JP2001041040A - Control device of cooling water flow rate and lubricating oil flow rate on heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To hold lubricating oil temperature at a proper value by controlling a flow rate of lubricating oil and a flow rate of cooling water on a heat exchanger to exchange heat between the lubricating oil and the cooling water of an engine. SOLUTION: A heat exchanger HE exchanges heat between a part of cooling water circulating in an engine E by an electric cooling water pump WP and a part of lubricating oil circulating in the engine E by an eletcric lubricating oil pump OP. An electronic control unit U computes target cooling water temperature TwREF and target cooling lubricating-oil temperature ToREF by correcting standard cooling water temperature TwBASE and standard lubricating-oil temperature ToBASE retrieved in accordance with engine rotation number Ne and an engine load Pb by a throttle opening change rate ΔθTH and controls working of the electric cooling water pump WP and working of the eletcric lubricating- oil pump OP in accordance with deviation of these target cooling water temperature TwREF and target cooling lubricating-oil temperature ToREF and actual cooling water temperature Tw and actual lubricating oil temperature To.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger for exchanging heat between a part of cooling water circulating in an engine by an electric cooling water pump and a part of lubricating oil circulating in the engine by a lubricating oil pump. In particular, the present invention relates to a control device for controlling the flow rate of cooling water and the flow rate of lubricating oil.

[0002]

2. Description of the Related Art A sub oil pan provided outside an engine for driving a gas heat pump device for air conditioning communicates with a main oil pan in a crankcase, and high-temperature engine cooling water is supplied to a radiator provided in the sub oil pan. Japanese Patent Application Laid-Open No.
It is known from -8934.

[0003]

However, in the above conventional apparatus, the lubricating oil is heated only by supplying the engine cooling water to a radiator provided in the sub oil pan. There is a problem that it is not possible to precisely control the response.

[0004] The present invention has been made in view of the above circumstances, and in a heat exchanger for exchanging heat between lubricating oil and cooling water for an engine, the lubricating oil is controlled by controlling the flow rate of lubricating oil and the flow rate of cooling water. The purpose is to be able to maintain the temperature at an appropriate value.

[0005]

In order to achieve the above object, according to the first aspect of the present invention, a part of cooling water circulating through an engine by an electric cooling water pump and an electric lubricating oil pump are used. In a heat exchanger that exchanges heat with a part of lubricating oil circulating in an engine, an engine speed detecting means for detecting an engine speed, an engine load detecting means for detecting an engine load, and a cooling water temperature. Cooling water temperature detecting means for detecting, lubricating oil temperature detecting means for detecting lubricating oil temperature, and control means for controlling the operation of the electric cooling water pump and the operation of the electric lubricating oil pump, the control means comprising: The target coolant temperature and the target lubricant temperature are calculated by correcting the reference coolant temperature and the reference lubricant temperature retrieved based on the engine speed and the engine load, and the target coolant temperature and the target lubricant temperature are calculated. And controlling the operation of the electric cooling water pump and the operation of the electric lubricating oil pump based on the deviation between the target lubricating oil temperature and the actual cooling water temperature and the actual lubricating oil temperature. A control device for water flow and lubricating oil flow is proposed.

According to the above configuration, the target cooling water temperature and the target lubricating oil temperature calculated by correcting the reference cooling water temperature and the reference lubricating oil temperature retrieved based on the engine speed and the engine load, and the actual cooling water Since the operation of the electric cooling water pump and the operation of the electric lubricating oil pump are controlled based on the deviation from the temperature and the actual lubricating oil temperature, the cooling water temperature and the lubricating oil temperature excessively increase at a high load when the engine is likely to overheat. And the lubricated portion can be protected. In addition, at low loads where the engine tends to be cold, the cooling water temperature and lubricating oil temperature are raised to the required temperature, and the lubricating oil viscosity is reduced to reduce the sliding resistance of the engine, thereby reducing fuel consumption. can do.

[0007] Incidentally, the intake negative pressure Pb in the embodiment corresponds to the engine load of the present invention, means S ₂ out intake negative pressure of the embodiment corresponds to an engine load detecting means of the present invention.

According to the invention described in claim 2,
In addition to the configuration of claim 1, a throttle opening change rate detecting means for detecting a throttle opening change rate is provided, and the control means converts the reference cooling water temperature and the reference lubricating oil temperature to the throttle opening change rate. A control device for controlling the flow rate of the cooling water and the flow rate of the lubricating oil in the heat exchanger, wherein the target temperature of the cooling water and the target lubricating oil temperature are calculated based on the correction is proposed.

According to the above configuration, the reference cooling water temperature and the reference lubricating oil temperature are corrected based on the rate of change of the throttle opening to calculate the target cooling water temperature and the target lubricating oil temperature. The target cooling water temperature and the target lubricating oil temperature are reduced during acceleration or the like, and excessive rises in the cooling water temperature and the lubricating oil temperature can be suppressed to protect the lubricated portion.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described based on embodiments of the present invention shown in the accompanying drawings.

1 to 7 show a first embodiment of the present invention. FIG. 1 is a view for explaining the overall structure of a cooling system and a lubrication system of an engine, and FIG. 2 is an electric cooling water valve and an electric lubricating oil. FIG. 3 is a diagram showing the structure of the valve, FIG. 3 is a first diagram of a flowchart for explaining the operation, FIG. 4 is a second diagram of a flowchart for explaining the operation, and FIG. 6 is a fourth diagram of the flowchart for explaining the operation, and FIG. 7 is a map for retrieving correction coefficients (KΔθ _TH ) w and (KΔθ _TH ) o from the throttle opening change rate Δθ _TH .

First, based on the schematic diagram of FIG.
The overall structure of the cooling system and the lubrication system will be described.

The engine E has a water jacket J surrounding the outer periphery of a cylinder bore formed in a cylinder block and the outer periphery of a combustion chamber formed in a cylinder head.
A radiator R is provided to cool the cooling water that has passed through the water jacket J and has increased in temperature. With the upper part of the downstream end and the radiator R of the water jacket J is connected with the radiator upper hose L _1, and the upstream end of the lower and the water jacket J of the radiator R is provided with an electric thermostat T and the electric cooling water pump WP in series connected through the radiator lower hose L _2, it is further connected with the downstream end of the electric thermostat T and the water jacket J via the bypass passage L _3.

The electric thermostat T is operated by an electromagnetic force unlike a general thermostat using a thermo-wax as a driving source. The cooling water exiting the water jacket J passes through the radiator R to the electric cooling water pump WP. The supply path and the path supplied to the electric cooling water pump WP without passing through the radiator R can be continuously switched. The electric cooling water pump WP uses the electric motor 11 as a driving source unlike a general cooling water pump using the crankshaft of the engine E as a driving source, and can continuously change the rotation speed.

The engine E has lubricated portions such as a bearing portion for supporting the crankshaft and a valve operating mechanism, and lubricating oil is supplied from the oil pan 12 to these lubricated portions.
The lubricating oil supply passage L ₄ supplying lubricating oil to the lubricated section of the oil pan 12 engine E, toward the downstream side from the upstream side, oil strainer 13, oil filter 1
4. Electric lubricating oil pump OP and electric relief valve R
V are sequentially arranged. The electric lubricating oil pump OP is composed of a trochoid pump and a gear pump.
Driven by Surplus lubricating oil discharged from the electric relief valve RV is returned to the lubricating oil supply passage L ₄ between the oil filter 14 and the electric lubricating oil pump OP via a relief passage L _5. Lubricating oil lubricates the lubrication target portion of the engine E is returned to the oil pan 12 through the passage L ₆ return lubricating oil.

The engine E cools the lubricating oil with cooling water.
A heat exchanger HE is provided. Lubricating oil is electric relief valve R
Lubricating oil supply passage L downstream of V_FourLubrication oil branching off from
Road L ₇Of the lubricating oil supplied to the heat exchanger HE through the
Oil passage L provided with an electric lubrication oil valve OV for controlling oil pressure
₈Through the relief passage L_FiveIs returned to. Cooling water is electric
Radiator lower hose L downstream of cooling water pump WP_Two
Water passage L branching from₉To the heat exchanger HE
Electric cooling water valve WV for controlling the flow rate of supplied cooling water
Water passage L provided with_TenElectric cooling water pump WP
Radiator lower hose L on the upstream side_TwoIs returned to.

[0017] The electronic control unit U, a signal from an engine rotational speed detecting means S ₁ for detecting an engine speed Ne, a signal from an intake negative pressure detecting means S ₂ for detecting the intake negative pressure Pb of the engine E , Throttle opening change rate Δθ
A signal from a throttle opening change rate detecting means S ₃ for detecting the _TH (the amount of change in the throttle opening theta _TH per unit time), provided the water jacket J cooling water temperature Tw within the water jacket J a signal from the coolant temperature detecting means S ₄ for detecting, provided in the lubricating oil passage L ₈ and the signal from the lubricating oil temperature detecting means S ₅ for detecting the lubricating oil temperature to is input.

The electronic control unit U controls the electric cooling water pump WP, the electric lubricating oil pump OP, the electric thermostat T, the electric relief valve RV, the electric cooling water valve WV and the electric cooling water pump WP based on the outputs of the _five detecting means S _{1 to} S _5. The operation of the electric lubricating oil valve OV is controlled, and when a failure occurs, a warning lamp 16 is turned on to give a warning. In addition, a transition is made to a fail-safe mode to suppress overheating, and the engine E is controlled via the fuel injection control device 17. Enrich the fuel injection amount.

Next, the electric cooling water valve W will be described with reference to FIG.
The structure of the V and the electric lubricating oil valve OV will be described. Since the electric cooling water valve WV and the electric lubricating oil valve OV have substantially the same structure, the electric cooling water valve WV will be described as a representative thereof.

The electric cooling water valve WV has a bottomed cylindrical valve housing 21, and a valve body 22 slidably housed therein is urged by a valve spring 23 in a direction to be seated on a valve seat 24. Is done. The valve housing 21 has an inlet port 25 and an outlet port 26 formed therein.
Is seated on the valve seat 24 with the valve spring 23, the inlet port 2
5 and the outlet port 26 are disconnected. A linear solenoid 27 is disposed at the bottom of the valve housing 21 facing the back of the valve body 22. When the linear solenoid 27 is excited, the valve body 22 is sucked against the resilience of the valve spring 23, and The port 25 communicates with the outlet port 26.

[0021] with the electric cooling water valve WV is inlet port 25 communicates with the heat exchanger HE, the outlet port 26 communicates with the radiator lower hose L _2, heat exchanger HE
Is controlled by the electronic control unit U to regulate the flow rate of the cooling water passing therethrough. Together with the electric lubricant valve OV inlet port 25 communicates with the heat exchanger HE, and the outlet port 26 communicates with the relief passage L _5, electron to adjust the flow rate of the lubricating oil passing through the heat exchanger HE It is controlled by the control unit U.

Next, an outline of the control of the electric thermostat T and the electric cooling water pump WP will be described.

When the cooling water temperature Tw is low, for example,
When the engine E is cold immediately after starting, the electronic control unit U
Command causes the thermostat T to de-energize,
Radiator lower hose L connected to outlet of radiator R_TwoBut
Closed, circuit for cooling water passing through radiator R cut off
Is done. Therefore, the electric cooling water pump WP is
Cooling water supplied to the water jacket J
Data upper hose L ₁Flows into the radiator R via
Bypass from downstream end of water jacket J
Passage L_Three, Electric thermostat T and radiator lower
Hose L_TwoTo the electric cooling water pump WP. This
Like, the temperature rises through the water jacket J
Circulating the cooling water without passing through the radiator R
By this, the warm-up operation of the engine E can be promoted.
You. When the cooling water temperature Tw is particularly low, the electric cooling water pump is used.
The operation of the WP is also stopped, and the cold water enters the water jacket J.
The warm-up operation of the engine E can be performed by retaining the cooling water.
More effectively promoted.

[0024] During hot after the completion the warm-up operation of the engine E, a radiator lower hose L ₂ leading to the outlet of the radiator R the electric thermostat T by a command from the electronic control unit U is accumulative excitement is opened, the cooling water A circuit passing through the radiator R is formed. Accordingly, the cooling water supplied from the electric cooling water pump WP in the water jacket J of the engine E does not flow into the bypass passage L _3, a radiator upper hose L ₁ from the downstream end of the water jacket J, the radiator R, the radiator lower hose L ₂ returns to the electric cooling water pump WP via the electric thermostat T and the radiator lower hose L ₂ . By cooling the cooling water, which has passed through the water jacket J and thus increased in temperature, through the radiator R,
The stable operation can be performed by appropriately maintaining the temperature of the engine E.

Next, the contents of control of the electric cooling water pump WP, the electric lubricating oil pump OP, the electric cooling water valve WV, and the electric lubricating oil valve OV will be described in detail with reference to the flowcharts of FIGS.

First, in step S1, the engine speed detecting means S ₁ , intake negative pressure detecting means S ₂ , throttle opening change rate detecting means S ₃ , cooling water temperature detecting means S ₄ and lubricating oil temperature detecting means S _{5 are used.} , Engine speed Ne,
The intake negative pressure Pb, the throttle opening change rate Δθ _TH , the cooling water temperature Tw, and the lubricating oil temperature To are respectively detected. In the following step S2, a reference coolant temperature Tw _BASE is searched on a map using the engine speed Ne and the intake negative pressure Pb as parameters, and the reference lubricating oil temperature To _BASE is also mapped using the engine speed Ne and the intake negative pressure Pb as parameters. Search by. The reference cooling water temperature Tw _BASE and the reference lubricating oil temperature To _BASE are set high when the engine speed Ne and the intake negative pressure Pb are low, and set low when the engine speed Ne and the intake negative pressure Pb are high. Is done.

[0027] In the subsequent step S3, by applying the throttle opening change rate [Delta] [theta] _TH detected by the throttle opening change rate detecting means S ₃ with the map shown in FIG. 7, the correction coefficient of the cooling water temperature (KΔθ _TH) w and Lubricating oil temperature correction coefficient (K
Δθ _TH ) Search for o. When the throttle opening change rate Δθ _TH increases, that is, when the degree of acceleration of the vehicle increases, the correction coefficient (KΔθ _TH ) w of the coolant temperature decreases for a while after being kept at 1.0 for a while, and the lubricating oil The temperature correction coefficient (KΔθ _TH ) o immediately decreases linearly from 1.0. The slope of the decreasing portion is that the correction coefficient (KΔθ _TH ) o of the lubricating oil temperature is the correction coefficient (KΔθ
_TH ) w is slower than w because lubricating oil is harder to heat and cool than cooling water.

Subsequently, at step S4, the reference cooling water temperature T
The target coolant temperature Tw _REF is calculated by multiplying w _BASE by the coolant temperature correction coefficient (KΔθ _TH ) w, and the lubricant temperature correction coefficient (KΔθ _TH ) o is added to the reference lubricant temperature To _BASE in step S5. To calculate the target lubricating oil temperature To _REF . Followed in step S6, the coolant temperature detecting means S ₄ target coolant temperature cooling water temperature Tw detected by the T
subtracting from w _REF to calculate a deviation Tdw of the cooling water temperature,
Furthermore, in step S7, the lubricating oil temperature To detected by the lubricating oil temperature detecting means S ₅ is subtracted from the target lubricating oil temperature To _REF for calculating a deviation Tdo the lubricating oil temperature.

In the following steps S8 and S9, if the deviation Tdw of the cooling water temperature is 0 and the deviation Tdo of the lubricating oil temperature is 0, that is, the cooling water temperature Tw and the lubricating oil temperature To
Are equal to the target values, the rotation number of the electric cooling water pump WP, the rotation number of the electric lubrication oil pump OP, the opening degree of the electric cooling water valve WV, and the opening degree of the electric lubrication oil valve OV are determined in step S10. Is held in the current state.

In step S8, the deviation Td of the cooling water temperature is determined.
If w is not 0, the deviation Td of the cooling water temperature is determined in step S11.
If w is negative, that is, if the cooling water temperature Tw is higher than the target cooling water temperature Tw _REF , the flow shifts to the flowchart of FIG. 5, and in step S11, the cooling water temperature deviation Tdw
Is non-negative, that is, if the cooling water temperature Tw is lower than the target cooling water temperature Tw _REF , the flow shifts to the flowchart of FIG.

When the cooling water temperature Tw is equal to the target cooling water temperature Tw _REF
If it is higher than step S1, the flow goes to step S1 in the flowchart of FIG.
2, the deviation Tdo of the lubricating oil temperature is 0 and the lubricating oil temperature T
If o coincides with the target lubricating oil temperature To _REF , the motor is operated in a state where the rotation speed of the electric lubricating oil pump OP and the opening of the electric lubricating oil valve OV are held in order to lower the cooling water temperature Tw in step S13. The rotation speed of the cooling water pump WP is increased and the opening of the electric cooling water valve WV is increased.

If the answer in step S12 is NO and the deviation Tdo of the lubricating oil temperature is not 0 and the deviation Tdo of the lubricating oil temperature is negative in step S14, that is, if the lubricating oil temperature To is equal to the target lubricating oil temperature To _If it is higher than _REF, the rotation speed of the electric cooling water pump WP, the rotation speed of the electric lubricating oil pump OP, the opening degree of the electric cooling water valve WV, Maximize the opening of all electric lubricating oil valves OV.

If the lubricating oil temperature deviation Tdo is non-negative in step S14, that is, if the lubricating oil temperature To is lower than the target lubricating oil temperature To _REF , the cooling water temperature Tw is lowered in step S16 to reduce the lubricating oil temperature. In order to raise the temperature To, the rotational speed of the electric cooling water pump WP and the opening of the electric cooling water valve WV are increased, and the rotational speed of the electric lubricating oil pump OP and the electric lubricating oil valve OV are increased.
Decrease the opening degree.

When the cooling water temperature Tw is equal to the target cooling water temperature Tw _REF
If it is lower than step S1 in the flowchart of FIG.
7, the deviation Tdo of the lubricating oil temperature is 0 and the lubricating oil temperature T
If o is equal to the target lubricating oil temperature To _REF , in step S18, the motor is operated in a state where the rotation speed of the electric lubricating oil pump OP and the opening of the electric lubricating oil valve OV are held in order to increase the cooling water temperature Tw. The number of rotations of the cooling water pump WP is reduced, and the opening of the electric cooling water valve WV is reduced.

If the answer in step S17 is NO and the lubricating oil temperature deviation Tdo is not 0, and if the lubricating oil temperature deviation Tdo is negative in step S19, that is, if the lubricating oil temperature To is equal to the target lubricating oil temperature To _If it is higher than _REF , the cooling water temperature Tw is raised in step S20 and the lubricating oil temperature T
In order to reduce o, the rotational speed of the electric cooling water pump WP and the opening of the electric cooling water valve WV are reduced, and the rotational speed of the electric lubricating oil pump OP and the opening of the electric lubricating oil valve OV are increased.

If the deviation Tdo of the lubricating oil temperature is non-negative in step S19, that is, if the lubricating oil temperature To is lower than the target lubricating oil temperature To _REF , the cooling water temperature Tw and the lubricating oil temperature To are set in step S21. In order to raise the rotation speed, the rotation speed of the electric cooling water pump WP and the rotation speed of the electric lubrication oil pump OP are decreased, and the opening degree of the electric cooling water valve WV and the electric lubrication oil valve OV are fully closed.

When the deviation Tdo of the lubricating oil temperature is not 0 in step S9 of the flowchart of FIG. 4, that is, the cooling water temperature Tw matches the target cooling water temperature Tw _REF , but the lubricating oil temperature To is equal to the target lubricating oil temperature Tw. If it does not match To _REF , the process moves to step S22. If the deviation Tdo of the lubricating oil temperature is negative and the lubricating oil temperature To is higher than the target lubricating oil temperature To _REF in step S22, step S2 is performed.
3. In order to lower the lubricating oil temperature To in step 3, while keeping the rotation speed of the electric cooling water pump WP and the opening of the electric cooling water valve WV, the rotation speed of the electric lubricating oil pump OP and the opening of the electric lubricating oil valve OV Increase the degree. On the other hand, if the lubricating oil temperature deviation Tdo is non-negative and the lubricating oil temperature To is lower than the target lubricating oil temperature To _{REF in} step S22, the electric cooling water pump WP is operated to increase the lubricating oil temperature To in step S24. The rotation speed of the electric lubricating oil pump OP and the opening degree of the electric lubricating oil valve OV are reduced while the rotation speed of the electric cooling water valve WV and the opening degree of the electric cooling water valve WV are held.

As described above, the reference cooling water temperature Tw retrieved from the map based on the engine speed Ne and the intake negative pressure Pb.
_BASE and reference lubricating oil temperature To _BASE are cooling water temperature Tw
Further, since the lubricating oil temperature To is set to be lower at a high load where the lubricating oil temperature To tends to increase, it is possible to prevent the coolant temperature Tw and the lubricating oil temperature To from excessively increasing and damage the lubricated portion of the engine E. . Conversely, the reference cooling water temperature Tw _BASE and the reference lubricating oil temperature To _BASE are set to be higher at low loads where the cooling water temperature Tw and the lubricating oil temperature To tend to be low. To reduce the frictional resistance of the sliding portion of the engine E, thereby saving fuel consumption.

Further, when the throttle opening change rate .DELTA..theta. _TH increases, such as during rapid acceleration of a vehicle, the correction coefficient (K.DELTA..theta.
_TH ) w and the lubricating oil temperature correction coefficient (KΔθ _TH ) o become smaller than 1.0, so that the target cooling water temperature Tw _REF
And the target lubricating oil temperature To _REF decreases. Thus, it is possible to suppress the excessive rise of the cooling water temperature Tw and the lubricating oil temperature To, and to protect the lubricated portion of the engine E.

Next, a second embodiment of the present invention will be described with reference to FIGS. The second embodiment differs from the first embodiment in the structure of the electric cooling water valve WV and the electric lubricating oil valve OV.

As shown in FIGS. 8 and 9, the electric cooling water valve WV and the electric lubricating oil valve OV of this embodiment are driven by a rotary solenoid 31, and include an outer cylinder 33 having an inlet port 32. And an inner cylinder 35 having an outlet port 34 and housed in the outer cylinder 33 so as to be relatively rotatable. The inner cylinder 35 having one through hole 35 ₁
6 is connected to the rotary solenoid 31 is reciprocally rotated at a predetermined angle range, the hole 35 ₁ 9 inlet port 32 overlaps the inlet port 32 communicates with the outlet port 34.

The electric cooling water valve WV is inlet port 32 is connected to the heat exchanger HE, the outlet port 34 is connected to the radiator lower hose L _2, to adjust the flow rate of the coolant passing through the heat exchanger HE It is controlled by the electronic control unit U. The electric lubricating oil valve OV inlet port 32 is connected to the heat exchanger HE, and the outlet port 34 is connected to the relief passage L _5, the electronic control to adjust the flow rate of the lubricating oil passing through the heat exchanger HE It is controlled by the unit U.

This embodiment is the same as the first embodiment except for the structure of the electric cooling water valve WV and the electric lubricating oil valve OV.

Although the embodiments of the present invention have been described in detail, various design changes can be made in the present invention without departing from the gist thereof.

For example, in the embodiment, the electric cooling water valve WV
Although the electric lubricating oil valve OV is provided downstream of the heat exchanger HE, they may be provided upstream of the heat exchanger HE. In the embodiment, the intake negative pressure P is used as the engine load.
Although “b” has been exemplified, the throttle opening, the internal pressure of the cylinder, the output torque of the engine, and the like can be adopted.

[0046]

As described above, according to the first aspect of the present invention, the target cooling water calculated by correcting the reference cooling water temperature and the reference lubricating oil temperature retrieved based on the engine speed and the engine load. Temperature and target lubricant temperature;
The operation of the electric cooling water pump and the operation of the electric lubricating oil pump are controlled based on the actual cooling water temperature and the deviation from the actual lubricating oil temperature. Can be suppressed, and the lubricated portion can be protected. In addition, at low loads where the engine tends to be cold, the cooling water temperature and lubricating oil temperature are raised to the required temperature, and the lubricating oil viscosity is reduced to reduce the sliding resistance of the engine, thereby reducing fuel consumption. can do.

According to the second aspect of the present invention,
The target cooling water temperature and the reference lubricating oil temperature are corrected based on the throttle opening change rate to calculate the target cooling water temperature and the target lubricating oil temperature. The target lubricating oil temperature can be lowered, and excessive rises of the cooling water temperature and the lubricating oil temperature can be suppressed to protect the lubricated portion.

[Brief description of the drawings]

FIG. 1 is a diagram illustrating an overall structure of a cooling system and a lubrication system of an engine.

FIG. 2 is a view showing the structure of an electric cooling water valve and an electric lubricating oil valve;

FIG. 3 is a first partial diagram of a flowchart for explaining the operation;

FIG. 4 is a second partial diagram of a flowchart for explaining the operation;

FIG. 5 is a third partial view of a flowchart for explaining the operation;

FIG. 6 is a third diagram of the flowchart for explaining the operation;

FIG. 7 shows a correction coefficient (K) based on a throttle opening change rate Δθ _TH.
Map to search for Δθ _TH ) w and (KΔθ _TH ) o

FIG. 8 is a perspective view of an electric cooling water valve and an electric lubricating oil valve according to a second embodiment of the present invention.

9 is a sectional view taken along line 9-9 in FIG.

[Explanation of symbols]

E engine Ne engine speed OP electric lubricant pump Pb intake negative pressure (engine load) S ₁ engine rotational speed detecting means S ₂ intake negative pressure detecting means (engine load detecting means) S ₃ throttle opening change rate detecting means S ₄ coolant temperature detecting means S ₅ lubricating oil temperature detecting means Tdo deviation Tdw deviation To the lubricating oil temperature To _BASE reference lubricating oil temperature To _REF target lubricating oil temperature Tw coolant temperature Tw _BASE reference coolant temperature Tw _REF target coolant temperature U electronic Control unit (control means) WP Electric cooling water pump Δθ _TH Throttle opening degree change rate

Claims (2)

[Claims] 1. An electric cooling water pump (WP) between a part of the cooling water circulating through the engine (E) and an electric lubricating oil pump (OP) between a part of the lubricating oil circulating through the engine (E). An engine speed detecting means (S ₁ ) for detecting an engine speed (Ne); an engine load detecting means (S ₂ ) for detecting an engine load (Pb); Cooling water temperature detecting means (S) for detecting the temperature (Tw)
₄ ) and lubricating oil temperature detecting means (S) for detecting lubricating oil temperature (To)
₅ ), and control means (U) for controlling the operation of the electric cooling water pump (WP) and the operation of the electric lubricating oil pump (OP), wherein the control means (U) includes an engine speed (Ne) ) and engine load (Pb) search criteria coolant temperature based on (Tw _BASE) and the reference lubricating oil temperature (the to _{BA SE)} a correction to the target coolant temperature (Tw _REF) and the target lubricating oil temperature (the to _REF ) Is calculated, and these target cooling water temperatures (Tw
_REF ) and the target coolant temperature (To _REF ) and the actual coolant temperature (Tw) and the deviation (Tdw, Tdo) between the actual coolant temperature (To) and the electric coolant pump (W).
A control device for controlling a flow rate of a coolant and a flow rate of a lubricating oil in a heat exchanger, wherein the control of the operation of P) and the operation of an electric lubricating oil pump (OP) are controlled. 2. The throttle opening change rate (Δθ)_TH) Detected
Throttle opening change rate detecting means (S_Three)
The control means (U) provides a reference coolant temperature (T
w_BASE) And reference lubricating oil temperature (To_BASE) Slot
Change rate (Δθ _TH) Based on the target cooling water
Temperature (Tw_REF) And target lubricating oil temperature (To_REF)
The heat exchanger according to claim 1, wherein the calculation is performed.
Control device for cooling water flow rate and lubricating oil flow rate.