JP4985419B2 - Hydraulic control device for engine - Google Patents

Description

  The present invention relates to an engine hydraulic control device, and more particularly to control of hydraulic pressure supplied to an oil circulation path inside an engine and a hydraulic operating component provided in the engine.

  As an engine lubrication device, a mechanical oil pump mechanically driven by an engine and an electric oil pump driven by an electric motor are used together to supply oil into the engine and reduce friction between rubbing parts. What to do is known. In such a lubrication apparatus, a technique capable of lubricating parts easily and appropriately is disclosed in, for example, Japanese Patent Laid-Open No. 2006-83782 (Patent Document 1).

  The internal combustion engine lubrication apparatus disclosed in this publication includes a mechanical oil pump that always supplies oil during operation of the internal combustion engine, and an electric motor that supplies oil when the amount of oil supplied by the mechanical oil pump is not sufficient. With an oil pump. Oil from these oil pumps is supplied to a main oil hole formed in the cylinder block and then supplied to a portion to be lubricated of the internal combustion engine via a plurality of branch passages branched from the main oil hole. The lubrication apparatus includes a first inflow portion where oil supplied by a mechanical oil pump flows into a main oil hole and a second portion where oil supplied by an electric oil pump flows into the main oil hole. At least one branch passage is branched from the main oil hole between the inflow portions.

According to the lubrication apparatus disclosed in this publication, since at least one branch passage is branched from the main oil hole between the first inflow portion and the second inflow portion, the first oil is sucked up by the mechanical oil pump and is firstly drawn. Part of the oil flowing into the main oil hole from the inflow site is supplied to the site to be lubricated via the branch passage. Therefore, the hydraulic pressure is reduced at the second inflow portion. Therefore, when the amount of oil supplied by the mechanical oil pump is not sufficient (that is, when the hydraulic pressure at the second inflow portion drops more than necessary), the oil sucked up by the electric oil pump at the second inflow portion is not contained. Supplied. Therefore, a decrease in hydraulic pressure can be prevented, and an appropriate amount of oil can be supplied to all the parts to be lubricated. Furthermore, when the amount of oil supplied by the mechanical oil pump is not sufficient, the capacity of the mechanical oil pump can be reduced by driving the electric oil pump to supply oil.
JP 2006-83782 A

  By the way, some engines are equipped with components that operate by hydraulic pressure (for example, a VVT (Variable Valve Timing) mechanism for changing the opening / closing timing of an intake valve or an exhaust valve). The lubricating device disclosed in Patent Document 1 describes two oil pumps, a mechanical oil pump and an electric oil pump. However, Patent Document 1 discloses a hydraulic pressure applied to a hydraulically operated component such as a VVT mechanism. No supply method is disclosed.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide mechanical oil in an engine including a mechanical oil pump, an electric oil pump, and a hydraulic operating component. An object of the present invention is to provide a hydraulic control device capable of supplying a sufficient hydraulic pressure to hydraulic operating parts while suppressing an increase in the capacity of the pump and the electric oil pump.

  A hydraulic control apparatus according to a first aspect of the present invention controls the hydraulic pressure of an engine provided with hydraulic operating parts. The hydraulic control device is driven by an engine, and a mechanical oil pump that supplies oil to a first oil passage connected to an oil circulation passage inside the engine, and a second oil that is driven by an electric motor and connected to an operating component. An electric oil pump that supplies oil to the road, and a connection state that connects the first oil path and the second oil path, and a communication state in which the oil in the first oil path flows to the second oil path and the first oil A switching valve that switches between a shut-off state in which the passage and the second oil passage are shut off, a detecting means for detecting a value related to the temperature inside the engine, and the switching valve is controlled based on the output of the detecting means And control means.

  According to the first invention, the mechanical oil pump supplies oil to the first oil passage connected to the oil circulation passage inside the engine. The electric oil pump supplies oil to the second oil passage connected to the hydraulic operation part. A switching valve is provided in the connection path connecting the first oil path and the second oil path. This switching valve is switched between a communication state and a shut-off state based on a value related to the temperature inside the engine (for example, the engine water temperature). If it does in this way, according to the temperature inside an engine, a 1st oil path and a 2nd oil path can be connected or interrupted | blocked. For example, when the temperature inside the engine is low, it is assumed that the output of the electric oil pump is low because the oil temperature is low and the oil viscosity is high. The second oil path can be supplied. As a result, the hydraulic pressure can be supplied from the mechanical oil pump to the operating component in addition to the electric oil pump, so that sufficient hydraulic pressure can be supplied to the operating component without increasing the capacity of the electric oil pump. it can. Also, for example, when the temperature inside the engine is high, since the oil temperature is high and the oil viscosity is low, it is possible to supply sufficient hydraulic pressure to the operating parts using only the electric oil pump, and the switching valve is controlled to be in the shut-off state. Thus, the first oil passage and the second oil passage can be blocked. Thereby, the oil from the mechanical oil pump is not supplied to the operating parts, and the load on the mechanical oil pump is reduced. Therefore, it is not necessary to increase the capacity of the mechanical oil pump in consideration of a decrease in output when the engine speed decreases. As a result, in an engine equipped with a mechanical oil pump, an electric oil pump, and a hydraulic operating component, the hydraulic oil pump and the hydraulic oil pump are prevented from increasing in capacity while suppressing the increase in the capacity of the hydraulic oil pump. It is possible to provide a hydraulic control device capable of supplying a sufficient hydraulic pressure to the operating parts.

  In the hydraulic control apparatus according to the second invention, in addition to the configuration of the first invention, the control means determines whether the value detected by the detection means is higher than a predetermined value. When the detected value is lower than a predetermined value, the switching valve is controlled so as to be in a communication state, and when the detected value is higher than a predetermined value, the switching valve is set to be in a cutoff state. Means for controlling.

  According to the second invention, when the value related to the internal temperature of the engine is lower than a predetermined value, it is assumed that the output of the electric oil pump is reduced, and the changeover valve is controlled to be in the communication state, and the first oil is controlled. Road oil can be supplied to the second oil path. In addition, when the value related to the temperature inside the engine is higher than a predetermined value, it is assumed that sufficient hydraulic pressure can be supplied to the operating parts only by the electric oil pump, and the switching valve is controlled to be in the shut-off state. The oil passage and the second oil passage can be blocked.

  In the hydraulic control device according to the third aspect of the invention, in addition to the configuration of the second aspect, the predetermined temperature depends on the temperature that satisfies the required performance of the operating parts only with the hydraulic pressure supplied from the electric oil pump. Is set.

  According to the third aspect of the invention, only when the hydraulic pressure supplied from the electric oil pump cannot satisfy the required performance of the operating parts, the switching valve is in a communicating state, and the insufficient hydraulic pressure can be compensated by the mechanical oil pump. . Therefore, the load on the mechanical oil pump can be minimized.

  In the hydraulic control apparatus according to the fourth aspect of the invention, in addition to the configuration of the second aspect of the invention, the predetermined temperature is set according to the upper limit value of the temperature at which the engine needs to be warmed up.

  According to the fourth aspect of the present invention, before the warm-up when the viscosity of the oil is high, the operation component can be operated by both the electric oil pump and the mechanical oil pump with the switching valve in a communicating state. On the other hand, after warming up with low oil viscosity, the operating part can be operated only by the electric oil pump with the switching valve shut off.

  A hydraulic control apparatus according to a fifth aspect of the invention includes, in addition to the configuration of any one of the second to fourth aspects, a hydraulic pressure detection means for detecting the hydraulic pressure of the first oil passage, and a hydraulic pressure detection means in the communication state. Means for controlling the electric oil pump so that the amount of oil flowing from the first oil passage into the second oil passage increases by reversely rotating the electric motor when the oil pressure detected by the motor exceeds a predetermined oil pressure And further including.

  According to the fifth invention, when the oil viscosity is high and the oil pressure in the first oil passage becomes excessive and exceeds a predetermined value, the electric oil pump is reversely rotated, and the second oil is discharged from the first oil passage. The amount of oil flowing into the road increases. Thereby, since the oil pressure of the first oil passage is lowered, an unnecessary load due to the high viscosity of the oil in the mechanical oil pump can be reduced.

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

  With reference to FIG. 1, an engine 100 of a vehicle equipped with a hydraulic control apparatus according to the present embodiment will be described.

  Air is drawn into the engine 100 from the air cleaner 102. The intake air amount is adjusted by the throttle valve 104. The throttle valve 104 is an electronic throttle valve that is driven by a motor.

  Air is mixed with fuel in the cylinder 106 (combustion chamber). Fuel is directly injected into the cylinder 106 from the injector 108. In addition to the direct injection injector 108, a port injection injector may be provided. Further, only a port injection injector may be provided.

  The air-fuel mixture in the cylinder 106 is ignited by the spark plug 110 and burns. The air-fuel mixture after combustion, that is, the exhaust gas is purified by the three-way catalyst 112 and then discharged outside the vehicle. The piston 114 is pushed down by the combustion of the air-fuel mixture, and the crankshaft 116 rotates.

  An oil circulation path (not shown) for supplying oil (lubricating oil) to the inner wall of the cylinder 106 and the crankshaft 116 is formed inside the engine 100. Oil in the oil circulation path is circulated by a mechanical oil pump 400 described later. Furthermore, a water jacket 308 through which cooling water flows is provided in the cylinder block of engine 100.

  An intake valve 118 and an exhaust valve 120 are provided at the top of the cylinder 106. The amount and timing of air introduced into the cylinder 106 is controlled by the intake valve 118. The amount and timing of the exhaust gas discharged from the cylinder 106 is controlled by the exhaust valve 120. The intake valve 118 is driven by a cam 122. The exhaust valve 120 is driven by a cam 124.

  The intake valve 118 is changed in opening / closing timing (phase) by the VVT mechanism 126. The opening / closing timing of the exhaust valve 120 may be changed.

  In the present embodiment, the camshaft (not shown) provided with the cam 122 is rotated by the VVT mechanism 126, whereby the opening / closing timing of the intake valve 118 is controlled. The method for controlling the opening / closing timing is not limited to this. In the present embodiment, VVT mechanism 126 is operated by hydraulic pressure.

  The engine 100 is controlled by an ECU (Electronic Control Unit) 200. The ECU 200 controls the throttle opening, the ignition timing, the fuel injection timing, the fuel injection amount, and the opening / closing timing of the intake valve 118 so that the engine 100 is in a desired operating state.

  The ECU 200 is connected with a cam angle sensor 300, a crank angle sensor 302, a temperature sensor 304, and a throttle opening sensor 306 by a harness or the like. The cam angle sensor 300 detects the position of the cam. The crank angle sensor 302 detects the rotation speed of the crankshaft 116 (engine rotation speed) and the rotation angle of the crankshaft 116. The temperature sensor 304 detects the coolant temperature THW inside the water jacket 308. The throttle opening sensor 306 detects the throttle opening. Each of these sensors outputs a signal representing the detection result to ECU 200.

  ECU 200 controls engine 100 based on signals input from these sensors, a map stored in ROM (Read Only Memory) 202, and a program.

  The VVT mechanism 126 will be further described with reference to FIG. Note that the structure of the VVT mechanism 126 described below is merely an example, and may be a VVT mechanism having another structure as long as it is hydraulically operated.

  The VVT mechanism 126 includes a housing 128, a vane 130, an advance chamber 132, and a retard chamber 134. The housing 128 is connected to the crankshaft 116 via a chain or a belt. The housing 128 rotates at half the engine speed.

  The vane 130 is rotatably supported inside the housing 128. The vane 130 is fixed to the camshaft and rotates together with the camshaft. As the vane 130 rotates relative to the housing 128, the opening / closing timing of the intake valve 118 is advanced or retarded.

  The advance chamber 132 is a space defined by the housing 128 and the vane 130. When the hydraulic pressure is supplied to the advance chamber 132, the vane 130 rotates clockwise in FIG. 2, and the opening / closing timing of the intake valve 118 is advanced.

  The retard chamber 134 is a space defined by the housing 128 and the vane 130. When the hydraulic pressure is supplied to the retard chamber 134, the vane 130 rotates counterclockwise in FIG. 2, and the opening / closing timing of the intake valve 118 is retarded.

  With reference to FIG. 3, the hydraulic control apparatus according to the present embodiment will be described. This hydraulic control device controls the hydraulic pressure supplied to the oil circulation path and the VVT mechanism 126. The hydraulic control device includes a mechanical oil pump (MOP) 400, an electric oil pump (EOP) 500, an OCV (Oil Control Valve) 600, and an ECU 200.

  The mechanical oil pump 400 is connected to the crankshaft 116, is driven by the engine 100, sucks oil stored in the oil pan 700, and supplies the sucked oil to the first oil path 410 connected to the oil circulation path. . The oil pressure in the first oil passage 410 is detected by the oil pressure sensor 204, and the detection result is transmitted to the ECU 200.

  The electric oil pump (EOP) 500 is equipped with a motor driven by a control signal from the ECU 200, and the oil stored in the oil pan 700 is sucked by driving the motor, and the sucked oil is connected to the VVT mechanism 126. Supplied to the second oil passage 510.

  The OCV 600 is an electromagnetic spool valve connected between the first oil passage 410 and the second oil passage 510. The OCV 600 is controlled to either a communication state or a shut-off state by a control signal from the ECU 200.

  In the communication state, the oil in the first connection path 610 connected to the first oil path 410 is supplied to the second connection path 620 connected to the second oil path 510. In the blocked state, the first connection path 610 and the second connection path 620 are blocked. That is, the OCV 600 switches between a communication state in which the oil in the first oil passage 410 flows to the second oil passage 510 and a shut-off state in which the first oil passage 410 and the second oil passage 510 are shut off.

  In the present embodiment, ECU 200 controls oil pressure supplied to first oil passage 410 and second oil passage 510 by controlling OCV 600 and electric oil pump 500 based on the outputs of temperature sensor 304 and oil pressure sensor 204. To control.

  FIG. 4 shows a functional block diagram of ECU 200 constituting the hydraulic control apparatus according to the present embodiment. ECU 200 includes an input interface (hereinafter referred to as input I / F) 210, an arithmetic processing unit 220, a storage unit 230, and an output interface (hereinafter referred to as output I / F) 240.

  The input I / F 210 receives the coolant temperature THW from the temperature sensor 304 and the oil pressure in the first oil passage 410 from the oil pressure sensor 204 and transmits it to the arithmetic processing unit 220.

  Various information, programs, threshold values, maps, and the like are stored in the storage unit 230, and data is read or stored from the arithmetic processing unit 220 as necessary.

  Arithmetic processing unit 220 includes a water temperature determination unit 222, an OCV control unit 224, and an EOP control unit 226.

  Water temperature determination unit 222 determines whether or not cooling water temperature THW is lower than a threshold value, and transmits the determination result to OCV control unit 224. This threshold value is set in advance according to the upper limit value of the temperature at which engine 100 needs to be warmed up, and is described in storage unit 230.

  The OCV control unit 224 controls the OCV 600 according to the determination result of the water temperature determination unit 222. The OCV control unit 224 generates an OCV control signal that makes the OVC 600 communicated when the coolant temperature THW is lower than the threshold value, and an OCV that shuts the OVC 600 when the coolant temperature THW is higher than the threshold value. Generate a control signal. The OCV control unit 224 transmits the generated OCV control signal to the output I / F 240.

  The EOP control unit 226 controls the electric oil pump 500 based on the hydraulic pressure in the first oil passage 410 when the OCV 600 is in communication.

  When the oil pressure in the first oil passage 410 is excessive because the oil viscosity is high (when the oil pressure in the first oil passage 410 exceeds an excessive value), the EOP control unit 226 passes through the OCV 600. Then, an EOP control signal for reversely rotating the electric oil pump 500 is generated so that a part of the oil supplied to the second oil passage 510 is returned to the oil pan 700. On the other hand, when the hydraulic pressure in the first oil passage 410 is not excessive, the EOP control unit 226 generates an EOP control signal that causes the electric oil pump 500 to rotate forward. The EOP control unit 226 transmits the generated EOP control signal to the output I / F 240.

  The output I / F 240 transmits an OCV control signal from the OCV control unit 224 to the OCV 600 and transmits an EOP control signal from the EOP control unit 226 to the electric oil pump 500.

  In the present embodiment, the water temperature determination unit 222, the OCV control unit 224, and the EOP control unit 226 are all executed by the CPU that is the arithmetic processing unit 220 executing the program stored in the storage unit 230. Although described as what is realized and functions as software, it may be realized by hardware. Such a program is recorded on a storage medium and mounted on the vehicle.

  With reference to FIG. 5, a control structure of a program executed by ECU 200 configuring the hydraulic control apparatus according to the present embodiment will be described. Note that this program is repeatedly executed at a predetermined cycle time.

  In step (hereinafter step is abbreviated as S) 100, ECU 200 determines whether or not coolant temperature THW is lower than a threshold value. If lower than the threshold value (YES in S100), the process proceeds to S104. Otherwise (NO in S100), the process proceeds to S102.

  In S102, ECU 200 transmits to OCV 600 an OCV control signal that causes OVC 600 to be shut off. In S104, ECU 200 transmits to OCV 600 an OCV control signal that causes OVC 600 to be in a communication state.

  In S106, ECU 200 determines whether or not the hydraulic pressure in first oil passage 410 is excessive. If so (YES in S106), the process proceeds to S108. Otherwise (NO in S106), the process proceeds to S110.

  In S <b> 108, ECU 200 transmits an EOP control signal for reversely rotating electric oil pump 500 to electric oil pump 500. In S <b> 110, ECU 200 transmits an EOP control signal for causing electric oil pump 500 to rotate forward to electric oil pump 500.

  The operation of the hydraulic control apparatus according to the present embodiment based on the above structure and flowchart will be described with reference to FIGS. 6 and 7.

[Before warming up (at extremely low temperatures, at low temperatures)]
Before the warm-up, the output of the motor driving the electric oil pump 500 is reduced and the viscosity of the oil is very high, so the output of the electric oil pump 500 is lower than after the warm-up. Therefore, there may occur a case where sufficient hydraulic pressure cannot be supplied to the VVT mechanism 126 only by the hydraulic pressure of the electric oil pump 500.

  Therefore, when cooling water temperature THW is lower than the threshold value (YES in S100), OVC 600 is brought into a communication state (S104). As a result, as shown in FIG. 6, the oil on the mechanical oil pump 400 side flows into the second oil passage 510 via the OCV 600 and is supplied to the VVT mechanism 126. As a result, the hydraulic pressure that is insufficient with only the electric oil pump 500 can be compensated by the mechanical oil pump 400, and sufficient hydraulic pressure can be supplied to the VVT mechanism 126. Therefore, the VVT mechanism 126 can be operated according to the required performance without increasing the capacity of the electric oil pump 500.

  Further, when the oil pressure in first oil passage 410 is excessive (YES in S106), electric oil pump 500 is rotated in the reverse direction (S108). As a result, as indicated by the dotted line arrow in FIG. 6, part of the oil that has flowed into the second oil passage 510 from the mechanical oil pump 400 side via the OCV 600 is returned to the oil pan 700.

  As a result, the amount of oil flowing from the first oil passage 410 into the second oil passage 510 increases, and the oil pressure in the first oil passage 410 decreases. Therefore, an unnecessary load due to the high viscosity of oil in mechanical oil pump 400 is reduced. Furthermore, it is possible to suppress the excessively low or low temperature oil from circulating in the oil circulation path before warming up and promote warming around the piston 114 of the engine 100.

[After warming up]
After warm-up, cooling water temperature THW becomes higher than the threshold value (NO in S100), and OVC 600 is turned off (S102). As a result, as shown in FIG. 7, the first oil passage 410 and the second oil passage 510 are completely shut off, and only the hydraulic pressure from the electric oil pump 500 is supplied to the VVT mechanism 126. Since the oil viscosity is lowered later, the output of the electric oil pump 500 is increased as compared with that before the warm-up. Therefore, a sufficient hydraulic pressure can be supplied to the VVT mechanism 126 using only the electric oil pump 500, and the VVT mechanism 126 can be operated as required.

  Furthermore, since the VVT mechanism 126 is operated only by the hydraulic pressure from the electric oil pump 500, even if the engine rotational speed becomes a low value (for example, idling rotational speed) and the output of the mechanical oil pump 400 decreases, the VVT The mechanism 126 can be operated as required. Therefore, the operating range of the VVT mechanism 126 can be expanded without increasing the capacity of the mechanical oil pump 400 to improve the fuel consumption rate.

  As described above, according to the hydraulic control apparatus according to the present embodiment, the oil passage on the mechanical oil pump side that supplies oil to the oil circulation path inside the engine and the electric oil pump side that supplies hydraulic pressure to the VVT mechanism An OCV is provided between the two oil passages. Before the warm-up when the oil viscosity is high, the OVC is in communication, and the oil on the mechanical oil pump side is supplied to the oil passage of the electric oil pump via the OCV. As a result, the hydraulic pressure that is insufficient with only the electric oil pump can be assisted by the mechanical oil pump, and the VVT mechanism can be operated as required. On the other hand, after warm-up with low oil viscosity, OVC is cut off, and the oil path on the mechanical oil pump side and the oil path on the electric oil pump side are completely cut off. Therefore, the VVT mechanism can be operated according to the required performance with only the electric oil pump.

  In the present embodiment, the case where the threshold value of the coolant temperature THW used for the OCV 600 switching determination is set to the upper limit value of the temperature at which the engine 100 needs to be warmed up has been described. Is not limited to this. For example, the pressure may be set according to the temperature that satisfies the required performance of the VVT mechanism 126 using only the hydraulic pressure supplied from the electric oil pump 500.

  In this way, only when the VVT mechanism 126 cannot be operated according to the required performance by only the hydraulic pressure from the electric oil pump 500, the OCV 600 can be brought into a communication state and the insufficient hydraulic pressure can be compensated by the mechanical oil pump 400. Therefore, it is possible to minimize the load on the mechanical oil pump 400 while suppressing an increase in the capacity of the electric oil pump 500.

  In the present embodiment, the OCV is controlled based on the comparison result between the coolant temperature THW detected by the temperature sensor 304 and the threshold value. However, for example, the oil temperature is detected and detected. The OCV may be controlled based on the comparison result between the oil temperature and the threshold value.

  Further, in the present embodiment, the case where the component operated by the hydraulic pressure from electric oil pump 500 is VVT mechanism 126 has been described, but the component is not limited to VVT mechanism 126 as long as the component is operated by the hydraulic pressure. For example, a component operated by hydraulic pressure from the electric oil pump 500 is an HLA (Hydraulic Lash Adjuster) that adjusts the clearance of the intake valve or the exhaust valve in addition to the VVT mechanism 126 or instead of the VVT mechanism 126. Also good.

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

It is a figure which shows the structure of the engine of the vehicle carrying the hydraulic control apparatus which concerns on embodiment of this invention. It is a figure which shows the VVT mechanism which concerns on embodiment of this invention. It is a figure which shows the structure of the hydraulic control apparatus which concerns on embodiment of this invention. It is a functional block diagram of ECU which comprises the hydraulic control apparatus which concerns on embodiment of this invention. It is a flowchart which shows the control structure of ECU which comprises the hydraulic control apparatus which concerns on embodiment of this invention. It is FIG. (1) which shows operation | movement of the hydraulic control apparatus which concerns on embodiment of this invention. It is FIG. (2) which shows operation | movement of the hydraulic control apparatus which concerns on embodiment of this invention.

Explanation of symbols

  100 engine, 102 air cleaner, 104 throttle valve, 106 cylinder, 108 injector, 110 spark plug, 112 three-way catalyst, 114 piston, 116 crankshaft, 118 intake valve, 120 exhaust valve, 122 cam, 126 VVT mechanism, 128 housing, 130 vane, 132 advance chamber, 134 retard chamber, 200 ECU, 202 ROM, 204 hydraulic sensor, 210 input I / F, 220 arithmetic processing unit, 222 water temperature determination unit, 224 OCV control unit, 226 EOP control unit, 230 Storage unit, 240 output I / F, 300 cam angle sensor, 302 crank angle sensor, 304 temperature sensor, 306 throttle opening sensor, 308 water jacket, 400 mechanical oil pump, 410 1st Road, 500 electric oil pump, 510 the second oil passage, 600 OCV, 610 first connection passage, 620 the second connection channel 700 the oil pan.

Claims (5)

A hydraulic control device for an engine having hydraulic operating parts,
A mechanical oil pump that is driven by the engine and supplies oil to a first oil passage connected to an oil circulation passage inside the engine;
An electric oil pump that is driven by an electric motor and supplies oil to a second oil passage connected to the operating component;
Provided in a connection path that connects the first oil path and the second oil path, a communication state in which oil in the first oil path flows into the second oil path, and the first oil path and the second oil path A switching valve for switching between the shut-off states, and
Detection means for detecting a value relating to the temperature inside the engine;
Based on an output of said detecting means, seen including a control means for controlling said switching valve,
The hydraulic control device, wherein the second oil passage is an oil passage downstream of the electric oil pump and upstream of the operating component . The control means includes
Means for determining whether a value detected by the detection means is higher than a predetermined value;
When the detected value is lower than the predetermined value, the switching valve is controlled so as to be in the communication state, and when the detected value is higher than the predetermined value, The hydraulic control apparatus according to claim 1, further comprising means for controlling the switching valve.   3. The hydraulic control device according to claim 2, wherein the predetermined value is set according to a temperature that satisfies the required performance of the operating component only by the hydraulic pressure supplied from the electric oil pump. The hydraulic control device according to claim 2, wherein the predetermined value is set according to an upper limit value of a temperature at which the engine needs to be warmed up. The hydraulic control device includes:
Oil pressure detecting means for detecting the oil pressure of the first oil passage;
In the communication state, when the hydraulic pressure detected by the hydraulic pressure detection means exceeds a predetermined hydraulic pressure, the amount of oil flowing from the first oil passage into the second oil passage is increased by reversely rotating the electric motor. The hydraulic control device according to claim 2, further comprising means for controlling the electric oil pump.

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