JP2008002346A - Lubricating oil supply device for two-cycle internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubricating oil supply device for a two-cycle internal combustion engine capable of suppressing oil consumption by performing the detailed control of the supply of oil depending on the operational state of an internal combustion engine, and preventing exhaust gas from turning into white smoke. <P>SOLUTION: The lubricating oil supply device comprises: constant capacity oil supply means 42, 52 each supplying oil of a constant capacity to a required area of the internal combustion engine by one operation; and an oil supply control means 70 performing the timing-drive control of the constant capacity oil supply means 42 52 based on a valve open time of a fuel injection valve 30 and an operational state of the internal combustion engine. The oil supply control means 70 determines operation timing from the valve open time of the fuel injection valve 30 and the operational state of the internal combustion engine, and the drive control of the constant capacity oil supply control means 70 is performed at each operation timing. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a lubricating oil supply device in a two-cycle internal combustion engine.

In a system in which fuel and oil are separately supplied to a two-cycle internal combustion engine, the oil is supplied by an oil pump to an intake path or a required lubrication site of the internal combustion engine, finally sent to a combustion chamber, burned with fuel, and discharged. .
A normal oil pump driven by an internal combustion engine has a limited range of changes in the discharge amount due to structural limitations, so the discharge amount is set according to the high load range of the internal combustion engine where the most oil supply is required. Has been.

For this reason, oil is excessively supplied in the low load region of the internal combustion engine, resulting in wasting of oil or white smoke of exhaust gas.
Therefore, there is an example in which the amount of oil supply is changed between a low rotation and a low output of the internal combustion engine and a high rotation and a high output (see Patent Document 1).

Japanese Patent Publication No.8-23286

  In the lubricating oil supply device disclosed in Patent Document 1, a first oil passage communicating with an intake port and a second oil passage communicating around a bearing mounting portion of a crankshaft are connected to an oil pump, and the second oil passage is connected to the second oil passage. A passage opening / closing valve is interposed, and the passage opening / closing valve is controlled to open at high rotation and high output and to close at low rotation and low output.

  In other words, the internal combustion engine has a load range that is divided into a high rotation high output side and a low rotation low output side at a middle rotation output, and a high amount of oil on the high rotation high output side has a certain amount more oil than the low rotation low output side. It is controlled to be supplied.

  Therefore, the amount of oil that is always suitable for the load of the internal combustion engine is not always supplied. For example, the setting of the amount of supply by the first oil passage on the low rotation and low output side matches the output during medium rotation. At low rotation and low output, the oil tends to be excessively supplied, the oil is wasted, and white smoke may be generated in the exhaust gas.

  The present invention has been made in view of such points, and the object of the present invention is to finely control the supply of oil according to the operating state of the internal combustion engine to suppress oil consumption and to prevent the exhaust gas from becoming white smoke. A lubricating oil supply device for a two-cycle internal combustion engine is provided.

  In order to achieve the above object, according to the first aspect of the present invention, there is provided a lubricating oil supply for a two-cycle internal combustion engine in which fuel is supplied to a combustion chamber or an intake passage by a fuel injection valve and oil is supplied to a required portion of the internal combustion engine. In the apparatus, a constant capacity oil supply means for supplying a constant volume of oil to a required part of the internal combustion engine in one operation, and the constant capacity oil supply means based on a valve opening time of the fuel injection valve and an operating state of the internal combustion engine. Oil supply control means for timing drive control, wherein the oil supply control means determines an operation timing from a valve opening time of the fuel injection valve and an operating state of the internal combustion engine, and the constant capacity oil for each operation timing. A lubricating oil supply device for a two-cycle internal combustion engine that drives and controls the supply means.

  According to a second aspect of the present invention, in the lubricating oil supply device for a two-cycle internal combustion engine according to the first aspect, the oil supply control means converts the valve opening time of the fuel injection valve based on the operating state of the internal combustion engine. The valve opening time is integrated for each calculation cycle, and the constant-capacity oil supply means is operated at an operation timing when the integrated value is equal to or greater than a predetermined threshold value.

  According to a third aspect of the present invention, in the lubricating oil supply device for a two-cycle internal combustion engine according to the second aspect, the oil supply control means uses at least the engine speed and the throttle opening indicating the operating state of the internal combustion engine as parameters. A map of predetermined mixture ratio coefficients corresponding to combinations of parameter values of the respective parameters, a mixture ratio coefficient corresponding to a combination of parameter values of the current operating state of the internal combustion engine is extracted based on the map, and the fuel injection The valve opening time of the valve is converted by the mixing ratio coefficient to obtain the converted valve opening time.

  According to a fourth aspect of the present invention, in the lubricating oil supply device for a two-cycle internal combustion engine according to the second or third aspect, the threshold value is a predetermined threshold value for each required portion for supplying oil. And

  According to a fifth aspect of the present invention, in the lubricating oil supply device for a two-cycle internal combustion engine according to the third aspect, the parameter indicating the operating state of the internal combustion engine includes an intake negative in addition to the engine speed and the throttle opening. It includes at least one of pressure, intake air temperature, and cooling water temperature.

  According to a sixth aspect of the present invention, in the lubricating oil supply device for a two-cycle internal combustion engine according to any one of the first to fifth aspects, the constant-capacity oil supply means is a plunger pump, and the oil supply The plunger pump is driven for one stroke by one operation instruction from the control means.

  According to a seventh aspect of the present invention, in the lubricating oil supply device for a two-cycle internal combustion engine according to any one of the first to fifth aspects, the constant-capacity oil supply means is connected to the internal combustion engine from the constant hydraulic pressure supply means. An on-off valve is interposed in an oil passage leading to a required portion, and drive control is performed such that the on-off valve is opened for a predetermined time by one operation instruction from the oil supply control means.

  According to the lubricating oil supply device for a two-cycle internal combustion engine according to claim 1, the oil supply control means determines the operation timing from the valve opening time of the fuel injection valve and the operating state of the internal combustion engine, and for each operation timing Since the constant-capacity oil supply means is driven and controlled, the oil supply is finely controlled in accordance with the operating state of the internal combustion engine, and the oil consumption is suppressed by preventing excessive supply of oil while performing sufficient lubrication. It is possible to prevent the flue gas from becoming white smoke by keeping the mixing ratio to be appropriate.

  According to the lubricating oil supply device for a two-cycle internal combustion engine according to claim 2, the oil supply control means calculates a conversion valve opening time obtained by converting the valve opening time of the fuel injection valve based on the operating state of the internal combustion engine for each calculation cycle. The constant-capacity oil supply means is operated at the timing when the integrated value becomes equal to or greater than a predetermined threshold value, so that the fuel / oil mixture ratio is always kept appropriate even in any operating state of the internal combustion engine. be able to.

  According to the lubricating oil supply device for a two-cycle internal combustion engine according to claim 3, the oil supply control means uses at least the engine speed and the throttle opening indicating the operating state of the internal combustion engine as parameters, and combinations of parameter values of the parameters. A map of a predetermined mixture ratio coefficient corresponding to is extracted, a mixture ratio coefficient corresponding to a combination of parameter values of the current operating state of the internal combustion engine is extracted based on the map, and a valve opening time of the fuel injection valve is determined as a mixture ratio coefficient Since the converted valve opening time is calculated by the above, the operating state of the internal combustion engine can be grasped substantially accurately and reflected in the converted valve opening time and the operation timing of the constant capacity oil supply means. It can be kept appropriate.

  According to the lubricating oil supply device for a two-cycle internal combustion engine according to claim 4, since the threshold value is a predetermined threshold value for each required part for supplying oil, finer oil supply control can be performed for each required part. is there.

  According to the lubricating oil supply device for a two-cycle internal combustion engine according to claim 5, the parameters indicating the operating state of the internal combustion engine include intake negative pressure, intake air temperature, cooling water temperature in addition to engine speed and throttle opening. Therefore, the operating state of the internal combustion engine can be grasped more accurately, and the oil supply amount can always be maintained more appropriately.

  According to the lubricating oil supply device for a two-cycle internal combustion engine according to claim 6, the constant capacity oil supply means is a plunger pump, and the plunger pump is driven for one stroke by one operation instruction from the oil supply control means. The oil supply amount can be accurately controlled.

  According to the lubricating oil supply device for a two-cycle internal combustion engine according to claim 7, the constant capacity oil supply means is configured such that an on-off valve is interposed in an oil passage from the constant hydraulic pressure supply means to a required portion of the internal combustion engine, Since the on-off valve is driven and controlled to open for a predetermined time by one operation instruction from the oil supply control means, the oil supply amount can be accurately controlled.

Hereinafter, an embodiment according to the present invention will be described with reference to FIGS.
A two-cycle internal combustion engine 1 according to the present embodiment is a single-cylinder internal combustion engine mounted on a motorcycle.

  In the two-cycle internal combustion engine 1, a cylinder block 3 and a cylinder head 4 are sequentially stacked above the crankcase 2 and are integrally coupled to each other.

A piston 5 is slidably fitted in a cylinder bore 3a formed in the cylinder block 3 in the direction of the central axis of the cylinder bore 3a. The piston 5 and the crankshaft 6 are connected to each other by a connecting rod 7. As the piston 5 reciprocates, the crankshaft 6 in the crank chamber 2a is rotationally driven.
A balancer shaft 8 having a balance weight 9 is provided in the vicinity of the crankshaft 6.

An intake pipe 11 connected to an air cleaner (not shown) and the throttle body 10 is connected to the intake passage 12 of the crankcase 2.
A reed valve 13 is attached to the intake passage 12.

The cylinder block 3 is provided with an exhaust passage 20 on the side opposite to the intake passage 12.
In the vicinity of the exhaust opening 20a that opens to the cylinder bore 3a of the exhaust passage 20, an exhaust control that changes the upper edge position of the exhaust opening 20a so that the exhaust timing can be changed and that the cross-sectional area of the exhaust passage 20 is also variable. A valve 21 is provided.

In the crankcase 2 and the cylinder block 3, a plurality of scavenging passages 15 communicating the cylinder bores 3a and the crank chamber 2a are formed around the cylinder bores 3a excluding the exhaust passage 20 side.
One scavenging passage 16 communicates between the cylinder bore 3a and the downstream side of the reed valve 13 in the intake passage 12.

Cylinder bore 3a The ceiling surface 4b of the cylinder head 4 facing the top surface of the piston 4 is recessed upward to form a combustion chamber 4a.
The recess of the ceiling surface 4b of the cylinder head 4 is formed to be tapered while being deviated from the central axis of the cylinder bore 3a toward the exhaust passage 20 as it goes upward.

The injection port of the fuel injection valve 30 is exposed at the top of the recess of the ceiling surface 4b that is biased toward the exhaust passage 20 side.
Therefore, the fuel injection valve 30 directly injects fuel into the combustion chamber 4a.
The tip electrode of the spark plug 31 protrudes from the top of the recess of the ceiling surface 4 b of the cylinder head 4 to the slope on the intake passage 12 side.

  As described above, the concave surface of the ceiling surface 4b of the combustion chamber 4a in the present two-cycle internal combustion engine 1 is formed so as to be biased toward the exhaust passage 20, so that the cylinder bore 3a particularly from the scavenging passage 16 on the intake passage 12 side during scavenging. The scavenging air that has flowed into the interior flows along the recesses in the ceiling surface 4b that are formed to be biased toward the exhaust passage 20 to form a large vertical vortex as indicated by an arrow in FIG.

  Since this vertical vortex is stratified and the intake fresh air flows outside so as to enclose the residual gas inside, at the spark ignition timing when the piston 4 is located near the top dead center, the vicinity of the electrode of the spark plug 31 is a fresh air component. Therefore, the ignition rate of the two-cycle internal combustion engine 1 is greatly improved.

The oil supply of the two-cycle internal combustion engine 1 is performed to two lubrication sites of the cylinder bore 3 a and the bearing portion of the crankshaft 6.
FIG. 2 is a cross-sectional view of the main part of the oil supply system and a schematic block diagram of the oil supply control system.

Four oil discharge passages 40, 40, 40, 40 are formed from the outer peripheral portion toward the central axis of the cylinder bore 3 a at the lower portion of the cylinder bore 3 a of the cylinder block 3 near the crank chamber 2 a.
Each oil discharge passage 40 has a distal end opened to the cylinder bore 3a, and a check valve 41 is mounted at the base end.

On the other hand, in the crank chamber 2a of the crankcase 2, oil discharge passages 50, 50 are bored toward a pair of left and right crank bearings 6B, 6B that rotatably support the crankshaft 6.
Each oil discharge passage 50 has a distal end facing between the inner and outer rings of the crank bearing 6B, and a check valve 51 is attached to the proximal end portion.

Two electromagnetic solenoid type plunger pumps 42 and 52 are connected to an oil tank 60 provided separately via connecting pipes 43 and 53, respectively.
An oil pipe 44 extending from the discharge port of one electromagnetic solenoid type plunger pump 42 branches into two oil pipes 46 and 46 via a branch pipe 45, and each oil pipe 46 further passes through a branch pipe 47. The oil pipe 48 is branched into two oil pipes 48 and 48, and each oil pipe 48 is connected to a check valve 41 attached to the base end of the oil discharge passage 40.

  The oil pipe 54 extended from the discharge port of the other electromagnetic solenoid type plunger pump 52 is branched into two oil pipes 56 and 56 via a branch pipe 55, and each oil pipe 56 is connected to the base of the oil discharge path 50. It is connected to a check valve 51 attached to the end.

  The electromagnetic solenoid type plunger pumps 42 and 52 are driven and controlled by the electronic control unit 70. The electromagnetic solenoid type plunger pumps 42 and 52 can discharge a fixed amount of oil by driving one stroke of the plunger, and the electronic controller 70 supplies oil by timing controlling the one stroke driving by a pump driving signal. The amount can be controlled.

The electronic control device 70 receives detection signals of various parameters indicating the operating state of the two-cycle internal combustion engine 1.
That is, the parameters include engine speed, throttle opening, intake negative pressure, intake air temperature, cooling water temperature, and the like, and their detection signals are input to the electronic control unit 70.

  The electronic control unit 70 performs arithmetic processing based on the values of these parameters, outputs the pump drive signal to drive and control the electromagnetic solenoid type plunger pumps 42 and 52, and outputs a fuel injection valve drive signal. The fuel injection valve 30 is drive-controlled, and a spark ignition drive signal is output to drive-control the spark plug 31.

Hereinafter, the drive control procedure of the electromagnetic solenoid type plunger pumps 42 and 52 by the electronic control unit 70 will be described with reference to the flowchart shown in FIG.
First, in step 1, it is determined whether or not “1” is set in the integration flag F. If “1” is set, the process jumps to step 5, but if “1” is not set (F = 0). , Go to step 2.

At the beginning of this control, since “1” is not set in the integration flag F, the process proceeds to Step 2.
In step 2, the opening time Tf of the fuel injection valve 30, the engine speed N, and the throttle opening θ are read.

Since the electronic control unit 70 controls the drive of the fuel injection valve 30, the valve opening time Tf of the fuel injection valve 30 is also calculated. In step 2, the calculated valve opening time Tf is read.
The engine speed N and the throttle opening degree θ are detected by sensors arranged at required portions of the internal combustion engine 1, respectively, and the detected engine speed N and the throttle opening degree θ are read.

In the next step 3, a map search is performed for the mixture ratio coefficient K from the read engine speed N and throttle opening θ.
An example of a map for searching for the mixture ratio coefficient K is shown in FIG.
The horizontal axis of the rectangular coordinate indicates the engine speed N, and the vertical axis indicates the throttle opening θ.

  Referring to FIG. 4, the horizontal axis is divided by engine speeds n1, n2, n3, n4,... And divided into engine speed ranges, and the vertical axis is throttle openings .theta.1, .theta.2, .theta.3, .theta.4,. Are divided into each throttle opening area, and a combination area K (i, j) of the engine speed area and the throttle opening area is formed in a lattice shape.

The combination region where the engine speed range is ni-1 ≦ N <ni and the throttle opening range is θi-1 ≦ θ <θi is K (i, j).
A predetermined mixing ratio coefficient K corresponds to each combination region K (i, j).

In the map shown in FIG. 4, the mixture ratio coefficient K is smaller in the combination region K (i, j) closer to the origin of the coordinates.
That is, the mixture ratio coefficient K shows a larger value as the engine speed increases and the output becomes higher.

  This mixing ratio coefficient K is a coefficient for converting the valve opening time Tf of the fuel injection valve 30 into a time (converted valve opening time Tc) that serves as a reference for determining an oil supply amount that makes the mixing ratio according to the operating state of the internal combustion engine. It is.

Therefore, in step 3, the map is searched to extract the mixture ratio coefficient K from the engine speed N and the throttle opening θ.
When the routine proceeds to step 4, the calculated mixture ratio coefficient K is multiplied by the valve opening time Tf of the fuel injection valve 30 to calculate a converted valve opening time Tc (= Tf × K).

In the next step 5, the converted valve opening time Tc is integrated every calculation cycle to calculate the integrated value S.
That is, the present integration value S _P by adding the converted valve opening time Tc to the previous integrated value S _P-1.
S _P = S _P-1 + Tc
The initial value of the integrated value S is 0.

In step 6, the current integrated value S _P which has been calculated, it is determined whether it is above a threshold value Sf to a predetermined.
This threshold value Sf is a threshold value determined in advance for each lubrication site for supplying oil, and an electromagnetic solenoid plunger pump 42 for supplying oil to the cylinder bore 3a and an electromagnetic solenoid plunger pump 52 for supplying oil to the crank bearing 6B. In this case, the threshold values Sf are set to different values.

This integrated value S _P is, until it reaches a threshold Sf, the process proceeds from step 6 to step 7, exits the control flow make a "1" in the integration flag F.
While “1” is set in the integration flag F, the process jumps from step 1 to step 5 to calculate the integrated value S by repeatedly integrating the previously calculated converted valve opening time Tc every calculation cycle.

In Step 6, the current integrated value S _P is, when it is judged equal to or larger than the threshold value Sf, jumps to Step 8, where the electromagnetic solenoid plunger pump is actuated 1, the plunger is constant capacity to move one stroke oil Is discharged.
In step 9, the integrated value S is cleared to 0, and in step 10, the integration flag F is set to “0” and the present control flow is exited.

The above control flow is executed for each calculation cycle.
Accordingly, the process proceeds from Step 1 to Steps 2, 3, and 4 to calculate the converted valve opening time Tc based on the operating state of the internal combustion engine. In Step 5, the converted valve opening time Tc is integrated to calculate the integrated value _SP. the calculated, until the integrated value S _P reaches the threshold value Sf, totalizing is repeated through steps 1 route steps 5,6,7 for each operation cycle.

When the integrated value S _P is equal to or greater than the threshold value Sf, proceeds from step 6 to the root of the steps 8, 9 and 10, the oil is 1 operates the electromagnetic solenoid plunger pump 42 (52) and constant volume supply, the integrated value Since S is set to 0 and the integration flag F is set to “0”, next time, the process proceeds from step 1 to steps 2, 3, and 4, and the conversion valve opening time Tc is newly calculated based on the operating state of the internal combustion engine, and again. 0 integrated operation of the integrated value S _P starts from.

That is, when the integrated value S _P has reached the threshold Sf electromagnetic solenoid plunger pump 42 (52) is operated 1 as operation timing, a volume of oil is supplied into the cylinder bore 3a and in the crank bearing 6B.

FIG. 5 shows a simplified example of the change of the integrated value S in the drive control of the electromagnetic solenoid type plunger pump.
The change of the integrated value S at the time of high rotation and high output is indicated by a solid line, and the change of the integrated value S at the time of low rotation and low output is indicated by a broken line.

  As shown in FIG. 5, the integrated value S for integrating the converted valve opening time Tc for each calculation cycle rises stepwise, and the amount of change in one calculation cycle (the height of one step of the step) is converted to valve opening. This corresponds to time Tc.

The time when the integrated value S reaches the threshold value Sf is the operation timing. At this operation timing, one electromagnetic solenoid plunger pump is operated, the integrated value S is cleared, the integration operation starts again, and rises in a stepped manner. Repeated.
The time t until the integrated value S reaches the threshold value Sf corresponds to a cycle in which the step-up series of the integrated value S is repeated, that is, a cycle in which the electromagnetic solenoid type plunger pump 52 is operated once.

  The mixture ratio coefficient K retrieved from the map shown in FIG. 4 is larger at high rotation and high output than at low rotation and low output, so the converted valve opening time Tc (= Tf × K) is also high. The output time is longer than the low rotation and low output.

  Therefore, as shown in FIG. 5, the amount of change in one calculation cycle (converted valve opening time Tc) is larger at the time of high rotation and high output (solid line) than at the time of low rotation and low output (broken line). The height is high.

Accordingly, the time t until the integrated value S reaches the threshold value Sf is shorter at high rotation and high output (solid line) than at low rotation and low output (broken line).
That is, the period t during which the electromagnetic solenoid type plunger pump is actuated 1 is shorter at the time of high rotation and high output than at the time of low rotation and low output, and the amount of oil supply is increased accordingly.

  The period t during which one electromagnetic solenoid type plunger pump is actuated changes according to the change in the operation state from the low rotation low output state to the high rotation high output state of the two-cycle internal combustion engine 1, and accordingly, according to the operation state. The oil supply is finely controlled.

  Therefore, sufficient oil is supplied to the lubricated part at high rotation and high output, and at low rotation and low output, the oil supply is suppressed to prevent excessive supply and to reduce oil consumption. It can be appropriately controlled to prevent the exhaust gas from becoming white smoke particularly at the time of low rotation and low output.

  In the electromagnetic solenoid type plunger pump 42 that supplies oil to the cylinder bore 3a and the electromagnetic solenoid type plunger pump 52 that supplies oil to the crank bearing 6B, the threshold values Sf are set to different values. The reciprocating sliding portion of the piston 5 and the crank bearing 6B can be properly lubricated.

  In the above embodiment, the engine speed N and the throttle opening θ are used as parameters indicating the operating state of the internal combustion engine for oil supply control. In addition to these, the intake negative pressure, the intake air temperature, the coolant temperature By adding at least one of the above to the parameters and retrieving the mixing ratio coefficient K from these parameters to obtain the converted valve opening time Tc, finer oil supply control is possible.

  The above is an embodiment in which the oil is supplied by an electromagnetic solenoid type plunger pump. However, any configuration may be used as long as a constant volume of oil is supplied by one operation. An on-off valve may be provided in an oil passage leading to a lubrication site, and the on-off valve may be opened for a predetermined time and supplied with a constant volume of oil in response to one operation instruction.

1 is a longitudinal sectional view of a two-cycle internal combustion engine according to an embodiment of the present invention. It is explanatory drawing which shows simultaneously the principal part cross section of an oil supply system, and the schematic block diagram of an oil supply control system. It is a flowchart which shows the drive control procedure of a plunger pump. It is a coordinate which shows the example of the map which searches the mixture ratio coefficient K. It is a figure which shows the example of the change of an integrated value.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... 2 cycle internal combustion engine, 2 ... Crank case, 3 ... Cylinder block, 3a ... Cylinder bore, 4 ... Cylinder head, 5 ... Piston, 6 ... Crankshaft, 6B ... Crank bearing, 10 ... Throttle body, 12 ... Intake passage, 15, 16 ... scavenging passage, 20 ... exhaust passage, 30 ... fuel injection valve, 31 ... spark plug,
40 ... oil discharge path, 41 ... check valve, 42 ... electromagnetic solenoid plunger pump,
50 ... Oil discharge path, 51 ... Check valve, 52 ... Electromagnetic solenoid plunger pump,
60 ... oil tank, 70 ... electronic control unit.

Claims (7)

In a two-cycle internal combustion engine lubricating oil supply device in which fuel is supplied to a combustion chamber or an intake passage by a fuel injection valve, and oil is supplied to a required portion of the internal combustion engine.
Constant capacity oil supply means for supplying a constant volume of oil to a required part of the internal combustion engine in one operation;
An oil supply control means for controlling the timing of the constant-capacity oil supply means based on the valve opening time of the fuel injection valve and the operating state of the internal combustion engine;
The oil supply control means determines an operation timing from a valve opening time of the fuel injection valve and an operating state of the internal combustion engine, and drives and controls the constant-capacity oil supply means for each operation timing. Lubricating oil supply device for cycle internal combustion engine. The oil supply control means includes
The converted valve opening time obtained by converting the valve opening time of the fuel injection valve based on the operating state of the internal combustion engine is integrated for each calculation cycle, and the time when the integrated value becomes equal to or greater than a predetermined threshold is set as the operation timing. 2. The lubricating oil supply device for a two-cycle internal combustion engine according to claim 1, wherein the capacity oil supply means is operated. The oil supply control means includes
A map of a predetermined mixing ratio coefficient corresponding to a combination of parameter values of the respective parameters with at least the engine speed and the throttle opening indicating the operating state of the internal combustion engine as parameters,
Extracting a mixing ratio coefficient corresponding to a combination of parameter values of the current operating state of the internal combustion engine based on the map;
The lubricating oil supply device for a two-cycle internal combustion engine according to claim 2, wherein the converted valve opening time is obtained by converting the valve opening time of the fuel injection valve by the mixing ratio coefficient.   The lubricating oil supply device for a two-cycle internal combustion engine according to claim 2 or 3, wherein the threshold value is a predetermined threshold value for each required portion for supplying oil.   The parameter indicating the operating state of the internal combustion engine includes at least one of intake negative pressure, intake air temperature, and cooling water temperature in addition to the engine speed and throttle opening. Lubricating oil supply device for a two-cycle internal combustion engine. The constant volume oil supply means is a plunger pump,
The lubricating oil supply device for a two-cycle internal combustion engine according to any one of claims 1 to 5, wherein the plunger pump is driven by one stroke in response to one operation instruction from the oil supply control means. The constant-capacity oil supply means is configured such that an open / close valve is interposed in an oil path from the constant hydraulic pressure supply means to a required lubrication site of the internal combustion engine,
The lubricating oil for a two-cycle internal combustion engine according to any one of claims 1 to 5, wherein the on-off valve is driven and controlled to open for a predetermined time by one operation instruction from the oil supply control means. Feeding device.

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