JP2017115704A - Oil flow control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an oil flow control device capable of preventing increase of oil pressure on an upstream side of the oil flow control device to cool a piston as necessary.SOLUTION: An oil flow control device 31 has a movable valve 40 configured to be turned to one of a first position of introducing oil to an oil jet 21 and a second position of discharging oil toward a downstream side. The movable valve 40 is configured to be turned to at least one of the first position and the second position according to suction pressure of an engine 1 acting on the movable valve 40 and elastic force of a coil spring 41 acting on the movable valve 40.SELECTED DRAWING: Figure 2

Description

  The present invention relates to an oil flow rate adjusting device mounted on an internal combustion engine.

  As an oil flow rate adjusting device in which the oil pressure increases in proportion to the rotational speed of the internal combustion engine, when the oil pressure becomes greater than a predetermined value, the oil is injected toward the piston of the internal combustion engine, It is known that it cools.

  However, in this oil flow rate adjusting device, oil is injected into the piston even in an operation region where the piston does not need to be cooled, such as in a low load region of the internal combustion engine, and the piston is excessively cooled. is there.

  As an oil flow rate adjusting device that can prevent oil from being injected into a piston in a low load range of an internal combustion engine, for example, a device described in Patent Document 1 is known. This oil flow rate adjusting device closes the oil inlet and the oil outlet by a movable valve that is operated by the intake negative pressure when the internal combustion engine has a large intake negative pressure, and does not inject oil toward the piston.

  On the other hand, when the internal combustion engine has a small intake negative pressure, the movable valve is operated by the biasing force of the coil spring, and the oil inlet and the oil outlet are connected to inject oil toward the piston.

JP 2014-173562 A

  In the conventional oil flow rate adjusting device, the oil inlet and the oil outlet are closed by a movable valve that is operated by the intake negative pressure when the internal combustion engine has a high intake negative pressure and the load is low.

  As a result, the oil becomes high pressure on the upstream side of the oil flow control device. For this reason, for example, the load of the oil pump that supplies oil to the oil flow rate adjustment device on the upstream side of the oil flow rate adjustment device may increase, and the friction of the internal combustion engine that drives the oil pump may increase. There is still room for improvement.

  The present invention has been made paying attention to the above problems, and can prevent the oil pressure on the upstream side of the oil flow rate adjusting device from increasing and cool the piston when necessary. It is an object of the present invention to provide an oil flow rate adjusting device that can be used.

  The present invention is an oil flow rate adjusting device that is provided upstream of an oil jet that injects oil toward a piston of an internal combustion engine, and that adjusts the flow rate of oil supplied to the oil jet. A movable valve that is switched to at least one of a first position for introduction and a second position for discharging oil toward the downstream side, wherein the movable valve is an intake pressure of the internal combustion engine that acts on the movable valve; And at least one of the first position and the second position according to the elastic force of the elastic member acting on the movable valve.

  As described above, according to the present invention, it is possible to prevent the oil pressure on the upstream side of the oil flow rate adjusting device from increasing and cool the piston when necessary.

FIG. 1 is a cross-sectional view of an internal combustion engine provided with an oil flow rate adjusting device according to a first embodiment of the present invention. FIG. 2 is a diagram illustrating the oil flow rate adjusting device according to the first embodiment of the present invention, and is a diagram illustrating an operation state of the oil flow rate adjusting device when the engine is in a high load region. FIG. 3 is a view showing the oil flow rate adjusting device according to the first embodiment of the present invention, and is a view showing an operating state of the oil flow rate adjusting device when the engine is in a low load region. FIG. 4 is a diagram illustrating the oil flow rate adjusting device according to the first embodiment of the present invention, and is a diagram illustrating an operation state of the oil flow rate adjusting device when the engine is in a medium load region. FIG. 5 is a diagram showing a relationship among a load, an intake pressure, and an engine load related to the movable valve of the oil flow control device according to the first embodiment of the present invention. FIG. 6 is a cross-sectional view of an internal combustion engine provided with a supercharger in addition to the oil flow rate adjusting device according to the first embodiment of the present invention. FIG. 7 is a diagram showing an oil flow rate adjusting device according to the second embodiment of the present invention, and is a diagram showing an operating state of the oil flow rate adjusting device when the engine is in a high load region. FIG. 8 is a diagram showing an oil flow rate adjusting device according to the second embodiment of the present invention, and is a diagram showing an operating state of the oil flow rate adjusting device when the engine is in a low load region. FIG. 9 is a view showing an oil discharge pipe having another shape in the oil flow rate adjusting device according to the first and second embodiments of the present invention.

Hereinafter, an oil flow rate adjusting device according to an embodiment of the present invention will be described with reference to the drawings.
(First embodiment)
1 to 6 are views showing an oil flow rate adjusting device according to a first embodiment of the present invention.

  First, the configuration will be described. In FIG. 1, an engine 1 as an internal combustion engine attached to a vehicle such as an automobile includes a cylinder block 2, a cylinder head 3 attached to an upper part of the cylinder block 2, and a cylinder head cover 4 attached to an upper part of the cylinder head 3. And an oil pan 5 which is attached to the lower part of the cylinder block 2 and stores oil.

  A cylinder 6 is formed in the cylinder block 2, and a piston 6 </ b> A is provided on the cylinder 6 so as to be movable up and down. The piston 6 </ b> A is connected to the crankshaft 19 via the connecting rod 18, and the lifting / lowering motion of the piston 6 </ b> A is converted to the rotational motion of the crankshaft 19 via the connecting rod 18.

  A crankcase 2A is formed below the cylinder block 2, and a crankshaft 19 is rotatably accommodated in the crankcase 2A. A crank chamber 10 is formed inside the crankcase 2 </ b> A, and the crank chamber 10 is installed above the oil pan 5.

  In the engine 1, a combustion chamber 7 is formed by the inner wall of the cylinder 6, the bottom surface of the cylinder head 3, and the top surface of the piston 6A. An intake port 8 and an exhaust port 9 are formed in the cylinder head 3, and the combustion chamber 7 communicates with the intake port 8 and the exhaust port 9, respectively. The number of combustion chambers 7 is provided according to the number of cylinders, and the intake port 8 and the exhaust port 9 are provided for each cylinder.

  An intake manifold 11 is attached to the cylinder head 3. The intake manifold 11 is provided with a throttle body 12 in which a throttle valve 12A is accommodated, a surge tank 13 provided on the downstream side of the throttle body 12, a branch from the surge tank 13, and provided on the downstream side of the surge tank 13. A plurality of branch pipes 14 connected to the intake port 8 are provided, and an intake passage 17 communicating with the intake port 8 is formed inside the intake manifold 11.

  An intake duct (not shown) is provided on the upstream side of the intake manifold 11 via an air cleaner (not shown), and the air drawn from the intake duct is purified by the air cleaner and then introduced from the intake manifold 11 to each intake port 8. Is done.

  An exhaust manifold (not shown) is attached to the cylinder head 3, and the exhaust gas exhausted from the exhaust port 9 is collected in the exhaust manifold. The exhaust gas collected in the exhaust manifold is purified by a catalytic converter (not shown) provided on the downstream side of the exhaust manifold and then discharged to the outside. Here, upstream and downstream refer to upstream and downstream with respect to the flow direction of fluid such as intake air and exhaust gas.

  The cylinder head 3 is provided with an intake valve 15, and the intake valve 15 opens and closes the intake port 8. The cylinder head 3 is provided with an exhaust valve 16, and the exhaust valve 16 opens and closes the exhaust port 9.

  The engine 1 is provided with an oil jet 21. The oil jet 21 is disposed in the crank chamber 10 near the piston 6A of the engine 1 and injects oil toward the lower surface of the piston 6A.

  An oil strainer 26 for purifying oil stored in the oil pan 5 is provided inside the oil pan 5. The oil strainer 26 and the oil jet 21 are connected by an oil pipe 23. An oil pump 27 is installed in the middle of the oil pipe 23, and the oil pump 27 pumps oil stored in the oil pan 5 to the oil jet 21.

The oil pipe 23 is connected to a main gallery (not shown), and the main gallery supplies oil to other hydraulic equipment (not shown) such as a VVT and a lash adjuster, and a lubricating part of the engine 1 such as a crank journal.
An oil flow rate adjusting device 31 is installed in the oil pipe 23 between the oil jet 21 and the oil pump 27 on the upstream side of the oil jet 21.

  In FIG. 2, the oil flow rate adjusting device 31 includes an outer cylinder member 32, and the outer cylinder member 32 is attached to the cylinder block 2. The outer cylinder member 32 may be formed integrally with the cylinder block 2.

  An inlet portion 33 and an outlet portion 34 are formed in the outer cylinder member 32, and the inlet portion 33 and the outlet portion 34 communicate with each other through an internal passage 35 formed in the outer cylinder member 32. The inlet 33 communicates with the oil pipe 23 and introduces oil supplied from the oil pipe 23 into the internal passage 35.

  A supply passage 36 and a discharge passage 37 are formed in the outlet portion 34. One end of an oil supply pipe 38 is connected to the outlet 34, and the other end of the oil supply pipe 38 is connected to the oil jet 21.

  The inside of the oil supply pipe 38 communicates with the supply passage 36, and the oil introduced into the internal passage 35 from the inlet 33 is introduced into the oil jet 21 from the supply passage 36 through the oil supply pipe 38.

  One end of an oil discharge pipe 39 is connected to the outlet 34, and the other end of the oil discharge pipe 39 is connected to the crankcase 2A. The inside of the oil discharge pipe 39 communicates with the discharge passage 37, and the oil introduced into the internal passage 35 from the inlet 33 is discharged from the discharge passage 37 to the crank chamber 10 through the oil discharge pipe 39.

  A movable valve 40 is slidably provided in the internal passage 35, and a communication hole 40 </ b> A is formed at the center in the vertical direction of the movable valve 40. The movable valve 40 is switched to at least one of a first position where the inlet 33 and the supply passage 36 are communicated with each other and a second position where the inlet 33 and the discharge passage 37 are communicated with each other through the communication hole 40A.

A coil spring 41 is provided between the outer cylinder member 32 and the movable valve 40 in the upper part of the internal passage 35. The coil spring 41 generates an elastic force that presses the movable valve 40 downward and switches the movable valve 40 to the first position.
A pressure chamber 42 is formed in the upper part of the internal passage 35 between the outer cylinder member 32 and the movable valve 40, and the coil spring 41 is installed in the pressure chamber 42.

  In FIG. 1, one end of an intake pipe 51 is connected to the outer cylinder member 32. The other end of the intake pipe 51 is attached to the surge tank 13. The pressure chamber 42 communicates with the intake passage 17 through an intake passage 51 </ b> A formed inside the intake pipe 51, and an intake negative pressure acts on the pressure chamber 42.

  The oil flow rate adjusting device 31 of the present embodiment moves the movable valve 40 to at least one of the first position and the second position according to the intake pressure acting on the movable valve 40 through the pressure chamber 42 and the elastic force of the coil spring 41. The flow rate of oil flowing through the supply passage 36 is adjusted. The coil spring 41 of the present embodiment constitutes an elastic member of the present invention, and the intake manifold 11 and the intake pipe 51 constitute an intake system of the present invention.

Next, the operation will be described.
(When the operating range of the engine 1 is in the low load range)
The movable valve 40 is pressed downward by a coil spring 41, and the bottom surface of the movable valve 40 is in contact with the lower bottom surface of the outer cylinder member 32. In this state, as shown in FIG. 2, the inlet 33 and the supply passage 36 are communicated with each other through the communication hole 40A.

  When the engine 1 is in the low load region, the opening degree of the throttle valve 12A is small, and the negative pressure acting on the movable valve 40 from the intake pipe 51 through the pressure chamber 42 becomes large. When the negative pressure acting on the movable valve 40 increases, the movable valve 40 moves upward against the pressing force of the coil spring 41 as shown in FIG.

  Thereby, the movable valve 40 blocks communication between the inlet portion 33 and the supply passage 36, and the communication hole 40 </ b> A of the movable valve 40 connects the inlet portion 33 and the discharge passage 37. For this reason, the oil introduced into the internal passage 35 from the oil pipe 23 through the inlet 33 is discharged from the discharge passage 37 to the crank chamber 10 through the oil discharge pipe 39 (oil is indicated by an arrow O1) and supplied to the oil jet 21. Not.

(When the operating range of the engine 1 is in the high load range)
When the engine 1 is in the high load region, the opening degree of the throttle valve 12A is large, and the negative pressure acting on the movable valve 40 from the intake pipe 51 through the pressure chamber 42 is small. When the negative pressure acting on the movable valve 40 decreases, the movable valve 40 is pressed by the coil spring 41 and moves downward as shown in FIG.

  Thereby, the communication hole 40 </ b> A of the movable valve 40 communicates the inlet portion 33 and the supply passage 36, and the movable valve 40 blocks communication between the inlet portion 33 and the discharge passage 37. For this reason, the oil introduced into the internal passage 35 from the oil pipe 23 through the inlet 33 is supplied from the supply passage 36 to the oil jet 21 through the oil supply pipe 38 (oil is indicated by an arrow O2).

  As a result, as shown by oil O3 in FIG. 1, oil is injected from the oil jet 21 toward the piston 6A, the piston 6A is cooled, and the inner wall of the cylinder 6 and the outer peripheral surface of the piston 6A are lubricated.

(When the operating range of the engine 1 is in the middle load range)
When the operation region of the engine 1 is in a medium load region between the low load region and the high load region, the negative pressure acting on the movable valve 40 from the intake pipe 51 through the pressure chamber 42 is larger than that in the high load region. And smaller than the low load range.

  When such negative pressure acts on the movable valve 40 through the pressure chamber 42, the movable valve 40 is pressed downward by the coil spring 41, and the communication hole 40A communicates the inlet 33 with both the supply passage 36 and the discharge passage 37. The movable valve 40 is switched so as to be in the first position and the second position. Here, the position including the first position and the second position is a position where the movable valve 40 communicates the inlet 33 with both the supply passage 36 and the discharge passage 37.

  For this reason, a part of the oil introduced into the internal passage 35 from the oil pipe 23 through the inlet 33 is supplied from the supply passage 36 to the oil jet 21 through the oil supply pipe 38 (oil is indicated by an arrow O4). Further, the remaining oil introduced into the internal passage 35 is discharged from the discharge passage 37 to the crank chamber 10 through the oil discharge pipe 39 (oil is indicated by an arrow O5).

FIG. 5 is a diagram showing the relationship between the load, the intake pressure, and the engine load related to the movable valve 40. As shown in FIG.
As shown in FIG. 5, when the load on the engine 1 is smaller than the load due to the elastic force (pressing force) of the coil spring 41 among the loads on the movable valve 40 and the intake negative pressure is “large”, The coil spring 41 is contracted by the intake negative pressure, and the movable valve 40 is operated. In this case, oil is supplied from the outlet portion 34 to the crank chamber 10.

  On the contrary, when the load on the movable valve 40 is larger than the load due to the elastic force of the coil spring 41 and the intake negative pressure is “small”, the tensile force due to the intake negative pressure is reduced. Then, the movable valve 40 returns to the original position by the elastic force of the coil spring 41. In this case, oil is supplied from the outlet portion 34 to the oil jet 21.

  When the load of the engine 1 is medium with respect to the elastic force of the coil spring 41 and the intake negative pressure is “medium”, the coil spring 41 is smaller than when the intake negative pressure is “small”. The movable valve 40 contracts and operates in the center in the vertical direction of the internal passage 35. In this case, oil is supplied from the outlet portion 34 to the crank chamber 10 and the oil jet 21, respectively.

  As described above, the oil flow rate adjusting device 31 of the present embodiment is a movable valve that is switched to at least one of the first position for introducing oil into the oil jet 21 and the second position for discharging oil toward the downstream side. The movable valve 40 has at least one of the first position and the second position according to the intake pressure of the engine 1 acting on the movable valve 40 and the elastic force of the coil spring 41 acting on the movable valve 40. Is switched to.

  Thereby, oil can be supplied to the piston 6A only when the operation region of the engine 1 is in the high load region, and the piston 6A can be cooled when the piston 6A needs to be cooled.

  Further, the oil flow rate adjusting device 31 does not supply oil to the oil jet 21 when the operation region of the engine 1 is in the low load region, and therefore can prevent the piston 6A from being excessively cooled. In addition, since the oil is not applied to the piston 6A, it is possible to prevent the friction of the engine 1 from being increased by the oil.

  Further, since the oil flow rate adjusting device 31 discharges oil to the crank chamber 10 when the engine 1 is in a low load region, the oil flow rate adjusting device 31 has a high pressure on the upstream side of the oil flow rate adjusting device 31. Can be prevented.

  For this reason, it is possible to prevent an increase in the load of the oil pump 27 that supplies oil to the oil flow rate adjusting device 31 on the upstream side of the oil flow rate adjusting device 31, and the friction of the engine 1 that drives the oil pump 27 increases. Can be prevented.

  Further, according to the oil flow rate adjusting device 31 of the present embodiment, the coil spring 41 has the movable valve 40 when the intake pressure acting on the movable valve 40 is the intake pressure corresponding to the high load range of the engine 1. The elastic force may be applied to the movable valve 40 so that is located at the first position.

  In addition, the coil spring 41 is movable so that the movable valve 40 is positioned at the second position when the intake pressure acting on the movable valve 40 is the intake pressure corresponding to the low operating range of the engine 1. An elastic force may be applied to the valve 40.

  In this way, the elastic force of the coil spring 41 is adjusted according to the load area of the engine 1, and the oil supply destination is easily distributed to the oil jet 21 and the crank chamber 10 according to the load area of the engine 1. Can do.

  Further, according to the oil flow rate adjustment device 31 of the present embodiment, the coil spring 41 has the intake pressure acting on the movable valve 40 corresponding to the middle load region between the high load operation and the low load operation of the engine 1. In the case of the intake pressure, an elastic force may be applied to the movable valve 40 so that the movable valve 40 is positioned at the first position and the second position.

  In this way, when the engine 1 is in the medium load region, an optimal amount of oil corresponding to the medium load region can be supplied to the oil jet 21, and the increase in the friction of the engine 1 can be prevented. Meanwhile, the piston 6A can be cooled.

  Furthermore, as the oil flow rate adjusting device 31 of the present embodiment, the discharge passage 37 may communicate with the crank chamber 10. In this way, the oil can be reliably returned to the oil pan 5. In addition, since it is unnecessary to form a passage in the cylinder block 2 for returning the oil to the oil pan 5, it is possible to eliminate the need for extra processing on the cylinder block 2 and increase the manufacturing cost of the cylinder block 2. Can be prevented.

  For example, the discharge passage 37 may be communicated with the main gallery without communicating with the crank chamber 10. In this case, it is possible to prevent the flow rate of oil supplied from the main gallery to other hydraulic equipment such as VVT and lash adjuster from decreasing.

  Further, according to the oil flow rate adjusting device 31 of the present embodiment, the coil spring 41 is installed in the pressure chamber 42 formed between the outer cylinder member 32 and the movable valve 40 in the upper part of the internal passage 35. .

  Thereby, when the oil flow rate adjusting device 31 breaks down for some reason, the movable valve 40 is pressed downward by the coil spring 41 so that the inlet 33 and the supply passage 36 can be communicated with each other.

  For this reason, a path for supplying oil to the oil jet 21 can be secured, the piston 6A can be cooled in a high load region of the engine 1, and seizure of the piston 6A can be prevented.

  Note that the oil flow rate adjusting device 31 of the present embodiment may be installed in the engine 1 provided with the supercharger 52 as shown in FIG. In this case, when the engine 1 is in a high load region, the air supercharged from the supercharger 52 through the surge tank 13 to the branch pipe 14 is introduced, whereby the intake pipe 51 is provided in the pressure chamber 42. High pressure positive pressure acts through.

  For this reason, the movable valve 40 moves downward by the elastic force and positive pressure of the coil spring 41, the communication hole 40 </ b> A of the movable valve 40 communicates the inlet portion 33 and the supply passage 36, and the movable valve 40 is connected to the inlet portion 33. And the communication with the discharge passage 37 are blocked.

  As a result, the oil introduced into the internal passage 35 from the oil pipe 23 through the inlet 33 is supplied from the supply passage 36 to the oil jet 21 through the oil supply pipe 38.

When the engine 1 is in a low load region, the supercharging pressure by the supercharger 52 becomes small, and therefore, the intake negative pressure acts on the pressure chamber 42. Therefore, as shown in FIG. It moves upward against the pressing force of the coil spring 41. As a result, oil is discharged from the discharge passage 37 to the crank chamber 10 through the oil discharge pipe 39.
(Second Embodiment)

  7 and 8 are views showing an oil flow rate adjusting device according to a second embodiment of the present invention. The same components as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted. .

  In FIG. 7, a coil spring 61 is provided between the outer cylinder member 32 and the movable valve 40 at the lower part of the internal passage 35. The coil spring 61 generates an elastic force that pulls the movable valve 40 downward and switches the movable valve 40 to at least one of the first position and the second position. The coil 61 of this Embodiment comprises the elastic member of this invention.

Next, the operation will be described.
(When the operating range of the engine 1 is in the low load range)
The movable valve 40 is pulled downward by a coil spring 41, and the bottom surface of the movable valve 40 is in contact with the bottom surface of the outer cylinder member 32. In this state, as shown in FIG. 7, the inlet 33 and the supply passage 36 are communicated with each other through the communication hole 40A.

  When the engine 1 is in the low load region, the negative pressure acting on the movable valve 40 through the pressure chamber 42 increases, so that the movable valve 40 moves upward against the tensile force of the coil spring 41 as shown in FIG. Move to.

  Thereby, the movable valve 40 blocks communication between the inlet portion 33 and the supply passage 36, and the communication hole 40 </ b> A of the movable valve 40 connects the inlet portion 33 and the discharge passage 37. For this reason, the oil introduced into the internal passage 35 from the oil pipe 23 through the inlet 33 is discharged from the discharge passage 37 to the crank chamber 10 through the oil discharge pipe 39 (oil is indicated by an arrow O6) and supplied to the oil jet 21. Not.

(When the operating range of the engine 1 is in the high load range)
When the engine 1 is in a high load region, the negative pressure acting on the movable valve 40 is reduced through the pressure chamber 42, so that the movable valve 40 is pulled downward by the coil spring 41 and moves downward as shown in FIG. To do.

  Thereby, the communication hole 40 </ b> A of the movable valve 40 communicates the inlet portion 33 and the supply passage 36, and the movable valve 40 blocks communication between the inlet portion 33 and the discharge passage 37. Therefore, the oil introduced from the oil pipe 23 into the internal passage 35 through the inlet 33 is supplied from the supply passage 36 to the oil jet 21 through the oil supply pipe 38 (oil is indicated by an arrow O7).

  Further, when the operating region of the engine 1 is in the middle load region between the low load region and the high load region, the negative pressure acting on the movable valve 40 through the pressure chamber 42 through the intake pipe 51 is higher than that in the high load region. And smaller than the low load range.

  When such negative pressure acts on the movable valve 40 through the pressure chamber 42, the movable valve 40 is pulled downward by the coil spring 41, and the communication hole 40 </ b> A communicates both the inlet portion 33 and the supply passage 36 and the discharge passage 37. The position of the movable valve 40 is switched to the position where it moves. Therefore, the oil introduced into the internal passage 35 from the oil pipe 23 through the inlet 33 is supplied to the oil jet 21 and discharged to the crank chamber 10 as in FIG.

  When the oil flow rate adjusting device 31 according to the present embodiment is installed in the engine 1 having the supercharger 52 shown in FIG. 6, the same operation as that in FIG. 8 is performed when the engine 1 is in the low load region. When the engine 1 is in the high load range, the same operation as that in FIG. 7 is performed.

  Here, in each of the above embodiments, the oil discharge pipe 39 has the same diameter. However, as shown in FIG. 9, the oil discharge pipe 39 may be provided with an orifice 39A. In this way, the flow rate of the oil flowing through the oil discharge pipe 39 can be reduced by the orifice 39A.

  Thereby, when the engine 1 is in a low load region, it is possible to prevent excessive oil from being discharged from the oil pipe 23 through the oil discharge pipe 39 to the crank chamber 10. For this reason, it can prevent that the oil flow volume supplied to other hydraulic equipments, such as VVT and a lash adjuster, and the lubrication site | part of the engine 1 reduces.

  The orifice 39A of the present embodiment constitutes an oil flow rate adjusting unit of the present invention. Note that the flow rate adjusting member may be a check valve, and is not limited to the check valve.

  While embodiments of the invention have been disclosed, it will be apparent to those skilled in the art that changes may be made without departing from the scope of the invention. All such modifications and equivalents are intended to be included in the following claims.

  DESCRIPTION OF SYMBOLS 1 ... Engine (internal combustion engine), 5 ... Oil pan, 6A ... Piston, 10 ... Crank chamber, 11 ... Intake manifold (intake system), 21 ... Oil jet, 31. ..Oil flow rate adjusting device, 32 ... outer cylinder member, 39A ... orifice (oil flow rate adjusting part), 40 ... movable valve, 41, 61 ... coil spring (elastic member), 51 .. Intake piping (intake system)

Claims (5)

An oil flow rate adjusting device provided on the upstream side of an oil jet for injecting oil toward a piston of an internal combustion engine, and adjusting an oil flow rate supplied to the oil jet,
A movable valve that is switched to at least one of a first position for introducing oil into the oil jet and a second position for discharging oil toward the downstream side;
The movable valve is switched to at least one of the first position and the second position according to an intake pressure of an intake system acting on the movable valve and an elastic force of an elastic member acting on the movable valve. An oil flow control device characterized by. When the intake pressure acting on the movable valve is an intake pressure corresponding to a high load range of the internal combustion engine, the elastic member is disposed on the movable valve so that the movable valve is positioned at the first position. Give elasticity,
When the intake pressure acting on the movable valve is an intake pressure corresponding to a low load range of the internal combustion engine, an elastic force is applied to the movable valve so that the movable valve is positioned at the second position. The oil flow rate adjusting device according to claim 1, wherein:   When the intake pressure acting on the movable valve is an intake pressure corresponding to a medium load range between a high load range and a low load range of the internal combustion engine, the elastic member moves the movable valve to the first position. 3. The oil flow rate adjusting device according to claim 2, wherein an elastic force is applied to the movable valve so as to be located at a position of 1 and the second position. The internal combustion engine has an oil pan for storing oil, and a crank chamber installed above the oil pan,
The oil flow rate adjusting device according to any one of claims 1 to 3, wherein the discharge passage communicates with the crank chamber.   2. An oil supply pipe that connects the oil jet and the oil flow rate adjusting device is provided, and the oil supply pipe has a flow rate adjusting unit that adjusts an oil flow rate flowing through the oil supply pipe. The oil flow control device according to any one of claims 4 to 4.