JPH0868308A - Lubricating oil supplying device for internal combustion engine - Google Patents

Abstract

PURPOSE: To precisely change over opening/closing characteristics of intake exhaust valves without influence of injection of lubricating oil from an oil jet. CONSTITUTION: A valve system changeover actuator 14 changes over opening/ closing operation characteristics of intake exhaust valves according to hydraulic pressure. A valve system changeover control valve 13 adjusts hydraulic pressure introduced from an oil pump 5 to the valve system changeover actuator 14 according to operation conditions. A hydraulic supply control valve 10 adjusts a distribution ratio of lubricating oil discharged from the oil pump 5 to each item of an engine. In a lubricating oil supplying device for an internal combustion engine having above-mentioned members, the hydraulic pressure supply control valve 10 is operated interlockingly with the operation of the valve system changeover control valve 13.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a lubricating oil supply system for an internal combustion engine.

[0002]

2. Description of the Related Art As a lubricating oil supply device for an automobile engine, there is a conventional device shown in FIG.

To explain this, a constant capacity type oil pump 161 is driven by an engine, and the oil pump 1
The lubricating oil discharged from 61 is supplied to the regulator valve 162,
It is guided to an oil gallery 165 via a relief valve 163 and an oil filter 164. Oil gallery 165
Is an engine lubrication portion 167 of a crankshaft bearing or a valve train on a cylinder head, an oil jet 168 for cooling a piston, and a valve train switching actuator 171 for switching open / close operation characteristics of intake / exhaust valves in response to hydraulic pressure. And communicates with each.

As shown in FIG. 17, the oil jet 17
0 is connected to the oil gallery 165 formed in the cylinder block 173 via the valve 172. When the oil pressure guided through the oil gallery 165 exceeds a predetermined value when the engine is rotating at high speed, the valve 172 opens, and the lubricating oil is injected from the oil jet 170 toward the back surface of the piston 174, and the lubricating oil causes the piston 174. Also, the heat of the cylinder bore and the like is removed (see, for example, JP-A-52-92037).

When the discharge pressure of the oil pump 161 is guided through the valve switching control valve 166 according to the operating conditions, the valve switching actuator 171 responds to this hydraulic pressure to open and close the intake valve or the exhaust valve. The cams involved are selectively switched to control the intake / exhaust timing or intake / exhaust amount (see, for example, JP-A-63-167016 and JP-A-63-57805).

[0006]

However, when the engine operating condition shifts from the low speed region to the high speed region, a valve 172 for introducing lubricating oil into the oil jet 168,
The valve operation switching control valves 166 that guide the operating oil pressure to the valve operation switching actuator 171 are set to open at respective predetermined operating points, but both may open at almost the same time. In this case, when the injection of a large amount of lubricating oil from the oil jet 170 is started, the valve closing operation of the regulator valve 162 that maintains the hydraulic pressure is delayed, and the discharge pressure of the oil pump 161 is temporarily reduced. When the control valve 166 is opened almost at the same time, the hydraulic pressure guided to the valve actuation switch actuator 171 does not immediately rise, the cam switching operation is performed after a predetermined operating point, and a torque step is generated, which causes a driver's inconvenience. May give pleasure.

In view of the above problems, the present invention makes it possible to accurately adjust the lift characteristics of intake and exhaust valves in a lubricating oil supply system for an internal combustion engine without being affected by the injection of lubricating oil from an oil jet. The purpose is to switch.

[0008]

According to the first aspect of the present invention,
From the oil pump, a valve switching actuator that switches the open / close operation characteristics of the intake / exhaust valve in response to the oil pressure, a valve switching control valve that adjusts the oil pressure guided from the oil pump to the valve switching actuator according to operating conditions In a lubricating oil supply device for an internal combustion engine, which includes a hydraulic pressure supply control valve that adjusts a ratio of distributing the discharged lubricating oil to each part of the engine, the hydraulic pressure supply control valve is operated in conjunction with the operation of the valve switching control valve. A control means is provided.

According to a second aspect of the present invention, there is provided a lubricating oil supply device for an internal combustion engine, which includes a valve switching actuator for switching the opening / closing operation characteristics of intake / exhaust valves in response to hydraulic pressure, and a hydraulic pressure introduced from an oil pump to the valve switching actuator. An electromagnetic valve switching control valve that adjusts according to operating conditions, an electromagnetic hydraulic supply control valve that adjusts the ratio at which the lubricating oil discharged from the oil pump is distributed to various parts of the engine, and the operating conditions And a control means for activating the valve switching control valve and for activating the hydraulic pressure supply control valve after a delay time has elapsed after activating the valve switching control valve.

According to another aspect of the present invention, there is provided a lubricating oil supply apparatus for an internal combustion engine, wherein a valve operating actuator for switching the opening / closing operating characteristics of intake / exhaust valves in response to hydraulic pressure and an oil pressure introduced from an oil pump to the valve operating actuator. An electromagnetic valve switching control valve that adjusts according to operating conditions, an electromagnetic hydraulic supply control valve that adjusts the ratio that distributes the lubricating oil discharged from the oil pump to various parts of the engine, and the discharge pressure of the oil pump. And a control means for actuating the valve switching control valve according to operating conditions, and for actuating the hydraulic pressure supply control valve after the discharge pressure of the oil pump fluctuates with the actuation of the valve switching control valve. Equipped with.

According to a fourth aspect of the present invention, the valve operating mechanism for switching the opening / closing operation characteristics of the intake / exhaust valve in response to the hydraulic pressure and the hydraulic pressure guided from the oil pump to the valve operating actuator are adjusted according to operating conditions. In a lubricating oil supply apparatus for an internal combustion engine, the hydraulic oil supply control valve is operated by a valve switching control valve for controlling the internal combustion engine, and a hydraulic pressure supply control valve for adjusting the ratio of distributing the lubricating oil discharged from the oil pump to each part of the engine. The hydraulic pressure introduced from the switching control valve to the valve switching actuator is used as a pilot hydraulic pressure for switching operation, and the set hydraulic pressure at which the hydraulic pressure supply control valve operates is set higher than the set hydraulic pressure at which the valve switching actuator operates.

[0012]

A lubricating oil supply system for an internal combustion engine according to claim 1
By operating the hydraulic pressure supply control valve in conjunction with the operation of the valve shift control valve, the operation switching of the valve shift actuator and the hydraulic pressure supply control valve is integrated and controlled based on one operating condition judgment result. The control system can be simplified, and the lubricating oil supply system can be enhanced in function and performance.

Since the valve switching control valve operates before the discharge pressure of the oil pump temporarily increases or decreases due to the operation of the hydraulic pressure supply control valve, the switching operation of the valve switching actuator is performed at a predetermined operating point and the torque is changed. It is possible to prevent a step from being generated and giving a driver an unpleasant feeling.

In the lubricating oil supply system for an internal combustion engine according to a second aspect of the present invention, one operating condition determination result is obtained by operating the hydraulic pressure supply control valve after a delay time has elapsed after operating the valve switching control valve. Based on this, it becomes possible to integrally control each operation switching of the valve switching actuator and the hydraulic pressure supply control valve, and the control system can be simplified, and the lubricating oil supply system can be made highly functional and have high performance.

Since the valve switching control valve operates before the discharge pressure of the oil pump temporarily increases or decreases due to the operation of the hydraulic pressure supply control valve, the switching operation of the valve switching actuator is performed at a predetermined operating point and the torque is changed. It is possible to prevent a step from being generated and giving a driver an unpleasant feeling.

According to the third aspect of the present invention, the lubricating oil supply device for an internal combustion engine operates under one operating condition by operating the hydraulic pressure supply control valve after the discharge pressure of the oil pump fluctuates with the operation of the valve switching control valve. Based on the judgment result, it is possible to integrate and control each operation switching of the valve operating actuator and the hydraulic supply control valve, simplifying the control system and improving the function and performance of the lubricating oil supply system. Be peeled off.

Since the valve switching control valve operates before the discharge pressure of the oil pump temporarily increases or decreases due to the operation of the hydraulic pressure supply control valve, the switching operation of the valve switching actuator is performed at a predetermined operating point and the torque is changed. It is possible to prevent a step from being generated and giving a driver an unpleasant feeling.

As described above, it is judged whether the switching operation of the valve switching actuator is completed based on the detected value of the discharge pressure of the oil pump and the hydraulic pressure supply control valve is operated to switch the valve switching actuator. The time when the operation of the hydraulic pressure supply control valve is delayed with respect to the operation can be minimized.

According to another aspect of the present invention, there is provided a lubricating oil supply device for an internal combustion engine, wherein the hydraulic pressure supply control valve is configured to perform a switching operation using the hydraulic pressure introduced from the valve switching control valve to the valve switching actuator as a pilot hydraulic pressure. Is set higher than the set hydraulic pressure at which the valve switching actuator operates, so when the hydraulic pressure guided to the valve switching actuator increases due to the operation of the valve switching control valve, the valve switching actuator is switched. Since the hydraulic pressure supply control valve operates in conjunction with this, the valve switching control valve operates before the oil pump discharge pressure temporarily increases or decreases due to the hydraulic pressure supply control valve's operation, so switching of the valve switching actuator The operation is performed at a predetermined driving point, and it is possible to prevent a torque step from being generated and giving a driver discomfort.

When the hydraulic pressure guided to the valve switching actuator is reduced by the operation of the valve switching control valve, the hydraulic supply control valve is activated before the switching operation of the valve switching actuator. When the discharge pressure of the oil pump temporarily rises during the operation of, there is a possibility that the operation of the valve switching actuator may be delayed and a torque step may occur, but if this torque step occurs in the low rotation range where the generated torque is small, The torque difference is small compared to the torque difference that occurs in the high speed range, and there is almost no fear of giving a driver discomfort.

[0021]

Embodiments of the present invention will be described below with reference to the accompanying drawings.

As shown in FIG. 1, the constant capacity oil pump 5 is driven by the engine 2 and supplies the lubricating oil sucked from the oil pan 18 to each part of the engine through the first oil supply passage 11 and the second oil supply passage 12. To do.

The relief valve 6 connected to the discharge side of the oil pump 5 opens when the discharge pressure of the oil pump 5 exceeds a predetermined value and functions to suppress the discharge pressure below a predetermined value. .

The second oil supply passage 12, which is connected to the discharge side of the oil pump 5 via the hydraulic pressure supply control valve 10, communicates with the oil jet 9 and also communicates with the crankshaft bearing 8 via the orifice 3. .

As shown in FIG. 2, the hydraulic pressure supply control valve 10 includes a spool valve 102 biased in a valve closing direction via a return spring 101 and an electromagnetic valve for driving the spool valve 102 against the return spring 101. The actuator 103 is provided. When the electromagnetic actuator 103 is not energized, it is held in a position that closes the second oil supply passage 12 by the urging force of the return spring 101 as shown in FIG.
As shown in FIG. 5, the second oil supply passage 12 is held in a position against the urging force of the return spring 101.

As shown in FIG. 4, the oil jet 9 is connected to the second oil supply passage 12 formed in the cylinder block 105. Lubricating oil guided through the second oil supply passage 12 is injected toward the rear surface of the piston 107,
This lubricating oil removes heat from the piston 107 and the cylinder bore. The injection of the lubricating oil from the oil jet 9 is controlled only by the hydraulic pressure supply control valve 10, and it is not necessary to provide a valve or the like having a predetermined valve opening pressure for each cylinder as in the conventional device.

On the other hand, the first oil supply passage 11 communicates with the valve operating system 7 through the orifice 1, communicates with the bearing 8 of the crankshaft through the orifice 2, and operates through the valve switching control valve 13. It communicates with the valve switching actuator 14.

The valve operating actuator 14 shown in FIG.
Is composed of a valve lift adjusting mechanism 40 and a valve timing adjusting mechanism 70 shown in FIG.

The valve lift adjusting mechanism 40 will be described below. Each cylinder is provided with a single main rocker arm 81 corresponding to the two intake valves 89. The base end of the main rocker arm 81 is swingably supported by the cylinder head 69 via the main rocker shaft 83 common to each cylinder, and the tip of the main rocker arm 81 is brought into contact with the top of the stem of each intake valve 89. 90 is fastened via the nut 91.

The main rocker arm 81 has a shaft 93.
A roller 94 is rotatably connected to the roller via a needle bearing, and the low speed cam 21 is brought into rolling contact with the roller 94.

The main rocker arm 81 is formed in a substantially rectangular shape in plan view, and the main rocker arm 81 has a roller 94.
A sub-rocker arm 82 is provided side by side. The base end of the sub rocker arm 82 is connected to the main rocker arm 81 via a sub rocker shaft 96 so as to be relatively rotatable. The sub-rocker shaft 96 is slidably fitted in a hole 97 formed in the sub-rocker arm 82, and is press-fitted into a hole 98 formed in each main rocker arm 81.

The sub-rocker arm 82 does not have a portion that comes into contact with the intake valve 89, and a cam follower portion 23 that slidably contacts the high-speed cam 22 is formed at the tip thereof so as to project in an arc shape, and the cam follower portion 23 is provided below it. A lost motion spring 25 that presses against the high speed cam 22 is interposed.

The main rocker arm 81 is integrally formed with a cylindrical recess 26 located directly below the sub rocker arm 82 and having the lost motion spring 25 interposed therebetween. The lower end of the coiled lost motion spring 25 is seated on the bottom surface 26a of the recess 26, and the upper end of the coiled lost motion spring 25 is in contact with the follower portion 28 formed integrally with the sub-rocker arm 82 via the retainer 27 slidably fitted in the recess 26. Contact.

The low speed cam 21 and the high speed cam 22 are integrally formed on a common cam shaft 72, and have different shapes (different sizes) so as to satisfy the valve lift characteristics required at low engine speed and high engine speed. (Including similar shapes). In this embodiment, as shown in FIG. 7, the high speed cam 22 has a profile in which both the valve lift amount and the valve opening period are larger than the low speed cam 21. Here, the valve lift amount and the valve opening period are both increased. If the lift amount of the cam that drives the exhaust valve is h ₁ , the lift amount of the high speed cam 22 is h ₃ , and the lift amount of the low speed cam 21 is h ₂ , then there is a relationship of h ₃ > h ₁ > h _2. There is.

As a connecting drive means capable of locking the relative rotation of both rocker arms 81 and 82, the plungers 33, 38 are provided across the main rocker arm 81 and the sub rocker arm 82.
The first oil supply passage 11 is connected to the back of the plunger 33 while the return spring 38 is interposed behind the plunger 34.

When the operating oil pressure introduced from the first oil supply passage 11 is low, the plungers 33 and 31 are accommodated in the sub-rocker arm 82 and the main rocker arm 81 by the urging force of the return spring 38 and do not restrain the swinging of both. On the other hand, when the operating oil pressure introduced from the first oil supply passage 11 rises, the plungers 33 and 31 slide while compressing the return spring 38 and are fitted over the main rocker arm 81 and the sub-rocker arm 82, so that both Swing together.

The first oil supply passage 11 is provided through the insides of the main rocker arm 81 and the main rocker shaft 83. The discharge hydraulic pressure of the oil pump 5 is guided to the first oil supply passage 11 via a solenoid switching valve 45 that constitutes the valve switching control valve 13 at a predetermined high rotation speed.

Next, the valve timing adjusting mechanism 70 will be described. The valve timing adjusting mechanism 70 is provided between the cam shaft 72 and the cam pulley 71, and changes the phase angle between the cam shaft 72 and the cam pulley 71 so as to change the opening / closing timing of the intake valve 89. Rotational force from a crankshaft (not shown) is transmitted to the cam pulley 71 via the timing belt 66.

At the end of the camshaft 72, a cylindrical inner housing 65 is fastened via bolts 64. A cylindrical outer housing 63 that is rotatably fitted to the inner housing 65 is provided, and a cam pulley 71 is formed integrally with the outer housing 63.

A ring-shaped helical gear 73 is interposed between the inner housing 65 and the outer housing 63. Helical splines are formed on the inner and outer circumferences of the helical gear 73, and each helical spline meshes with the outer circumference of the inner housing 65 and the inner circumference of the outer housing 63, and the helical gear 73 moves axially against the return spring 74. As the inner housing 65 rotates relative to the outer housing 63, the cam pulley 7
The phase angle in the rotation direction of the camshaft 72 with respect to 1 changes.

A hydraulic chamber 75 is defined between the inner housing 65, the outer housing 63 and the helical gear 73. When the hydraulic pressure guided to the hydraulic chamber 75 rises above a predetermined value, the helical gear 73 moves from the initial position to the right in the figure against the return spring 74.
The cam shaft 72 is adapted to rotate in a direction that advances the opening / closing timing of the intake valve 89.

As a result, when the helical gear 73 is in the initial position, the opening and closing timing of the intake valve 89 is delayed as shown by the solid line in FIG. 7, and when the helical gear 73 is displaced to the maximum, the broken line in FIG. As shown by, the opening / closing timing of the intake valve 89 is advanced.

The hydraulic chamber 75 is formed in a shaft hole 78 formed inside the camshaft 72, an oil gallery 59 formed in the cylinder head 69, an orifice 77, and a cylinder block 68 to form the first oil supply passage 11. The discharge hydraulic pressure from the oil pump 5 is introduced through the constituent main gallery 58.

As the valve switching control valve 13, an electromagnetic switching valve 79 is provided at the other end of the camshaft 72, the opening / closing of which is controlled according to engine operating conditions. The electromagnetic switching valve 79 opens the shaft hole 78 when not energized to reduce the hydraulic pressure introduced to the hydraulic chamber 75 as shown in the figure, and closes the shaft hole 78 when energized to increase the hydraulic pressure introduced to the hydraulic chamber 75. ing.

As a control means for the valve lift adjusting mechanism 40, the valve timing adjusting mechanism 70 and the hydraulic pressure supply control valve 10, the control unit 5 for controlling the energization of the electromagnetic switching valve 45, the electromagnetic switching valve 79 and the hydraulic pressure supply control valve 10 is controlled.
1 is provided.

The control unit 51 inputs an engine rotation signal, an engine load signal, a cooling water temperature signal, a lubricating oil temperature signal, an intake supercharging pressure signal by a supercharger, and the like, and based on these detected values. The valve lift characteristics are smoothly switched while suppressing a rapid change in engine torque (torque step).

As shown in FIG. 8, the control unit 51 delays the opening / closing timing of the intake valve 89 at the time of low rotation and low load, and reduces the lift amount of the intake valve 89 via the low speed cam 21 to reduce the low rotation and high load. Sometimes the opening / closing timing of the intake valve 89 is advanced, and the intake valve 8
The valve timing adjusting mechanism 70 and the valve lift adjusting mechanism 40 are arranged so that the lift amount of the intake valve 89 is decreased, the opening / closing timing of the intake valve 89 is delayed at the time of high rotation, and the lift amount of the intake valve 89 is increased via the high speed cam 22. To drive.

Based on the above structure, the valve opening / closing timing of the intake valve is delayed via the valve timing adjusting mechanism 70 and the lift amount of the intake valve 89 is reduced via the valve lift adjusting mechanism 40 when the engine speed is low and the load is low. By reducing the overlap, the blowback of exhaust gas from the exhaust port to the cylinder can be suppressed, the residual gas ratio can be reduced, combustion can be stabilized, idle stability can be improved, and fuel consumption can be reduced.

By advancing the opening / closing timing of the intake valve 89 via the valve timing adjusting mechanism 70 at the time of low rotation and high load, the air-fuel mixture sucked into the cylinder is discharged to the intake port near the bottom dead center of the intake stroke. Can be suppressed, and the intake charging efficiency can be improved. At this time, by reducing the lift amount of the intake valve via the valve lift adjustment mechanism,
Avoid excessive valve overlap,
Residual gas can be reduced and generated torque can be increased.

Valve timing adjusting mechanism 70 during high rotation
By delaying the opening / closing timing of the intake valve 89 via the valve lift amount and increasing the lift amount of the intake valve 89 via the valve lift adjusting mechanism 40, the intake supercharging effect can be utilized to increase the intake charging efficiency. Moreover, by increasing the valve overlap, the negative pressure wave generated in the exhaust pipe can provide the exhaust gas scavenging effect, and the exhaust loss can be reduced to improve the output. That is, in the latter half of the exhaust stroke, a negative pressure is generated by the exhaust gas moving in the exhaust pipe, and the intake flow flows into the cylinder during the overlap period, so that the scavenging effect of the exhaust gas can be enhanced.

The control unit 51 includes an intake valve 89
During the operation for switching the valve lift characteristic of, the valve timing adjusting mechanism 70 and the valve lift adjusting mechanism 40 are switched with a time lag to alleviate the torque step difference of the engine generated at the time of switching.

The control unit 51 first switches the electromagnetic switching valve 45 of the valve lift adjusting mechanism 40 from OFF to ON under the operating condition of shifting from low rotation and low load to high rotation, and then the valve timing adjusting mechanism 70 is operated. The electromagnetic switching valve 79 is switched from OFF to ON. Then, under an operating condition that shifts from high rotation to low rotation and low load, the electromagnetic switching valve 79 of the valve timing adjustment mechanism 70 is first switched from ON to O.
After switching to FF, the electromagnetic switching valve 45 of the valve lift adjusting mechanism 40 is switched from ON to OFF.

Further, the control unit 51 operates the hydraulic pressure supply control valve 10 in conjunction with the operation of the valve lift adjusting mechanism 40 which constitutes the valve operating actuator 14. That is, when the rotation speed is low, the lift amount of the intake valve 89 is reduced via the valve lift adjustment mechanism 40, and the oil pressure supply control valve 10 is closed to close the oil jet 9
Stops the injection of lubricating oil from. At the time of high rotation, the lift amount of the intake valve 89 is increased via the valve lift adjusting mechanism 40, and the hydraulic pressure supply control valve 10 is opened to inject the lubricating oil from the oil jet 9.

Based on the above construction, as shown in FIG. 9, by stopping the injection of the lubricating oil from the oil jet 9 at the time of low rotation, the supercooling of the piston 36 is prevented. Further, since the lubricating oil is supplied to the bearing 8 of the crankshaft via only the orifice 2, the temperature of the lubricating oil interposed in the bearing 8 is kept high and the friction is reduced.

The piston 36 is cooled by injecting the lubricating oil from the oil jet 9 at the time of high rotation. Further, the lubricating oil is supplied to the bearing 8 of the crankshaft through both the orifice 2 and the orifice 3, thereby preventing the bearing 8 from being overheated.

By operating the hydraulic pressure supply control valve 10 in conjunction with the operation of the valve operating actuator 14,
It becomes possible to integrally control each operation switching of the valve operating actuator 14 and the hydraulic pressure supply control valve 10 based on one operation condition determination result, and the control unit 5
The control operation in 1 can be simplified, and the lubricating oil supply system can be made highly functional and highly efficient.

By the way, when the injection of a large amount of lubricating oil from the oil jet 9 is started when shifting from the low speed region to the high speed region, the closing operation of the relief valve 6 for maintaining the hydraulic pressure is delayed,
The discharge pressure of the oil pump 5 temporarily drops. Therefore, when shifting from the low speed region to the high speed region, the electromagnetic switching valve 45
When the valve closing operation and the opening operation of the hydraulic pressure supply control valve 10 are simultaneously performed, the discharge pressure of the oil pump 5 is temporarily reduced, so that the operation of the valve lift adjusting mechanism 40 is performed from a predetermined operating point. If it is performed with a delay, a torque step may occur, which may give the driver an unpleasant feeling.

When shifting from the high speed range to the low speed range,
When the injection of a large amount of lubricating oil from the oil jet 9 is stopped, the opening operation of the relief valve 6 that maintains the hydraulic pressure is delayed, and the discharge pressure of the oil pump 5 temporarily rises. For this reason, when the electromagnetic switching valve 45 is opened and the hydraulic pressure supply control valve 10 is closed at the same time when shifting from the high speed range to the low speed range, the discharge pressure of the oil pump 5 is temporarily reduced. Due to the rise, the operation of the valve lift adjusting mechanism 40 may be performed later than a predetermined operating point, and a torque step may occur, which may give a driver discomfort. However, the torque step generated at the time of transition from the high speed range to the low speed range is smaller than the torque step generated at the time of transition from the low speed range to the high speed range because it occurs in the low rotation range where the generated torque is small.

In response to this, the valve lift adjusting mechanism 4
0 and the valve timing adjusting mechanism 70 until the operation of the valve switching actuator 14 is completed, the control unit 51 uses the electromagnetic switching of the valve lift adjusting mechanism 40 so as not to operate the hydraulic pressure supply control valve 10. ON / OFF of the valve switching control valve 13 including the valve 45 and the electromagnetic switching valve 79 of the valve timing adjusting mechanism 70
Is issued, a predetermined delay time Δt (for example, 0.5
Seconds), the hydraulic pressure supply control valve 10 is turned on / off.
Control to instruct F is performed.

The flowchart of FIG. 10 shows that the hydraulic pressure supply control valve 1 is operated after the delay time has elapsed after the valve switching control valve 13 executed in the control unit 51 was operated.
A control program for operating 0 is shown, which is executed at regular intervals.

First, in step A1, signals such as engine speed, cooling water temperature and engine load are input. Then, in step A2, it is determined whether or not the switching conditions for the valve operating control valve 13 and the hydraulic pressure supply control valve 10 are satisfied.

After the engine cooling water temperature is higher than a predetermined value, when the engine speed exceeds a predetermined value, the valve switching control valve 13 and the hydraulic pressure supply control valve 10 are switched.

When the engine cooling water temperature is below a predetermined temperature, the valve switching control valve 1 is operated regardless of the engine speed.
3 and the hydraulic pressure supply control valve 10 are not switched, and the hydraulic pressure control valve 10 is also maintained in the closed state, and the injection of the lubricating oil from the oil jet 9 is stopped.

If the switching condition is satisfied, step A3
Then, a command to turn ON / OFF the valve switching control valve 13 is given.

Then, in step A4, it is determined whether a predetermined delay time Δt (for example, 0.5 seconds) has elapsed.

If the delay time Δt has elapsed, step A
Proceed to step 5 to command ON / OFF of the hydraulic pressure supply control valve 10.

In this way, when shifting from the low speed range to the high speed range, the hydraulic pressure supply control valve 10 is opened after the delay time Δt has elapsed after the valve switching control valve 13 was closed. . Since the switching operation of the valve operation switching actuator 14 ends while the delay time Δt elapses, even if the discharge pressure of the oil pump 5 temporarily drops when the hydraulic pressure supply control valve 10 closes, it is affected by this. It is possible to prevent the valve operating actuator 14 from being switched at a predetermined operating point without causing a torque step and causing a driver to feel uncomfortable.

When shifting from the high speed range to the low speed range,
The hydraulic pressure supply control valve 10 is closed after the delay time Δt has elapsed after the valve operating switching control valve 13 was opened. While the delay time Δt elapses, the valve operating actuator 14
Therefore, even if the discharge pressure of the oil pump 5 is temporarily increased when the hydraulic pressure supply control valve 10 is closed, the switching operation of the valve operating actuator 14 is not affected by this. It is possible to prevent the driver from feeling uncomfortable due to a torque step.

Next, another embodiment shown in FIG. 11 will be described. It should be noted that the same reference numerals are used for the portions corresponding to those in FIG.

A hydraulic sensor 15 for detecting the hydraulic pressure Pv of the first oil supply passage 11 connecting the valve switching control valve 13 and the valve switching actuator 14 is provided.

The control unit 51 controls the oil pressure sensor 1 after the valve switching control valve 13 is instructed to be turned ON / OFF.
After it is determined that the hydraulic pressure Pv detected by 5 increases or decreases beyond a predetermined value, the hydraulic pressure supply control valve 10 is turned on.
Performs control to command OFF.

In the flowchart of FIG. 12, the hydraulic pressure supply control valve 1 is operated after a delay time has elapsed after the valve switching control valve 13 executed in the control unit 51 was operated.
A control program for operating 0 is shown, which is executed at regular intervals.

First, in step B1, signals such as engine speed, cooling water temperature and engine load are input. Then, the process proceeds to step B2, where it is determined whether or not the conditions for switching the valve operating switching control valve 13 and the hydraulic pressure supply control valve 10 are satisfied.

If the switching condition is satisfied, step B3
Then, a command to turn ON / OFF the valve switching control valve 13 is given.

Then, the process proceeds to step B4, where the hydraulic pressure Pv detected by the hydraulic pressure sensor 15 is the predetermined value Pv1 or Pv.
It is determined whether to increase or decrease beyond v2.

When it is determined that the hydraulic pressure Pv has increased or decreased beyond the predetermined value Pv1 or Pv2, the process proceeds to step B5 to instruct ON / OFF of the hydraulic pressure supply control valve 10.

Even when the valve switching control valve 13 is closed at the time of shifting from the low speed region to the high speed region, the hydraulic pressure Pv does not increase while the valve switching actuator 14 is being switched. When the valve switching actuator 14 completes the switching operation, the hydraulic pressure Pv rises above a predetermined value Pv1.

Therefore, when shifting from the low speed range to the high speed range, the hydraulic pressure Pv introduced to the valve actuation switching actuator 14 after the valve actuation switching control valve 13 closes is a predetermined value Pv1.
Even if the discharge pressure of the oil pump 5 is temporarily reduced when the hydraulic pressure supply control valve 10 is closed after the hydraulic pressure supply control valve 10 is opened after the hydraulic pressure supply control valve 10 has risen over the range, it is affected by this. It is possible to prevent the valve operating actuator 14 from being switched at a predetermined operating point without causing a torque step and causing a driver to feel uncomfortable.

When shifting from the high speed range to the low speed range,
Even when the valve operating switching control valve 13 is opened, the hydraulic pressure Pv does not decrease while the valve operating switching actuator 14 is performing the switching operation, and when the valve operating switching actuator 14 completes the switching operation, the hydraulic pressure Pv is reached. Falls below a predetermined value Pv2.

Therefore, when shifting from the low speed range to the high speed range, the hydraulic pressure Pv introduced to the valve actuation switching actuator 14 after the valve actuation switching control valve 13 is opened is a predetermined value Pv2.
Even if the discharge pressure of the oil pump 5 temporarily rises when the hydraulic pressure supply control valve 10 is opened by closing the hydraulic pressure supply control valve 10 after the hydraulic pressure supply control valve 10 has fallen over the range, it is affected by this. It is possible to prevent the valve operating actuator 14 from being switched at a predetermined operating point without causing a torque step and causing a driver to feel uncomfortable.

In this way, by detecting the oil pressure Pv introduced to the valve operating valve switching actuator 14 and determining whether the switching operation of the valve operating valve switching actuator 14 has been completed, the valve operating operation of the valve operating valve switching actuator 14 is switched. On the other hand, the time for delaying the opening / closing operation of the hydraulic pressure supply control valve 10 can be minimized.

Next, another embodiment shown in FIG. 13 has a structure in which the hydraulic pressure supply control valve 16 for opening and closing the second oil supply passage 12 is opened and closed in response to the pilot pressure. It should be noted that the same reference numerals are used for the portions corresponding to those in FIG.

As shown in FIG. 14, the hydraulic pressure supply control valve 16 includes a spool valve 102 biased in a valve closing direction via a return spring 101, and a hydraulic pressure for driving the spool valve 102 against the return spring 101. A chamber 105 is provided.

A hydraulic pressure chamber 105 of the hydraulic pressure supply control valve 16 and a pilot pressure passage 17 connecting the valve operation switching control valve 13 of the first oil supply passage 11 and the valve operation switching actuator 14 are provided.

The pilot pressure at which the hydraulic pressure supply control valve 16 operates is set higher than the hydraulic pressure at which the valve operating actuator 13 operates.

In the low speed range, the pilot pressure introduced into the hydraulic chamber 105 is maintained below a predetermined value, and as shown in FIG.
The biasing force of the return spring 101 holds the second oil supply passage 12 in a position that closes the second oil supply passage 12.

When shifting from the low speed region to the high speed region, the hydraulic pressure introduced to the valve operating valve switching actuator 14 is changed after the switching operation of the valve operating valve switching actuator 14 is completed after the valve operating valve switching control valve 13 is closed. When the pressure rises above a predetermined value, as shown in FIG. 15, the position is switched to a position for opening the second oil supply passage 12 against the biasing force of the return spring 101.

Therefore, even when the discharge pressure of the oil pump 5 temporarily rises during the opening operation of the hydraulic pressure supply control valve 10 when shifting from the low speed region to the high speed region, the valve operating is not affected by this. The switching operation of the switching actuator 14 is performed at a predetermined operating point, and it is possible to prevent the driver from feeling uncomfortable due to a torque step.

When shifting from the high speed region to the low speed region, the valve operating control valve 13 is opened to operate the valve operating actuator 1.
When the hydraulic pressure guided to 4 falls below a predetermined value, the hydraulic pressure supply control valve 16 is first switched by the biasing force of the return spring 101 to a position that closes the second oil supply passage 12, and then the valve operating actuator 14 The switching operation is performed.

As described above, when the hydraulic pressure supply control valve 16 is closed first and the injection of a large amount of lubricating oil from the oil jet 9 is stopped when shifting from the high speed range to the low speed range, the relief for maintaining the hydraulic pressure is provided. Since the opening operation of the valve 6 is delayed and the discharge pressure of the oil pump 5 is temporarily increased, the operation of the valve operating actuator 14 may be delayed and a torque step may occur, but from this high speed range to the low speed range. Since the torque step generated at the time of transition occurs in the low rotation range where the generated torque is small, it is smaller than the torque step generated at the time of transition from the low speed range to the high speed range, and there is almost no fear of causing a driver discomfort.

[0091]

As described above, the lubricating oil supply apparatus for the internal combustion engine according to the first aspect of the invention is provided with the control means for operating the hydraulic pressure supply control valve in conjunction with the operation of the valve switching control valve. In addition to being simplified, it is possible to make the lubricating oil supply system highly functional and highly efficient. By operating the valve switching control valve before the discharge pressure of the oil pump temporarily increases or decreases due to the operation of the hydraulic pressure supply control valve, for example, without being affected by the injection of lubricating oil from the oil jet,
It is possible to improve the timing accuracy of the switching operation of the valve operating switching actuator, eliminate the torque step of the engine that occurs at the time of switching, and prevent the driver from feeling uncomfortable.

A lubricating oil supply system for an internal combustion engine according to a second aspect of the present invention comprises a control means for activating the hydraulic pressure supply control valve after a delay time has elapsed after operating the valve switching control valve, so that the control system is simple. As a result, it is possible to improve the functionality and performance of the lubricating oil supply system. By operating the valve switching control valve before the discharge pressure of the oil pump temporarily increases or decreases due to the operation of the hydraulic pressure supply control valve, for example, without being affected by the injection of lubricating oil from the oil jet,
It is possible to improve the timing accuracy of the switching operation of the valve operating switching actuator, eliminate the torque step of the engine that occurs at the time of switching, and prevent the driver from feeling uncomfortable.

A lubricating oil supply system for an internal combustion engine according to a third aspect of the present invention comprises control means for operating the hydraulic pressure supply control valve after the discharge pressure of the oil pump fluctuates due to the operation of the valve switching control valve. The system can be simplified and the lubricating oil supply system can be made highly functional and highly efficient. Since the valve switching control valve operates before the discharge pressure of the oil pump temporarily increases or decreases due to the operation of the hydraulic supply control valve, there is a delay in the operation of the hydraulic supply control valve relative to the switching operation of the valve switching actuator. It is possible to improve the timing accuracy of the switching operation of the valve operating actuator while minimizing it, eliminate the torque step of the engine that occurs during switching, and prevent the driver from feeling uncomfortable.

In the lubricating oil supply apparatus for an internal combustion engine according to a fourth aspect of the present invention, the hydraulic pressure supply control valve is configured to perform switching operation using the hydraulic pressure introduced from the valve switching control valve to the valve switching actuator as the pilot hydraulic pressure. Is set higher than the set hydraulic pressure at which the valve switching actuator operates, so when the hydraulic pressure guided to the valve switching actuator increases due to the operation of the valve switching control valve, the valve switching actuator is switched. The hydraulic pressure supply control valve operates in conjunction with the operation, and the valve operating control valve operates before the discharge pressure of the oil pump temporarily increases or decreases due to the operation of the hydraulic pressure supply control valve. Therefore, for example, the switching operation of the valve switching actuator is performed at a predetermined operating point without being affected by the injection of lubricating oil from the oil jet, etc., and a torque step is generated, which may cause a driver discomfort. It can be prevented.

[Brief description of drawings]

FIG. 1 is a diagram of a lubricating oil supply system showing an embodiment of the present invention.

FIG. 2 is a sectional view of a hydraulic pressure supply control valve.

FIG. 3 is a sectional view of a hydraulic pressure supply control valve.

FIG. 4 is a sectional view showing an oil jet and the like.

FIG. 5 is a mechanical configuration diagram of the same.

FIG. 6 is a sectional view taken along line XX of FIG.

FIG. 7 is a switching characteristic diagram of valve lift characteristics.

FIG. 8 is a characteristic diagram showing control contents for switching valve lift characteristics in the same manner.

FIG. 9 is a characteristic diagram showing the relationship between the amount of oil supplied to each part of the engine and the engine speed.

FIG. 10 is a flowchart showing the same control contents.

FIG. 11 is a diagram of a lubricating oil supply system showing another embodiment.

FIG. 12 is a flowchart showing the same control contents.

FIG. 13 is a diagram of a lubricating oil supply system showing still another embodiment.

FIG. 14 is a sectional view of the hydraulic pressure supply control valve.

FIG. 15 is a sectional view of a hydraulic pressure supply control valve.

FIG. 16 is a diagram of a lubricating oil supply system showing a conventional example.

FIG. 17 is a sectional view showing an oil jet and the like.

[Explanation of symbols]

 5 Oil Pump 7 Lubricating Portion of Valve Operating System 8 Crankshaft Bearing 9 Oil Jet 10 Hydraulic Supply Control Valve 11 First Oil Supply Passage 12 Second Oil Supply Passage 13 Valve Switching Control Valve 14 Valve Switching Actuator 15 Hydraulic Sensor 16 Hydraulic supply control valve 40 Valve lift adjustment mechanism 45 Electromagnetic switching valve 51 Control unit 70 Valve timing adjustment mechanism 79 Electromagnetic switching valve

Claims (4)

[Claims] Claim: What is claimed is: 1. A valve switching actuator that switches the opening / closing operation characteristics of intake / exhaust valves in response to hydraulic pressure, and a valve switching control valve that adjusts the hydraulic pressure introduced from an oil pump to the valve switching actuator according to operating conditions. And a hydraulic pressure supply control valve that adjusts the ratio of the distribution of the lubricating oil discharged from the oil pump to the various parts of the engine. A lubricating oil supply device for an internal combustion engine, comprising a control means for operating a supply control valve. 2. A valve switching actuator for switching the opening / closing operation characteristics of intake / exhaust valves in response to hydraulic pressure, and an electromagnetic valve for controlling the hydraulic pressure introduced from an oil pump to the valve switching actuator according to operating conditions. A switching control valve, an electromagnetic hydraulic supply control valve that adjusts the ratio of the lubricating oil discharged from the oil pump to the various parts of the engine, and a valve switching control valve that is operated and operated according to operating conditions. A lubricating oil supply device for an internal combustion engine, comprising: a control unit that operates the hydraulic pressure supply control valve after a delay time has elapsed after operating the switching control valve. 3. A valve switching actuator for switching the opening / closing operation characteristics of intake / exhaust valves in response to oil pressure, and an electromagnetic valve for adjusting the oil pressure introduced from an oil pump to the valve switching actuator according to operating conditions. A switching control valve, an electromagnetic hydraulic pressure supply control valve that adjusts the ratio of distribution of lubricating oil discharged from the oil pump to each part of the engine, a means for detecting the discharge pressure of the oil pump, and a valve that operates according to operating conditions. A control means for activating the valve switching control valve and for activating the hydraulic pressure supply control valve after the discharge pressure of the oil pump fluctuates with the operation of the valve switching control valve, and an internal combustion engine characterized by the following: Lubricating oil supply device. 4. A valve switching actuator that switches the opening / closing operation characteristics of intake / exhaust valves in response to hydraulic pressure, and a valve switching control valve that adjusts the hydraulic pressure introduced from an oil pump to the valve switching actuator in accordance with operating conditions. And a hydraulic pressure supply control valve for adjusting the ratio of distributing the lubricating oil discharged from the oil pump to the various parts of the engine, the hydraulic pressure supply control valve is operated from the valve switching control valve. Lubrication of an internal combustion engine characterized in that the hydraulic pressure introduced to the valve switching actuator is switched to operate as a pilot hydraulic pressure, and the set hydraulic pressure at which the hydraulic pressure supply control valve operates is set higher than the set hydraulic pressure at which the valve switching actuator operates. Oil supply device.