of the hydraulic pressure immediately after the restart command to.

[First Embodiment]
Based on FIGS. 1-8, embodiment is described as an example of the hydraulic control apparatus which concerns on this invention. FIG. 2 is a block diagram of the hydraulic control apparatus of the present invention. The hydraulic control apparatus according to the present invention includes an oil pump 1 that operates by rotation of an engine 81, a main oil passage 11 that transmits oil generated by the oil pump 1 to a mission 82, the oil pump 1 and the mission 82. And a controller 3 that controls a control solenoid 21 included in the pressure accumulating unit 2. The accumulator 2 also includes an accumulator 22.

  The controller 3 includes a CPU 31, a memory 32, and an I / O interface 33. These elements are electrically connected by a data bus. The memory 32 has a program area for holding a program for causing the CPU 31 to perform an operation, and a work area necessary for the operation process. The I / O interface 33 inputs at least a steady operation state of the engine 81 or the oil pump 1, an idling stop state, and a state signal 811 of the oil pump 1 indicating the restart timing to the CPU 31 and controls the control solenoid 21. This is an interface for outputting a control signal 331 to be transmitted. The control solenoid 21 is an electromagnetic control valve that controls opening and closing of the valve with an electromagnet.

  FIG. 1 is a first embodiment of a hydraulic control apparatus according to the present invention, in which (A) is a diagram showing the configuration and the state of hydraulic pressure during steady operation of the oil pump, and (B) is the same configuration and when idling is stopped. The figure which shows the state of oil_pressure | hydraulic, (C) is a figure which shows the state of the oil_pressure | hydraulic immediately after the restart command to the same structure and the engine and the engine 81. However, the description of the engine 81 and the controller 3 is omitted.

Hereinafter, in the description, the oil passage is connected means that the pipe as the oil passage is joined, and the communication means that the oil flows without being blocked by a valve body or the like. It shall mean a state that can In the accumulator 22, the main oil passage 11, the branch passage 12, the inflow passage 121, the discharge passage 122, the reference hydraulic chamber 41, and the control hydraulic chamber 42, the hatched portions are accumulated in the oil pump 1 or the accumulator 22. This is a region where high oil pressure is maintained by the oil that is present. It is assumed that the high hydraulic pressure is approximately the pressure P. Further, a low pressure is generally the pressure P _0.

  The configuration of the first embodiment of the hydraulic control device of the present invention will be described based on FIGS. The hydraulic control device is connected to an oil pump 1 that operates as the engine 81 rotates, a main oil passage 11 that connects the oil pump 1 and the transmission 82, and a branch passage 12 that branches from the main oil passage 11. The hydraulic control device has an accumulator 22. The branch path 12 includes an inflow path 121 (inflow upper flow path 121a, inflow lower flow path 121b) and a discharge path 122 (discharge upper flow path 122a, discharge lower flow path 122b).

The pressure accumulating unit 2 includes the accumulator 22, the inflow passage 121 having the check valve 5, the discharge passage 122 having the balance valve unit 4 (hereinafter referred to as BBU 4), and the control solenoid 21. Is done. In the figure, it is assumed that the pressure in the oil passage with hatching is a high pressure and is generally the pressure P. Further, oil passages not shaded is assumed to be approximately the pressure P ₀ at low pressure.

  The check valve 5 is a valve that prevents backflow of oil. For example, the flow path can be closed by a push-back valve body 51 (see FIG. 1B) urged by a compression urging spring 52 in the reverse direction of the forward direction of the oil flow. With this configuration, the push-back valve body 51 blocks the flow path against oil that flows backward to prevent backflow. For forward oil, if a hydraulic pressure that generates a force stronger than the sum of the hydraulic pressure on the downstream side of the push-back valve body 51 and the repulsive force (referred to as g) of the compression biasing spring 52 is applied, A road can be secured (see FIG. 1A). In FIG. 1, the push-back valve body 51 is represented by a sphere, but the present invention is not limited to this.

  In the example of the hydraulic control apparatus, the inflow path 121 and the discharge path 122 are joined and then connected to the accumulator 22. More specifically, the inflow lower flow path 121b and the discharge upper flow path 122a are connected to the accumulator 22 in a joined state. The inflow path 121 may also be referred to as an oil inflow path, and the discharge path 122 may be referred to as an oil discharge path. These inflow lower flow path 121b and discharge upper flow path 122a may be separately connected to the accumulator 22. The oil pressurized by the oil pump 1 flows into the accumulator 22 via the main oil path 11 and the inflow path 121. At this time, the pressure accumulation piston 222 moves in the direction of expanding the volume of the accumulator 22 and compresses the pressure accumulation compression spring 221. Pressure is accumulated in the accumulator 22 as a repulsive force of the pressure-accumulating compression spring 221.

  Between the accumulator 22 and the main oil passage 11, an inflow passage 121 and a discharge passage 122 exist. The inflow path 121 is referred to as the inflow lower flow path 121b near the accumulator 22 and the inflow upper flow path 121a (see FIG. 1B) near the accumulator 22 with the check valve 5 provided therebetween as a boundary. The discharge path 122 is referred to as the discharge upper flow path 122a near the accumulator 22, and the main oil path 11 is referred to as the discharge lower flow path 122b, with the BBU 4 provided therebetween as a boundary.

  The BBU 4 has a reference hydraulic chamber 41 and a control hydraulic chamber 42 and incorporates a balance valve element 43. The control solenoid 21 has an A path, a B path, and a C path that are oil outlets, and is controlled by the controller 3 so that the B path and the A path are communicated and the B path and the C path are shut off. Then, it is possible to switch to at least two modes of the C mode in which the B road and the A road are blocked and the B road and the C road are communicated. The controller 3 operates the control solenoid 21 to increase / decrease the hydraulic pressure in the control hydraulic chamber 42 and change the hydraulic pressure difference between the reference hydraulic chamber 41 and the control hydraulic chamber 42, thereby moving the balance valve element 43, so that the BBU 4 Open and close.

Specifically, the accumulator 22, the downstream side of the check valve 5, the reference hydraulic chamber 41, and the A path of the control solenoid 21 are connected. The control hydraulic chamber 42 is connected to the B path of the control solenoid 21. Further, the tip of the C path of the control solenoid 21 leads to the oil return 83. A return oil path from the mission 82 on the upstream side of the oil pump 1 also leads to the oil return 83. It can be assumed that there is no hydraulic pressure pressurized by the oil pump 1 in the oil passage leading to the oil return 83. The oil the pressure in the oil passage that communicates with the return 83 as an oil was present has a low pressure and P _0.

  With the above configuration, the hydraulic pressure in the reference hydraulic chamber 41 constantly matches the hydraulic pressure in the accumulator 22. On the other hand, the hydraulic pressure in the control hydraulic chamber 42 can be controlled by selecting the state of the control solenoid 21 to the A mode or the C mode. First, when the control solenoid 21 is set to the A mode, the A path and the B path communicate with each other. Therefore, in principle, the hydraulic pressure in the control hydraulic chamber 42 is equal to the hydraulic pressure in the reference hydraulic chamber 41.

On the other hand, when the control solenoid 21 is set to the C mode, the B path and the A path are cut off, and the B path and the C path are communicated, whereby the hydraulic pressure in the control hydraulic chamber 42 is discharged and the reference hydraulic chamber 41 is discharged. In contrast, the hydraulic pressure is low. By operating the control solenoid 21 in this way, the hydraulic pressure in the control hydraulic chamber 42 can be increased or decreased. For example, the high hydraulic pressure P can be set, or the low hydraulic pressure P ₀ can be set. The operation of the control solenoid 21 is performed under the control of the controller 3.

[First Embodiment: During steady operation of oil pump 1]
First, an operation during the steady operation of the oil pump 1, that is, when the oil pump 1 is operating and pressurizing oil will be described with reference to FIG. During the steady operation of the oil pump 1, the control solenoid 21 is set to the A mode. With this control, the hydraulic pressure in the control hydraulic chamber 42 becomes substantially the same as the hydraulic pressure in the reference hydraulic chamber 41. The balance valve body 43 is movably inserted between the reference hydraulic chamber 41 and the control hydraulic chamber 42, but is sealed by an O-ring 432 so that the oils are not mixed with each other.

  Further, in the balance valve body 43, the effective sectional area Sa of the surface 431a that receives the hydraulic pressure in the reference hydraulic chamber 41 is formed smaller than the effective sectional area Sb of the surface 431b that receives the hydraulic pressure in the control hydraulic chamber 42. (See FIG. 1C). That is, Sa <Sb. When the hydraulic pressure in the reference hydraulic chamber 41 and the control hydraulic chamber 42 is P, the force that pushes the balance valve body 43 from the reference hydraulic chamber 41 toward the control hydraulic chamber 42 is Fa = P × Sa. On the other hand, the force pushing the balance valve body 43 from the control hydraulic chamber 42 toward the reference hydraulic chamber 41 is Fb = P × Sb.

  Then, since Fa <Fb, the balance valve body 43 is pushed and moved to the reference hydraulic chamber 41 side by the force Fb-Fa, and comes into contact with the movement restricting member 44a (see FIG. 1A) and is stationary. The BBU 4 is designed to close the discharge passage 122 at the position of the balance valve body 43 at this time. On the other hand, the oil pressurized by the oil pump 1 moves the spherical pushback valve body 51 of the check valve 5, so that the inflow path 121 has an inflow area. With the above configuration, the oil flows into the accumulator 22 up to the upper limit pressure and is accumulated. Note that the mark X in C of the control solenoid 21 indicates that the C path is disconnected from the B path.

[First embodiment: When idling is stopped]
Next, the operation when idling is stopped will be described with reference to FIG. When the engine is temporarily stopped, the pressurizing operation of the oil pump 1 is also stopped. In principle, the hydraulic pressure in the main oil passage 11 is reduced to a low hydraulic pressure P ₀ (for example, atmospheric pressure). The check valve 5 closes the inflow path 121 due to the repulsive force of the compression urging spring 52 and the force accompanying the pressure in the accumulator 22.

  Further, the control of the control solenoid 21 is the same as that during the steady operation of the oil pump 1, and the A path and the B path are communicated, and the C path remains blocked. As a result, the hydraulic pressure in the control hydraulic chamber 42 is maintained at a hydraulic pressure equivalent to that in the reference hydraulic chamber 41, and the closed state of the discharge passage 122 is maintained by the operation of the balance valve body 43 similar to the above. As a result, the accumulator 22 holds the oil accumulated during the steady operation of the oil pump 1 together with the pressure. Note that the mark X in C of the control solenoid 21 indicates that the C path is disconnected from the B path.

[First Embodiment: Immediately after a restart command to the engine]
Next, the operation immediately after the restart command to the engine 81 will be described with reference to FIG. The oil pump 1 also restarts with the engine restart, but the oil pressure in the main oil passage 11 has not yet recovered immediately after the order of several hundred milliseconds from the start command. At this time, the controller 3 sets the control solenoid 21 in the C mode, blocks the B path from the A path, and connects the B path and the C path. As a result, the high pressure oil in the control hydraulic chamber 42 is discharged to the oil return 83.

  Then, Fa becomes dominant among the forces acting on the balance valve body 43 described above, and the balance valve body 43 moves to the control hydraulic pressure chamber 42 side and comes into contact with the movement restricting member 44b and stops. By this operation, the discharge upper flow path 122a and the discharge lower flow path 122b communicate with each other. As a result, the high hydraulic oil accumulated in the accumulator 22 is discharged to the main oil passage 11 through the discharge passage 122, and the lack of pressurization by the oil pump 1 is compensated.

  Note that the mark “A” in A of the control solenoid 21 indicates that the A path is blocked from the B path. In the example of FIG. 1, the movement restricting members 44a and 44b restrict the movement range of the balance valve element 43, but the balance valve element 43 has a reference hydraulic chamber side section 431a or a control hydraulic chamber side section 431b. The movement range may be regulated by urging with a compression spring or a tension spring.

[First embodiment: During steady operation of the oil pump 1 again]
The above is the situation of several hundred milliseconds immediately after the restart command to the engine 81. After that, the pressurized oil from the oil pump 1 is supplied, and the oil pump 1 returns to the state during steady operation. At this time, the control solenoid 21 is in the A mode under the control of the controller 3. That is, the B road is communicated with the A road by blocking the C road. As a result, the balance valve body 43 moves again to the reference hydraulic chamber 41 side and closes the discharge lower flow path 122b. Then, the oil pump 1 returns to the state during the steady operation shown in FIG. 1A, and the oil pressurized by the oil pump 1 is accumulated in the accumulator 22 through the inflow passage 121.

[First Embodiment: Processing Flow by Controller]
Next, processing of the controller 3 for performing the above operation will be described. As described above, the controller 3 has the CPU 31, and the CPU 31 controls the control solenoid 21 according to the processing flow shown in FIG. When the switch of the electric system of the automobile is connected, the controller 3 also starts operation. In order to prevent malfunction when the power is turned on, a “past flag” regarding the engine 81 or the pump operation is bit-set (Step 1). The “past flag” is a flag for recording a state of whether the engine 81 is operating or stopped, and at least one bit of the bit set and reset may be secured in the work area of the memory 32.

“The past flag” is set to a bit is a flag indicating that the engine 81 or the oil pump 1 was operating when the operation status of the engine 81 or the oil pump 1 was confirmed. However, since it is an initial setting here, it is assumed that bits are set for convenience. Then, the control solenoid 21 is set to the A mode. That is, the B road and the A road are communicated, and the B road and the C road are blocked (Step 2). This is an operation for making the hydraulic pressure in the control hydraulic chamber 42 coincide with the hydraulic pressure in the reference hydraulic chamber 41. In addition, necessary initial settings are performed (Step 3). The controller power supply is checked (Step 4). As a result, if the power is turned off (if it is OFF), the processing is branched to “end” as “true” (Step 5). If the power is not turned off, the processing after Step 6 is performed as “false”.

  It is checked whether the engine 81 or the oil pump 1 is operating or stopped via the state signal 811 of the engine 81 or the oil pump 1. If it is operating, the "current flag" relating to engine operation is set, and if it is stopped, it is reset. As for the “current flag”, at least one bit of set and reset may be secured in the work area of the memory 32 as in the case of the “past flag” (Step 6). Subsequently, it is checked whether the “past flag” is set or reset (Step 7).

Referring to “past flag” and “current flag”, if “past flag is reset” and “current flag is set”, proceed to Step 9 as “true”, otherwise as “false” It progresses to Step10 (Step8). Step 8 is a processing example for detecting a state immediately after a restart command to the engine 81.

  If the condition branch of Step 8 is “true”, the state is immediately after the restart command to the engine 81, and therefore, the process proceeds to Step 9, and the control solenoid 21 is set to the C mode. That is, the B road is blocked from the A road, and the B road and the C road are communicated. This discharges the high-pressure oil in the control hydraulic chamber 42 through the C path, and the hydraulic pressure in the control hydraulic chamber 42 decreases, so the balance valve element 43 releases the discharge path 122 from closing. As a result, the high-pressure oil accumulated in the accumulator 22 is discharged to the main oil passage 11.

  On the other hand, if the condition branch of Step 8 is “false”, it is during steady operation or at the time of idling stop, so the process proceeds to Step 10 and the A mode of the control solenoid 21 is maintained. That is, the B road is cut off from the C road, and the B road and the A road are communicated. By this operation, the discharge passage 122 is kept closed.

  Step 10 is performed both during the steady operation of the oil pump 1 and when idling is stopped. That is, the discharge path 122 is maintained in a closed state, and the inflow path 121 is controlled by the check valve 5. During the steady operation of the oil pump 1, the oil pump 1 moves the push-back valve body 51 of the check valve 5 to the downstream side by the force accompanying the oil pressure of the main oil passage 11, and the oil flows into the accumulator 22. At the time of idling stop, the oil pressure of the main oil passage 11 and the inflow upper flow passage 121a is reduced by stopping the oil pump 1, so the inflow passage 121 is also closed, and the accumulated pressure and oil in the accumulator 22 are maintained as they are.

  After executing Step 9 or Step 10, Step 11 updates the “Past Flag” with the value of “Current Flag” and returns to Step 4 to check the controller power supply. Thereafter, Step 4 to Step 11 are repeated until the controller 3 is turned off. As described above, the flowchart shown in FIG. 4 shows basic processing. For example, the time until the discharge of the oil accumulated in the accumulator 22 is completed is secured between Step 4 and Step 11. It is also possible to include a waiting time process for adjusting the time.

  FIG. 3 shows the operating state of the engine and the oil pump, the mode of the control solenoid 21 and the communication state of the oil passage, the hydraulic pressure difference between the two hydraulic chambers of the reference hydraulic chamber 41 and the control hydraulic chamber 42, and the closing / opening of the discharge passage 122 by BBU4. Summarize state relationships. First, there are three operating states of the oil pump in the left column, during the steady operation of the oil pump 1, when idling is stopped, and immediately after the engine restart command. Among these, the control solenoid 21 during the steady operation of the oil pump and at the time of idling stop is set to the A mode by the controller 3 so that the B path and the A path are communicated and the B path and the C path are blocked. Thereby, the hydraulic pressure difference between the reference hydraulic chamber 41 and the control hydraulic chamber 42 becomes zero or small, and the discharge passage 122 is closed by the balance valve body 43 of the BBU 4.

  Immediately after the engine restart command, the controller 3 causes the control solenoid 21 to enter the C mode. That is, the B road and the A road are blocked, and the B road and the C road are communicated. As a result, the hydraulic pressure in the control hydraulic chamber 42 decreases, and the hydraulic pressure difference from the reference hydraulic chamber 41 increases. As a result, the balance valve body 43 of the BBU 4 moves to the opening position, and the discharge path 122 is opened.

  The BBU 4 according to the first embodiment closes and opens the discharge oil passage 122 by moving the balance valve body 43 by the difference in force generated in accordance with the hydraulic pressure difference between the reference hydraulic chamber 41 and the control hydraulic chamber 42. . For example, the capacity of the control hydraulic chamber 42 is set to 1/5 of the capacity of the accumulator 22. Then, the control solenoid 21 can be configured by an electromagnetic valve having an effective cross-sectional area that is 1/5 of the effective cross-sectional area of the BBU 4 that discharges the accumulated high-pressure oil to the accumulator 22. That is, there is an effect that a valve having a sectional area of five times can be effectively controlled by using a solenoid having a small sectional area (control solenoid 21).

[Second Embodiment]
Next, based on FIG. 5, the structure and operation | movement of 2nd Embodiment of the hydraulic control apparatus of this invention are demonstrated. Since the form of the mission 82, the oil return 83, and the oil pump 1 is the same as that of the first embodiment, the description and description on the drawing are omitted. The hydraulic control apparatus is configured such that a downstream flow path 122c connected to a discharge lower flow path 122b is sandwiched between a reference hydraulic pressure chamber 41A and a control hydraulic pressure chamber 42A (see FIGS. 5B and 5D). A partition wall 45 having a communication port 45a to the downstream channel 122c is provided between the reference hydraulic chamber 41A and the downstream channel 122c. An insertion hole 46A for inserting the balance valve body 43A is provided between the discharge lower flow path 122b and the control hydraulic chamber 42A, and the balance valve body 43A is movably inserted through the insertion hole 46A.

  The reference hydraulic chamber 41A is connected to the accumulator 22 via the inflow lower flow path 121b (discharge upper flow path 122a). The A path of the control solenoid 21 is also connected to the accumulator 22 by the inflow lower flow path 121b (discharge upper flow path 122a). The control hydraulic chamber 42A is connected to the B path of the control solenoid 21 through an oil path. Further, the C path of the control solenoid 21 is connected to the oil return 83.

  An O-ring 432 is provided on the side of the balance valve body 43A, and is sealed so that oil in the control hydraulic chamber 42A does not leak into the discharge lower flow path 122b. A disk-like piston 434A is fixed to the balance valve body 43A on the control hydraulic chamber 42A side. A conical communication closing part 435 is provided on the reference hydraulic chamber 41A side of the balance valve body 43A (see FIG. 5A). The discharge passage 122 (122a and 122b) is closed by fitting the communication closing portion 435 into the communication port 45a. Here, in the balance valve body 43A, the effective cross-sectional area Sa on the communication closing portion 435 side is configured to be smaller than the effective cross-sectional area Sb on the piston 434A side. That is, Sa <Sb. In the hydraulic control apparatus, the effective cross-sectional area Sa on the communication closing portion 435 side is the cross-sectional area of the communication port 45a.

[Second Embodiment: During steady operation of oil pump 1]
First, based on FIG. 5 (A), the operation of the hydraulic control apparatus during the steady operation of the engine 81 and the oil pump 1 will be described. The control solenoid 21 during steady operation is in the A mode. Then, as described above, the B path and the A path communicate with each other and the C path is blocked, so that the control hydraulic chamber 42A has a hydraulic pressure P substantially equal to the reference hydraulic chamber 41A. Then, the force by which the hydraulic pressure in the reference hydraulic chamber 41A moves the balance valve body 43A toward the control hydraulic chamber 42A is Fa = P × Sa. On the other hand, the force with which the hydraulic pressure in the control hydraulic chamber 42A fits the balance valve body 43A into the communication port 45a is Fb = P × Sb.

  As described above, since Sa <Sb, Fa <Fb. However, the repulsive force f of the push-back compression spring 433a is in the same direction as Fa. Therefore, the effective sectional area Sb on the piston 434A side is formed to be sufficiently larger than the sectional area Sa of the communication port 45a so as to satisfy (Fa + f) <Fb. Then, the control solenoid 21 is set to the A mode, and the pressure Fb-Fa-f is applied to the balance valve body 43A by setting the hydraulic pressure of the control hydraulic chamber 42A to the same pressure as the hydraulic pressure P of the reference hydraulic chamber 41A. it can.

  With this force, the communication closing portion 435 of the balance valve body 43A can be fitted into the communication port 45a and the discharge passage 122 can be closed. FIG. 5A shows this state. On the other hand, the oil pressurized by the oil pump 1 moves the push-back valve body 51 of the check valve 5 in the reverse flow direction, so that an inflow area is secured in the inflow path 121. With the above configuration, the oil flows into the accumulator 22 up to the upper limit pressure and is accumulated. Note that the mark X in C of the control solenoid 21 indicates that the C path is disconnected from the B path.

[Second embodiment: When idling is stopped]
When idling is stopped, that is, when the oil pump 1 is stopped, the push-back valve body 51 of the check valve 5 cannot be moved in the reverse flow direction, and the inflow path 121 is also closed (FIG. 5B). Thus, since the inflow path 121 and the discharge path 122 are closed in a state where pressure is accumulated in the accumulator 22, the accumulated pressure is held in the accumulator 22. Note that the mark X in C of the control solenoid 21 indicates that the C path is disconnected from the B path.

[Second Embodiment: Immediately after a restart command to the engine]
FIG. 5C shows an operation immediately after a restart command to the engine 81 in the hydraulic control apparatus. The control solenoid 21 is switched to the C mode. That is, the B road and the A road are blocked, and the B road and the C road are communicated. As a result, high-pressure oil of pressure P flows out from the control hydraulic chamber 42A through the B path and the C path. The force Fb associated with the hydraulic pressure in the control hydraulic chamber 42A is lost, and the balance valve element 43A is connected to the communication port 45a by the repulsive force f of the pushback compression spring 433a and the force Fa associated with the hydraulic pressure in the reference hydraulic chamber 41A. Then, the discharge passage 122 is opened. As a result, the oil retained in the accumulator 22 is discharged to the main oil passage 11, and the insufficient pressurization immediately after the restart command to the engine 81 can be compensated. Note that the mark “A” in A of the control solenoid 21 indicates that the A path is blocked from the B path.

[Numeric example]
In the hydraulic control device, for example, the repulsive force g = 5 (N) of the compression biasing spring 52, the cross-sectional area S ₀ = 30 (mm ² ) of the push-back valve body 51, Sa = 30 (mm ² ), high hydraulic pressure P = 0.8 (N / mm ² ), low oil pressure P ₀ = 0.1 (N / mm ² ), repulsive force f = 20 (N) of the push-back compression spring 433a, Sb = 65 (mm ² ) The operations during steady operation (FIG. 5A), when idling is stopped (FIG. 5B), and immediately after a restart command to the engine 81 (FIG. 5C) will be described.

[Numerical example: During steady operation of oil pump 1]
First, during the steady operation of the oil pump 1, the control solenoid 21 is in the A mode, and the hydraulic pressures in the reference hydraulic chamber 41A and the control hydraulic chamber 42A are both high. Then, the force to move the balance valve body 43A toward the reference hydraulic chamber 41A and close the communication port 45a is Fb = P × Sb = 0.8 (N / mm ² ) × 65 (mm ² ) = 52 (N). On the other hand, the force opposite to this is Fa + f = P × Sa + f = 0.8 (N / mm ² ) × 30 (mm ² ) +20 (N) = 44 (N). Then, since the force to close is won, the communication port 45a is closed, that is, the discharge passage 122 is closed.

On the other hand, the check valve 5 in the inflow passage 121 is in an open state as described below. The force for closing the check valve 5 is the repulsive force g of the compression biasing spring 52, and g = 5 (N). On the other hand, the hydraulic pressure of the high-pressure oil generated when the oil pump 1 is pressurized is an inflow hydraulic pressure exceeding P = 0.8 (N / mm ² ). For example, the inflow hydraulic pressure is 1.0 (N / mm ^2). ). Then, the force derived from the inflow hydraulic pressure applied to the push-back valve body 51 of the check valve 5 is 1.0 (N / mm ² ) × S ₀ = 1.0 (N / mm ² ) × 30 (mm ² ) = 30 (N). The force 30 (N) derived from the inflow pressure easily overcomes g = 5 (N), which is a force for closing the check valve 5, opens the accumulator 22, and high-pressure oil is accumulated in the accumulator 22.

Eventually, when the hydraulic pressure in the accumulator 22 rises to P = 0.8 (N / mm ² ), the force that closes the check valve 5 is added to the repulsive force g of the compression biasing spring 52, and the inflow lower flow path 121 b. As the hydraulic pressure P increases, the force applied to the push-back valve body 51 also increases. This is P × S ₀ = 0.8 (N / mm ² ) × 30 (mm ² ) = 24 (N). When the repulsive force g = 5 (N) of the compression urging spring 52 is also applied, 29 (N) is obtained. As the difference between the two decreases, such as a force 29 (N) for closing the check valve 5 with respect to the inflow pressure 30 (N), the inflow amount gradually decreases. However, as a result, the oil with the hydraulic pressure P = 0.8 (N / mm ² ) is accumulated in the accumulator 22.

[Numeric example: When idling is stopped]
Next, a state where the pressurizing operation by the oil pump 1 is stopped will be described. The force for closing the check valve 5 is P × S ₀ + g = 29 (N). On the other hand, since the hydraulic pressure of the non-pressurized main oil passage 11 is P ₀ , the force with which the hydraulic pressure attempts to open the check valve 5 is P ₀ × S ₀ = 0.1 (N / mm ² ) × 30 (mm ² ) = 3 (N). Obviously, the force to close the valve is won, and the check valve 5 remains closed. Similarly to the steady operation of the oil pump 1, the balance valve body 43 </ b> A has a superior force for closing the communication port 45 a, so that the discharge path 122 continues to be closed.

[Numerical example: Immediately after a restart command to the engine 81]
Next, the operation immediately after the restart command to the engine 81 will be described. High pressure oil in the control oil pressure chamber 42A is discharged, so that the force from the low pressure P ₀ is applied to the surface 431b. This force is P ₀ × Sb = 0.1 (N / mm ² ) × 65 (mm ² ) = 6.5 (N). On the other hand, the force to move the balance valve body 43A to the control hydraulic chamber 42A side and open the communication port 45a is P × Sa + f = 0.8 (N / mm ² ) × 30 (mm ² ) +20 ( N) = 44 (N). As described above, since the force to open the communication port 45a is won, the discharge passage 122 is opened, and the accumulated high-pressure oil is discharged to the accumulator 22.

[Numerical example: Again during steady operation of oil pump 1]
When the oil pump 1 is constantly pressurized, the control solenoid 21 is again in the A mode. In the A mode, the high pressure oil of the hydraulic pressure P is introduced into the control hydraulic chamber 42A. Then, again, the force for closing the communication port 45a by the balance valve body 43A exceeds the force for opening, and the discharge passage 122 is closed. On the other hand, the check valve 5 is opened by the hydraulic pressure pressurized by the oil pump 1, and high-pressure oil is accumulated in the accumulator 22 through the inflow path 121. The above is an example of the operation of the hydraulic control apparatus when specific numerical values are applied.

  The above is the configuration and operation of the second embodiment of the hydraulic control apparatus of the present invention. With this configuration, the hydraulic pressure accumulated in the accumulator 22 having a relatively large capacity is discharged through the discharge path 122 by eliminating the hydraulic pressure in the control hydraulic chamber 42A having a capacity much smaller than that of the accumulator 22. Can do. Since the capacity of the high pressure oil in the control hydraulic chamber 42A is small, there is an effect that the large capacity hydraulic pressure of the accumulator 22 can be controlled even if the B path and the C path of the control solenoid 21 have a relatively small effective area.

  Further, the simple structure of the balance valve body 43A makes it possible to make the effective sectional area on the control hydraulic chamber 42A side larger than the effective sectional area on the reference hydraulic chamber 41A side, so that the BBU 4A can be reliably operated by operating the control solenoid 21. There is an effect that can be operated to open and close.

[Third Embodiment]
A third embodiment of the hydraulic control device of the present invention will be described based on FIG. The forms of the mission 82, the oil return 83, and the oil pump 1 are the same as those in the first embodiment and the second embodiment, so the description and description on the drawings are omitted. The inflow path 121 provided with the check valve 5 is configured to be built in the balance valve body 43B. That is, the balance valve body 43B is provided with an inflow path inlet 436 at the side of the balance valve body 43B and an inflow path outlet 437 at the end. When the oil pump 1 is in operation, the pressurized oil enters the valve body 43B from the inflow upper flow path 121a through the inflow path inlet 436, and from the inflow path outlet 437 through the inflow lower flow path 121b to the accumulator. To 22. The pressurized oil flows in the balance valve body 43B with the check valve 5 opened.

  The reference hydraulic chamber 41 </ b> B is connected to the accumulator 22 through the inflow passage outlet 437. The A path of the control solenoid 21 is also connected to the accumulator 22 by the inflow lower flow path 121b (discharge upper flow path 122a). The control hydraulic chamber 42B is connected to the B path of the control solenoid 21 through an oil path. Further, the C path of the control solenoid 21 is connected to the oil return 83.

  The balance valve body 43B itself is movably disposed between the reference hydraulic chamber 41B side and the control hydraulic chamber 42B side, and the oil on the reference hydraulic chamber 41B side and the control hydraulic chamber 42B are respectively provided by two O-rings 432. Side oil is sealed to prevent leakage. With such a configuration, a portion other than the space occupied by the balance valve body 43B in the control hydraulic chamber 42B is a space for storing high-pressure oil. On the other hand, the entire space of the reference hydraulic chamber 41B is occupied by the balance valve body 43B, and the high-pressure oil stored in the reference hydraulic chamber 41B is stored in the internal space of the balance valve body 43B.

  In addition, an oil passage serving as both the inflow lower flow passage 121b and the discharge upper flow passage 122a is provided in the reference hydraulic chamber 41B at a position where the inflow passage outlet 437 of the balance valve body 43B contacts, and the oil passage is provided in the accumulator 22. It reaches. A discharge lower flow path 122b is provided adjacent to the oil passage, and when the balance valve body 43B contacts the oil passage opening, the discharge lower flow path 122b is closed by the balance valve body 43B (FIG. 6). (See (A) and (B).) When the balance valve body 43B moves to the control hydraulic pressure chamber 42B side, the discharge lower flow path 122b is opened, and the discharge path 122 is opened from the accumulator 22 to the main oil path 11.

  The balance valve body 43B moves according to the hydraulic balance between the reference hydraulic chamber 41B side and the control hydraulic chamber 42B side. The end 431b of the balance valve body 43B receives the hydraulic pressure in the control hydraulic chamber 42B. The effective cross-sectional area that receives the hydraulic pressure is Sb. On the other hand, the pressure that the balance valve body 43B receives from the oil on the reference hydraulic chamber 41B side is the end of the balance valve body 43B on the reference hydraulic chamber 41B side and the inside of the balance valve body 43B. It depends on the valve body part which comprises. The portions that receive these hydraulic pressures are collectively referred to as an end portion 431a, and the effective cross-sectional area is defined as Sa.

  Therefore, if Sa <Sb is configured so that the reference hydraulic pressure chamber 41B and the control hydraulic pressure chamber 42B have the same pressure P, the force Fa pressing the balance valve body 43B from the reference hydraulic pressure chamber 41B side and the control hydraulic pressure chamber 42B side are pressed. The forces Fb are Fa = P × Sa and Fb = P × Sb, respectively. As described above, since Sa <Sb, Fa <Fb is established, and the balance valve body 43B is pushed and positioned on the reference hydraulic chamber 41B side. Further, in order to compensate for Fb, a pressing compression spring 433b may be provided at the end 431b of the balance valve body 43B. The indentation compression spring 433b has a repulsive force F. In this case, the balance valve body 43B is pushed to the reference hydraulic chamber 41B side by the force of Fb + F−Fa.

[Third embodiment: During steady operation of the oil pump 1]
FIG. 6A shows a state where the oil pump 1 is normally operating. At this time, the control solenoid 21 is in the A mode. Then, since the B path and the A path are communicated and the C path is blocked as described above, the control hydraulic chamber 42B has a hydraulic pressure P substantially equal to the reference hydraulic chamber 41B. Then, as described above, the balance valve body 43B is pushed to the reference hydraulic chamber 41B side by the force of Fb + F−Fa.

  And the front-end | tip part of the balance valve body 43B contact | abuts to the reference | standard hydraulic chamber wall surface 411, and the discharge path 122 is closed. On the other hand, the oil pressurized by the oil pump 1 moves the push-back valve body 51 of the check valve 5 in the direction of the back flow for the check valve 5, so that the inflow path 121 formed inside the balance valve body 43 </ b> B. The oil inflow area is secured. With the above configuration, the oil flows into the accumulator 22 up to the upper limit pressure and is accumulated. Note that the mark X in C of the control solenoid 21 indicates that the C path is disconnected from the B path.

[Third embodiment: When idling is stopped]
Next, the state when the oil pump 1 stops with the temporary stop of the engine 81 will be described with reference to FIG. The control solenoid 21 is still in the A mode, and the hydraulic pressure in the reference hydraulic chamber 41B and the control hydraulic chamber 42B is approximately P. Therefore, the balance valve body 43B is pushed toward the reference hydraulic chamber 41B by the force of Fb + F−Fa, and the discharge passage 122 remains closed (FIG. 6B). Since the oil pump 1 is stopped, the oil that is not pressurized cannot open the check valve 5 and the inflow path 121 is also closed. Thus, since the inflow path 121 and the discharge path 122 are closed in a state where pressure is accumulated in the accumulator 22, the accumulated pressure is held in the accumulator 22. Note that the mark X in C of the control solenoid 21 indicates that the C path is disconnected from the B path.

[Third embodiment: Immediately after a restart command to the engine]
FIG. 6C shows an operation immediately after a restart command to the engine 81 in the hydraulic control apparatus. The control solenoid 21 is switched to the C mode. That is, the B road and the A road are blocked, and the B road and the C road are communicated. As a result, high-pressure oil of pressure P flows out from the control hydraulic chamber 42B through the B path and the C path. Then, the force Fb accompanying the hydraulic pressure in the control hydraulic chamber 42B is lost.

  Only the repulsive force F of the pressing compression spring 433b cannot resist the force Fa accompanying the hydraulic pressure in the reference hydraulic chamber 41B, and the balance valve body 43B moves to the control hydraulic chamber 42B side. Then, when the tip of the balance valve body 43B is separated from the reference hydraulic chamber wall surface 411, the discharge lower flow path 122b, that is, the discharge path 122 is opened. As a result, the oil retained in the accumulator 22 is discharged to the main oil passage 11, and the insufficient pressurization immediately after the restart command to the engine 81 can be compensated. Note that the mark “A” in A of the control solenoid 21 indicates that the A path is blocked from the B path.

[Numeric example]
In the hydraulic control apparatus, for example, the repulsive force g = 1 (N) of the compression biasing spring 52, the cross-sectional area S ₀ = 30 (mm ² ) of the push-back valve body 51, Sa = 120 (mm ² ), high hydraulic pressure P = 0.8 (N / mm ² ), low oil pressure P ₀ = 0.1 (N / mm ² ), repulsive force F = 50 (N) of the pressing compression spring 433b, Sb = 160 (mm ² ) The operations during steady operation (FIG. 6A), when idling is stopped (FIG. 6B), and immediately after a restart command to the engine 81 (FIG. 6C) will be described.

[Numerical example: During steady operation of oil pump 1]
First, during the steady operation of the oil pump 1, the control solenoid 21 is in the A mode, and the hydraulic pressures in the reference hydraulic chamber 41B and the control hydraulic chamber 42B are both high. Then, the force for moving the balance valve body 43B to the reference hydraulic chamber 41B side is controlled by Fb + F = P × Sb + F = 0.8 (N / mm ² ) × 160 (mm ² ) +50 (N) = 178 (N). The force to move to the hydraulic chamber 42B is Fa = P × Sa = 0.8 (N / mm ² ) × 120 (mm ² ) = 96 (N). Thus, since the force moved to the reference | standard hydraulic chamber 41B side prevails, the discharge path 122 is the closed state.

On the other hand, the check valve 5 in the inflow passage 121 is in an open state as will be confirmed below. The force for closing the check valve 5 is the repulsive force g of the compression urging spring 52, and g = 1 (N). On the other hand, the hydraulic pressure of the high-pressure oil generated when the oil pump 1 is pressurized is an inflow hydraulic pressure exceeding P = 0.8 (N / mm ² ). For example, the inflow hydraulic pressure is 0.85 (N / mm ^2). ). Then, the force derived from the inflow hydraulic pressure applied to the push-back valve body 51 of the check valve 5 is 0.85 (N / mm ² ) × S ₀ = 0.85 (N / mm ² ) × 30 (mm ² ) = 25.5 (N). The force 25.5 (N) derived from the inflow pressure easily overcomes g = 1 (N), which is the force for closing the check valve 5, opens the accumulator 22, and high-pressure oil is accumulated in the accumulator 22. The

Eventually, when the hydraulic pressure in the accumulator 22 rises to P = 0.8 (N / mm ² ), the force that closes the check valve 5 is added to the repulsive force g of the compression biasing spring 52, and the inflow lower flow path 121 b. As the hydraulic pressure P increases, the force applied to the push-back valve body 51 also increases. This is P × S ₀ = 0.8 (N / mm ² ) × 30 (mm ² ) = 24 (N). When the repulsive force g = 1 (N) of the compression urging spring 52 is also applied, 25 (N) is obtained. As the difference between the two decreases, such as the force 25 (N) for closing the check valve 5 with respect to the inflow pressure 25.5 (N), the amount of inflow gradually decreases. However, as a result, the oil with the hydraulic pressure P = 0.8 (N / mm ² ) is accumulated in the accumulator 22.

[Numeric example: When idling is stopped]
Next, a state where the pressurizing operation by the oil pump 1 is stopped will be described. The force for closing the check valve 5 is P × S ₀ + g = 25 (N). On the other hand, since the hydraulic pressure of the non-pressurized main oil passage 11 is P ₀ , the force with which the hydraulic pressure attempts to open the check valve 5 is P ₀ × S ₀ = 0.1 (N / mm ² ) × 30 (mm ² ) = 3 (N). Obviously, the force to close the valve is won, and the check valve 5 remains closed. Further, as in the steady operation of the oil pump 1, the 178 (N), which is the force for moving the balance valve body 43B to the reference hydraulic chamber 41B side, is the force for moving the control valve chamber 42B. Since it is superior to (N), the discharge passage 122 is kept closed.

[Numerical example: Immediately after a restart command to the engine 81]
Next, the operation immediately after the restart command to the engine 81 will be described. High pressure oil in the control oil pressure chamber 42B is discharged, so that the force from the low pressure P ₀ is applied to the end portion 431b. This force is P ₀ × Sb = 0.1 (N / mm ² ) × 160 (mm ² ) = 16 (N). This force and the repulsive force F = 50 (N) of the pressing compression spring 433b are the forces that move the balance valve body 43B to the reference hydraulic chamber 41B. This is 66 (N) in total. On the other hand, the force for moving the balance valve body 43B to the control hydraulic chamber 42B side and opening the discharge passage 122 is P × Sa = 0.8 (N / mm ² ) × 120 (mm ² ) = 96. (N). Since this force exceeds 66 (N), the balance valve body 43B moves to the control hydraulic chamber 42B side, the discharge passage 122 is opened, and the high-pressure oil accumulated in the accumulator 22 is discharged. .

[Numerical example: Again during steady operation of oil pump 1]
When the oil pump 1 is constantly pressurized, the control solenoid 21 is again in the A mode. In the A mode, the high pressure oil of the hydraulic pressure P is introduced into the control hydraulic chamber 42B. Then, the balance valve body 43B moves again to the reference hydraulic chamber 41B side, and the discharge path 122 is closed. On the other hand, the check valve 5 is opened by the hydraulic pressure pressurized by the oil pump 1, and high-pressure oil is accumulated in the accumulator 22 through the inflow path 121. The above is an example of the operation of the hydraulic control apparatus when specific numerical values are applied.

  The hydraulic control device according to the third embodiment has an effect that a compact hydraulic control device can be obtained by incorporating the check valve 5 of the inflow passage 121 in the balance valve body 43B.

[Fourth Embodiment]
Next, based on FIG. 7, 4th Embodiment which concerns on the hydraulic control apparatus of this invention is described. Since the forms of the mission 82, the oil return 83, and the oil pump 1 are the same as those of the first embodiment, the second embodiment, and the third embodiment, the description and description on the drawings are omitted. In the hydraulic control apparatus, the inflow lower flow path 121b downstream of the inflow path 121 and the discharge upper flow path 122a upstream of the discharge path 122 are shared by one oil path, and the inflow upper flow path 121a upstream of the inflow path 121 The discharge lower flow path 122b downstream of the discharge path 122 is shared by one oil path.

  A portion of the inflow passage 121 provided with the check valve 5 is incorporated in the reference hydraulic chamber 41C. The balance valve body 43C is configured to pass through the insertion hole 46C of the reference hydraulic chamber 41C and the control hydraulic chamber 42C. An O-ring 432 is provided on the side of the balance valve body 43C and is isolated so that the oil in the reference hydraulic chamber 41C and the oil in the control hydraulic chamber 42C do not mix.

  The inflow lower flow path 121b (discharge upper flow path 122a) is connected to the A path of the accumulator 22, the reference hydraulic chamber 41C, and the control solenoid 21. The control hydraulic chamber 42C is connected to the B path of the control solenoid 21. Here, in the control hydraulic chamber 42C, the oil passage connected to the B passage is installed at a position where the flow-in oil acts on the control hydraulic chamber side section 431b so that the balance valve body 43C can be pushed. It has been.

  Further, a piston 434C is provided at the end of the balance valve body 43C on the side of the control hydraulic pressure chamber 42C, and the balance valve body 43C is moved toward the reference hydraulic pressure chamber 41C by receiving hydraulic pressure from the piston 434C. The check valve 5 is opened by moving. That is, when the check valve 5 is opened by the hydraulic pressure on the control hydraulic chamber 42C side pushing the balance valve body 43C, the discharge passage 122 (122a and 122b) can be opened.

  Here, the force required to open the check valve 5 will be described. The check valve 5 is biased to the closed side by the hydraulic pressure P in the reference hydraulic chamber 41C and the repulsive force g of the compression biasing spring 52 that biases the pushback valve body 51. A surface on which pressure is applied to the push-back valve body 51 is defined as a reference hydraulic chamber side section 431a and an effective sectional area Sa. Then, the force Fa for closing the check valve 5 is Fa = P × Sa + g. On the other hand, the source of the force that opens the check valve 5 against this Fa is the force by which the hydraulic pressure in the control hydraulic chamber 42C pushes the control hydraulic chamber side section 431b. The effective cross-sectional area of the surface on which the hydraulic pressure is applied is Sb.

[Fourth Embodiment: During steady operation of oil pump]
FIG. 7A shows a steady operation state of the oil pump 1. At this time, the control solenoid 21 is in the C mode. As a result, the B and C paths communicate with each other and the A path is shut off, so that the high hydraulic pressure is not accumulated in the control hydraulic chamber 42C, and the hydraulic pressure is considerably lower than that of the reference hydraulic chamber 41C. Yes. Therefore, a force sufficient to open the check valve 5 does not act on the balance valve body 43C.

  However, when the oil pump 1 operates in a steady manner and sufficiently pressurized oil acts on the inflow upper flow path 121a, the check valve 5 opens and the pressurized oil flows in, and is added through the inflow lower flow path 121b. Pressure oil is accumulated in the accumulator 22. The above is the pressure accumulation state during the steady operation of the oil pump 1 shown in FIG. Further, the balance valve element 43C may be urged to move toward the control hydraulic pressure chamber 42C by the repulsive force f of the push-back compression spring 433a so as not to hinder oil inflow. Note that the mark “A” in A of the control solenoid 21 indicates that the A path is blocked from the B path.

[Fourth embodiment: idling stop]
Next, the state when the oil pump 1 stops with the temporary stop of the engine will be described with reference to FIG. The control solenoid 21 is still in the C mode, and no high hydraulic pressure is accumulated in the control hydraulic chamber 42C, and the hydraulic pressure is considerably lower than that in the reference hydraulic chamber 41C. Therefore, a force sufficient to open the check valve 5 does not act on the balance valve body 43C. Further, since the oil pump 1 is stopped and the oil is not pressurized, no force is generated to open the check valve 5 through the inflow upper flow path 121a.

  Therefore, the valve body of the check valve 5 is firmly attached to the inlet to the inflow upper flow path 121a (also the discharge lower flow path 122b) by the hydraulic pressure in the reference hydraulic chamber 41C and the compression biasing spring 52 of the repulsive force g. To maintain the closed state. By this operation, even if the oil pressure in the main oil passage 11 is lowered, the accumulated pressure in the accumulator 22 is maintained. Further, the balance valve element 43C is moved to the control hydraulic pressure chamber 42C side by the repulsive force f of the push-back compression spring 433a so that the balance valve element 43C does not prevent the check valve 5 from being closed. You may force. Note that the mark “A” in A of the control solenoid 21 indicates that the A path is blocked from the B path.

[Fourth embodiment: Immediately after a restart command to the engine]
FIG. 7C shows the operation immediately after a restart command to the engine 81 in the hydraulic control apparatus. Here, the control solenoid 21 is switched to the A mode. That is, the B road and the C road are blocked, and the B road and the A road are communicated. As a result, a part of the high-pressure oil accumulated in the accumulator 22 flows into the control hydraulic chamber 42C through the A path and the B path, and the hydraulic pressure in the control hydraulic chamber 42C becomes a hydraulic pressure P that is substantially the same as that in the reference hydraulic chamber 41C. It has become. Then, the balance valve body 43C is pushed toward the reference hydraulic chamber 41C with the hydraulic pressure P introduced into the control hydraulic chamber 42C, the check valve 5 is opened, and the discharge passage 122 is opened.

  As described above, in order to open the check valve 5, a force of Fa = P × Sa + g or more is required. Further, since the balance valve body 43C itself is pushed back and biased by the repulsive force f by the push-back compression spring 433a, taking this into consideration, a force larger than Fa + f = P × Sa + g + f is introduced into the control hydraulic chamber 42C. It is necessary to generate with the hydraulic pressure P. For this purpose, it is necessary to make the effective sectional area Sb of the control hydraulic chamber side section 431b where the hydraulic pressure is applied in the control hydraulic chamber 42C sufficiently larger than Sa.

  If Sb is sufficiently larger than Sa and is formed so as to satisfy the conditional expression P × Sa + f + g <P × Sb, the balance valve body 43C is pushed into the reference hydraulic chamber 41C side by hydraulic pressure in the control hydraulic chamber 42C, The check valve 5 can be opened. If it does so, the discharge path 122 will be open | released, the oil currently hold | maintained at the accumulator 22 will be discharged to the main oil path 11, and the shortage of pressurization immediately after the restart command to the engine 81 can be compensated. Note that the mark X in C of the control solenoid 21 indicates that the C path is disconnected from the B path.

[Fourth Embodiment: Again during steady operation of oil pump 1]
The above is the situation of several hundred milliseconds immediately after the restart command to the engine 81. After that, the pressurized oil from the oil pump 1 is supplied, and the oil pump 1 returns to the state during steady operation. At this time, the control solenoid 21 is in the C mode under the control of the controller 3. That is, the B road is disconnected from the A road and communicated with the C road. By this switching, the high-pressure oil in the control hydraulic chamber 42C is discharged through the B path and the C path. Then, the force of P × Sb that attempts to move the balance valve body 43C to the reference hydraulic chamber 41C side is lost. Then, the balance valve element 43C is moved to the control hydraulic pressure chamber 42C side by the repulsive force f of the pushback compression spring 433a or the hydraulic pressure in the reference hydraulic pressure chamber 41C, and the state shown in FIG. .

[Fourth Embodiment: Processing Flow by Controller 3]
The control of the control solenoid 21 in the hydraulic control apparatus is different from the other embodiments, and will be described based on the processing flowchart shown in FIG. The processing flow in FIG. 8 is almost the same as the processing flow in FIG. 4, but Step 2, Step 9, and Step 10 are different. First, when the switch of the electric system of the automobile is connected, the controller 3 also starts operation. In order to prevent malfunction when the power is turned on, a “past flag” regarding the engine 81 or the pump operation is bit-set (Step 1).

  Since it is an initial setting here, it is assumed that bits are set for convenience. The control solenoid 21 is set to the C mode. That is, the B road and the C road are communicated and the B road and the A road are blocked (Step 2). This is an operation for making the hydraulic pressure in the control hydraulic chamber 42C sufficiently lower than the hydraulic pressure in the reference hydraulic chamber 41C. In addition, necessary initial settings are performed (Step 3).

  The controller power supply is checked (Step 4). As a result, if the power is turned off (if it is OFF), the processing is branched to “end” as “true” (Step 5). If the power is not turned off, the processing after Step 6 is performed as “false”.

  It is checked whether the engine 81 or the oil pump 1 is operating or stopped via the state signal 811 of the engine 81 or the oil pump 1. If it is operating, the "current flag" relating to engine operation is set, and if it is stopped, it is reset. As for the “current flag”, at least one bit of set and reset may be secured in the work area of the memory 32 as in the case of the “past flag” (Step 6). Subsequently, it is checked whether the “past flag” is set or reset (Step 7).

Referring to “past flag” and “current flag”, if “past flag is reset” and “current flag is set”, proceed to Step 9 as “true”, otherwise as “false” It progresses to Step10 (Step8). Step 8 is a processing example for detecting a state immediately after a restart command to the engine 81.

  If the condition branch at Step 8 is “true”, the state is immediately after the restart command to the engine 81, so that the process proceeds to Step 9 to set the control solenoid 21 to the A mode. That is, the B road is cut off from the C road, and the B road and the A road are communicated. By this operation, the control hydraulic chamber 42C is also filled with high-pressure oil, and the balance valve body 43C is pushed into the reference hydraulic chamber 41C side by the force resulting from the hydraulic pressure P of the high-pressure oil. When the balance valve body 43C is pushed and the check valve 5 is opened, the discharge passage 122 is opened. As a result, the high-pressure oil accumulated in the accumulator 22 is discharged to the main oil passage 11.

  On the other hand, if the conditional branch of Step 8 is “false”, it is during steady operation or when idling is stopped, so the process proceeds to Step 10 to maintain the C mode of the control solenoid 21. That is, the B road is blocked from the A road, and the B road and the C road are communicated. By this operation, the discharge passage 122 is kept closed.

  Step 10 is performed both during the steady operation of the oil pump 1 and when idling is stopped. That is, the discharge path 122 is maintained in a closed state, and the inflow path 121 is controlled by the check valve 5. During the steady operation of the oil pump 1, the operation of the oil pump 1 moves the push-back valve body 51 of the check valve 5 to the downstream side by the force accompanying the oil pressure of the main oil passage 11 and the inflow upstream passage 121 a, and the accumulator 22. Oil flows in. At the time of idling stop, the oil pressure of the main oil passage 11 and the inflow upper flow passage 121a is reduced by stopping the oil pump 1, so the inflow passage 121 is also closed, and the accumulated pressure and oil in the accumulator 22 are maintained as they are.

  After executing Step 9 or Step 10, Step 11 updates the “Past Flag” with the value of “Current Flag” and returns to Step 4 to check the controller power supply. Thereafter, Step 4 to Step 11 are repeated until the controller 3 is turned off. As described above, the flowchart shown in FIG. 4 shows basic processing. For example, the time until the discharge of the oil accumulated in the accumulator 22 is completed is secured between Step 4 and Step 11. It is also possible to include a waiting time process for adjusting the time.

  In the fourth embodiment of the hydraulic control apparatus of the present invention, the simple structure of the balance valve body 43C is used, and the effective sectional area on the control hydraulic chamber 42C side is easily configured to be larger than the effective sectional area on the reference hydraulic chamber 41C side. Therefore, there is an effect that the opening and closing of the balance valve unit 4C can be reliably operated by operating the control solenoid 21.

  In the hydraulic control apparatus, it is the push-back valve body 51 that seals (seals) the oil accumulated in the accumulator 22 so that it does not inadvertently leak to the main oil passage 11 side. At the opening of the check valve 5, the protruding portion of the balance valve body 43 </ b> C abuts on the push-back valve body 51 and moves the push-back valve body 51 in the reverse flow direction for the check valve 5. It is something to be made.

  Here, if the push-back valve body 51 is hit with a strike mark by the balance valve body 43C, the oil seal (sealing) cannot be ensured. Therefore, the durability and reliability of the sealing performance of the check valve 5 can be improved by forming the push-back valve body 51 with higher hardness than the protruding portion of the balance valve body 43C. As a result, it has the effect of improving the durability and reliability of the hydraulic control device.

DESCRIPTION OF SYMBOLS 1 ... Oil pump, 11 ... Main oil path, 12 ... Branching path, 121 ... Inflow path,
121a ... Inflow upper flow path, 121b ... Inflow lower flow path, 122 ... Discharge path,
122a ... discharge upper flow path, 122b ... discharge lower flow path, 2 ... pressure accumulating section, 21 ... control solenoid,
22 ... Accumulator, 221 ... Compression spring for pressure accumulation, 222 ... Pressure accumulation piston,
3 ... Controller, 31 ... CPU, 32 ... Memory, 33 ... I / O interface,
331: Control signal, 4, 4A, 4B, 4C ... Balance valve unit (BBU),
41, 41A, 41B, 41C ... reference hydraulic chamber, 411 ... reference hydraulic chamber wall surface,
42, 42A, 42B, 42C ... control hydraulic chamber,
43, 43A, 43B, 43C ... balance valve body,
431a: Reference hydraulic chamber side cross section (effective cross-sectional area Sa),
431b ... Control hydraulic chamber side cross section (effective cross-sectional area Sb), 432 ... O-ring,
433a ... push-back compression spring, 433b ... push-in compression spring,
434A, 434C ... piston, 435 ... communication closing part, 436 ... inflow path inlet,
437 ... Inlet passage outlet, 44a, 44b ... Movement restricting member, 45 ... Bulkhead, 45a ... Communication port,
46A, 46C ... insertion hole, 5 ... check valve, 51 ... push-back valve body, 52 ... compression biasing spring,
81 ... Engine, 811 ... Engine or oil pump status signal,
82 ... Mission, 83 ... Oil return.

Claims (12)

  In a hydraulic control apparatus having an oil pump that operates as the engine rotates, a main oil passage that connects the oil pump and a transmission, a branch passage that branches from the main oil passage, and an accumulator connected to the branch passage The control solenoid has a balance valve unit including a reference hydraulic chamber, a control hydraulic chamber, and a balance valve body, and a check valve for preventing a backflow is provided in the oil inflow path to the accumulator in the branch path. The balance valve unit is provided in the oil discharge path from the accumulator, and the control solenoid is operated to introduce and discharge high-pressure oil into the control hydraulic chamber, and the reference hydraulic chamber and the control hydraulic pressure Opening and closing the balance valve unit by moving the balance valve body by increasing or decreasing the hydraulic pressure difference in the chamber Hydraulic control device according to claim.   2. The hydraulic control device according to claim 1, wherein the control solenoid has three oil inlets / outlets of an A path, a B path, and a C path, and communicates between the B path and the A path. An electromagnetic control valve capable of switching between an A mode that blocks between the C paths and a C mode that communicates between the B paths and the C paths and blocks between the B paths and the A paths. The solenoid A, the reference hydraulic chamber, and the downstream side of the check valve of the oil inflow passage are connected directly or via the accumulator, and the control hydraulic chamber and the control solenoid B are connected. When the oil pump is in a pressurizing operation and stopped, the control solenoid is set to the A mode so that the hydraulic pressures in the control hydraulic pressure chamber and the reference hydraulic pressure chamber are close to each other. Position the valve on the closed side While closing the oil discharge path, immediately after the restart command to the engine, the control solenoid is set to the C mode to lower the hydraulic pressure in the control hydraulic chamber, thereby opening the balance valve body to the open side. A hydraulic control device, wherein the hydraulic discharge device is positioned to open the oil discharge passage.   2. The hydraulic control device according to claim 1, wherein the control solenoid has three oil inlets / outlets of an A path, a B path, and a C path, and communicates between the B path and the A path. An electromagnetic control valve capable of switching between an A mode that blocks between the C paths and a C mode that communicates between the B paths and the C paths and blocks between the B paths and the A paths. The solenoid A, the reference hydraulic chamber, and the downstream side of the check valve of the oil inflow passage are connected directly or via the accumulator, and the control hydraulic chamber and the control solenoid B are connected. Thus, when the oil pump is in a pressurizing operation and when it is stopped, the control solenoid is set to C mode to reduce the hydraulic pressure in the control hydraulic chamber so that the balance valve body is closed. Position the oil discharge On the other hand, immediately after the restart command to the engine, the control solenoid is set to the A mode so that the hydraulic pressures in the control hydraulic pressure chamber and the reference hydraulic pressure chamber are close to each other, thereby bringing the balance valve body to the open side. A hydraulic control device, wherein the hydraulic discharge device is positioned to open the oil discharge passage.   3. The hydraulic control device according to claim 2, wherein a downstream flow path of the oil discharge path is sandwiched between the reference hydraulic chamber and the control hydraulic chamber, and a downstream flow of the reference hydraulic chamber and the oil discharge path is defined. A partition having a communication port to the downstream flow path is provided between the passages, and an insertion hole for inserting the balance valve element is provided between the downstream flow path of the oil discharge path and the control hydraulic chamber. The balance valve body is movably inserted through the insertion hole, and an O-ring is provided on a side portion of the balance valve body, and a disk-shaped piston is provided in the control hydraulic chamber of the balance valve body. A fixed conical or cylindrical communication closing portion is provided on the reference hydraulic chamber side of the balance valve body, and the communication closing portion is fitted into a communication port to the downstream flow path of the oil discharge passage. The balance valve unit is closed Further, in the balance valve body, the effective cross-sectional area on the side of the communication closing portion is configured to be smaller than the effective cross-sectional area on the piston side, and when the oil pump is in a pressurizing operation. When stopped, the control solenoid is set to the A mode, and the oil pressure in the control hydraulic chamber and the reference hydraulic chamber are brought close to each other so that the balance valve body is positioned on the closed side and the oil discharge path is closed. On the other hand, immediately after the restart command to the engine, the control solenoid is set to the C mode, and the oil pressure in the control hydraulic chamber is lowered, so that the balance valve body is positioned on the open side and the oil discharge path is opened. A hydraulic control device that is opened.   3. The hydraulic control device according to claim 2, wherein the oil inflow path is referred to as an inflow upper flow path with the check valve provided between the oil inflow paths as a boundary, and the oil inflow path flows into the accumulator. The oil discharge path is referred to as a discharge upper flow path, and the oil discharge path is referred to as a discharge upper flow path with the balance valve unit provided between the oil discharge paths as a boundary, and the main oil path is referred to as a discharge lower flow path. The inflow lower flow path and the discharge upper flow path are shared by a single oil path and connected to the accumulator, and the balance valve body is movably disposed between the reference hydraulic pressure chamber and the control hydraulic pressure chamber, The reference hydraulic chamber is connected to the inflow lower flow path and the discharge upper flow path, the inflow upper flow path and the discharge lower flow path that are shared by a single oil path. The oil inflow passage having a check valve structure is formed, and at the end of the balance valve body on the reference hydraulic pressure chamber side, an inflow passage outlet is formed and communicates with the inflow lower flow path. An inflow passage inlet is provided in a side portion and is connected to the inflow upper flow path. In the balance valve body, an effective cross-sectional area formed by an end portion on the reference hydraulic chamber side and the check valve is set in the control hydraulic chamber. When the oil pump is in a pressurizing operation and stopped, the control solenoid is set to the A mode so that the control hydraulic pressure is set to be smaller than the effective sectional area of the end of the balance valve body. By closing the oil discharge passage by moving the balance valve body to the reference hydraulic chamber side by bringing the oil pressures of the chamber and the reference hydraulic chamber close to each other, immediately after the restart command to the engine, Control soreno The de as C-mode, by reducing the hydraulic pressure of the control hydraulic chamber, a hydraulic control device, characterized in that the balance valve body to open the oil discharge passage are moved into the control oil pressure chamber closer.   4. The hydraulic control device according to claim 3, wherein the oil inflow path is referred to as an inflow upper flow path with the check valve provided between the oil inflow paths as a boundary, and the accumulator position is inflow. The oil discharge path is referred to as a discharge upper flow path, and the oil discharge path is referred to as a discharge upper flow path with the balance valve unit provided between the oil discharge paths as a boundary, and the main oil path is referred to as a discharge lower flow path. The inflow lower flow path and the discharge upper flow path are shared by one oil path, the inflow upper flow path and the discharge lower flow path are shared by one oil path, and the oil inflow path having the check valve structure is the reference hydraulic pressure. The balance valve body is formed in a chamber and has a configuration in which an insertion hole between the reference hydraulic chamber and the control hydraulic chamber is inserted, and an O-ring is provided on a side portion of the balance valve body, and the balun A piston is provided at an end of the valve body and in the end of the control hydraulic chamber, and the check valve is moved by receiving the hydraulic pressure from the piston and moving the balance valve body toward the reference hydraulic chamber. When the oil pump is in a pressurizing operation and when it is stopped by forming an opening so that the effective cross-sectional area where the piston receives hydraulic pressure is wider than the effective cross-sectional area of the check valve While the control solenoid is set to C mode and the hydraulic pressure in the control hydraulic chamber is reduced, the balance valve element reduces the force to open the check valve and closes the oil discharge passage, Immediately after the restart command to the engine, the control solenoid is set to the A mode, and a part of the oil accumulated in the accumulator is introduced into the control hydraulic chamber to increase the hydraulic pressure of the control hydraulic chamber. Hydraulic control apparatus characterized by hydraulic pressure of the control oil pressure chamber with a force to push the piston, thereby opening the oil discharge passage opens the check valve.   The hydraulic control device according to claim 3 or 6, wherein the check valve includes a push-back valve body and a compression valve that urges the push-back valve body in a direction opposite to an oil inflow direction to the accumulator. On the other hand, an end portion of the balance valve body, the end portion on the reference hydraulic chamber side is formed as a projecting portion, and is configured to abut against the push-back valve body. The return valve body is formed with higher hardness than the protruding portion.   In a hydraulic control apparatus having an oil pump that operates as the engine rotates, a main oil passage that connects the oil pump and a transmission, a branch passage that branches from the main oil passage, and an accumulator connected to the branch passage The control solenoid has a balance valve unit including a reference hydraulic chamber, a control hydraulic chamber, and a balance valve body, and a check valve for preventing a backflow is provided in the oil inflow path to the accumulator in the branch path. The balance valve unit is provided in the oil discharge path from the accumulator, and the control solenoid is operated to introduce and discharge high-pressure oil into the control hydraulic chamber, and the reference hydraulic chamber and the control hydraulic pressure The balance valve unit is moved by opening and closing the balance valve unit by increasing or decreasing the hydraulic pressure difference in the chamber. Hydraulic control method comprising Rukoto.   9. The hydraulic control method according to claim 8, wherein the control solenoid has three oil inlets / outlets of an A path, a B path, and a C path, and communicates between the B path and the A path. An electromagnetic control valve capable of switching between an A mode that blocks between the C paths and a C mode that communicates between the B paths and the C paths and blocks between the B paths and the A paths. The solenoid A, the reference hydraulic chamber, and the downstream side of the check valve of the oil inflow passage are connected directly or via the accumulator, and the control hydraulic chamber and the control solenoid B are connected. When the oil pump is in a pressurizing operation and stopped, the control solenoid is set to the A mode so that the hydraulic pressures in the control hydraulic pressure chamber and the reference hydraulic pressure chamber are close to each other. Position the valve on the closed side While closing the oil discharge path, immediately after the restart command to the engine, the control solenoid is set to the C mode to lower the hydraulic pressure in the control hydraulic chamber, thereby opening the balance valve body to the open side. A hydraulic control method characterized in that the oil discharge path is opened by being positioned.   9. The hydraulic control method according to claim 8, wherein the control solenoid has three oil inlets / outlets of an A path, a B path, and a C path, and communicates between the B path and the A path. An electromagnetic control valve capable of switching between an A mode that blocks between the C paths and a C mode that communicates between the B paths and the C paths and blocks between the B paths and the A paths. The solenoid A, the reference hydraulic chamber, and the downstream side of the check valve of the oil inflow passage are connected directly or via the accumulator, and the control hydraulic chamber and the control solenoid B are connected. Thus, when the oil pump is in a pressurizing operation and when it is stopped, the control solenoid is set to C mode to reduce the hydraulic pressure in the control hydraulic chamber so that the balance valve body is closed. Position the oil discharge On the other hand, immediately after the restart command to the engine, the control solenoid is set to the A mode, a part of the oil accumulated in the accumulator is introduced into the control hydraulic chamber, and the control hydraulic chamber and the A hydraulic control method characterized by bringing the balance valve body to an open side and opening the oil discharge passage by bringing the hydraulic pressures in a reference hydraulic chamber close to each other.   10. The hydraulic control method according to claim 9, further comprising a controller for controlling the control solenoid, wherein a current flag and a past flag for recording operation and stop states of the engine or the oil pump are provided in a memory of the controller. The past flag is set in advance, the control solenoid is set in the A mode in advance, and the current flag is updated every time the operation of the engine or the oil pump is confirmed. Alternatively, when the oil pump is operating, the current flag is bit-set and when stopped, the bit is reset. If the past flag is bit-reset and the current flag is bit-set, the control solenoid is set to C mode. The discharge path is opened while the past flag is bit. If the current flag is not reset and the current flag is not set, the current flag is set before the control solenoid is set to A mode to close the discharge passage and confirm the operation of the engine or the oil pump again. The hydraulic control method, wherein the past flag is updated with the content of.   The hydraulic control method according to claim 10, further comprising a controller for controlling the control solenoid, wherein a current flag and a past flag for recording an operation state and a stop state of the engine or the oil pump are provided in a memory of the controller. The past flag is set in advance, the control solenoid is set in the C mode in advance, and the current flag is updated every time the operation of the engine or the oil pump is confirmed. Alternatively, when the oil pump is operating, the current flag is bit-set and when stopped, the bit is reset. If the past flag is bit-reset and the current flag is bit-set, the control solenoid is set to the A mode. The discharge flag is opened while the past flag is set to If the reset flag and the current flag are not set, the control solenoid is set to C mode, the discharge passage is closed, and the operation of the engine or the oil pump is confirmed again before the current flag is set. A hydraulic control method, wherein a past flag is updated with the content of the flag.

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