JP6123994B2 - Oil supply device - Google Patents

Description

  The present invention relates to an oil supply apparatus, and more particularly to an oil supply apparatus that cools a piston by injecting oil onto the piston.

As a cooling device for cooling a piston of an engine, a device provided with an oil jet (also referred to as “piston cooling jet” or “PCJ”) is known.
At this time, the oil jet pumps oil accumulated in the oil pan by an oil pump, injects lubricating oil to pistons provided in each cylinder inside the engine, and cools the pistons.

JP 2004-293509 A

By the way, in the conventional oil supply apparatus, it is not preferable to inject oil from the oil jet toward the piston when the engine is in a low load region.
This is because the piston is unnecessarily cooled by the oil, causing an increase in cooling loss and unsatisfactory total combustion, resulting in a deterioration in fuel consumption.
In addition, in the conventional oil supply device, the piston is cooled by oil injection not only in the high load region where piston cooling is required but also in the low load region where piston cooling is not required, so that the fuel consumption deteriorates. There was a fear.
Further, when the oil supply device is electronically controlled, on / off control of oil injection can be performed, but there is a disadvantage that the device has a complicated structure and is expensive.
For this reason, an oil supply device that can switch on and off oil injection in a low load region and a high load region with a simple and inexpensive configuration without improving complicated fuel consumption and adding complicated controls and devices. Realization was anxious.

  It is an object of the present invention to supply piston cooling oil to an oil jet and perform piston cooling when piston cooling is required in accordance with engine load.

Therefore, in order to eliminate the above-mentioned inconvenience, the present invention includes an oil jet that injects oil toward the piston of the engine, and an oil supply device that includes an oil flow rate adjusting device in an oil passage upstream of the oil jet. The oil flow rate adjusting device includes an outer cylinder portion having an oil inlet and an oil outlet, and is slidably disposed in the outer cylinder portion, and the oil inlet and the oil outlet can communicate with each other. A movable valve having an internal passage, a pressure chamber formed between the inside of the outer cylinder portion and the movable valve, and communicated with the intake system of the engine, and in the same direction as the sliding direction of the movable valve An elastic member that urges the movable valve, and the movable valve is disposed in a direction in which the sliding direction is orthogonal to the oil inlet and the oil outlet, When an air pressure is applied, the movable valve is in a position where it does not slide according to the biasing force of the elastic member, and the oil inlet and the oil outlet communicate with each other via the internal passage, or the pressure When the engine intake pressure is applied to the chamber, the movable valve is slid against the urging force of the elastic member, and the oil inlet and the oil outlet are not communicated by the side wall of the movable valve. The flow rate of oil flowing through the oil passage is adjusted by operating in any of the closed states.

According to the present invention, the oil flow rate adjusting device is opened and closed according to the intake pressure, and the oil flow rate according to the engine load is supplied to the oil jet.
Piston cooling is not performed at low loads, and fuel consumption deterioration is prevented by preventing cooling loss and incomplete combustion.
Piston cooling is performed at high loads to prevent abnormal combustion and improve component durability.

FIG. 1 shows an operation example of an oil flow rate adjusting device, (a) is a schematic enlarged cross-sectional view of the oil flow rate adjusting device in a state where a negative pressure is applied to move the movable valve to a closed position and the oil passage is closed, (b) FIG. 3 is a schematic enlarged cross-sectional view of an oil flow rate adjusting device in a state in which a movable valve is set to an open position without applying negative pressure and an oil passage is opened. Example 1 FIG. 2 is a schematic configuration diagram of the engine. Example 1 FIG. 3 is a diagram showing the relationship between the engine load and the load on the movable valve. Example 1 FIG. 4 is a schematic configuration diagram of an engine with a supercharger. (Example 2) FIG. 5 shows an operation example of the oil flow rate adjusting device, (a) is a schematic enlarged cross-sectional view of the oil flow rate adjusting device in a state where the movable valve is set to the closed position without applying positive pressure and the oil passage is closed, (b) ) Is a schematic enlarged cross-sectional view of the oil flow rate adjusting device in a state where a positive pressure is applied to move the movable valve to the open position and the oil passage is opened. (Example 2) FIG. 6 is a diagram showing the relationship between the engine load and the load on the movable valve. (Example 2)

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

1 to 3 show a first embodiment of the present invention.
In FIG. 2, 1 is an engine.
The engine 1 includes a cylinder block 2, a cylinder head 3 attached to the upper surface of the cylinder block 2, a cylinder head cover 4 attached to the upper surface of the cylinder head 3, and an oil pan 5 attached to the lower surface of the cylinder block 2. It consists of.
In the engine 1, a combustion chamber 7 is formed by the cylinder block 2, the cylinder head 3, and the upper surface of the piston 6.
At this time, the downstream end of the intake passage 8 is connected to the combustion chamber 7, and the upstream end of the exhaust passage 9 is connected to the combustion chamber 7.
In the intake system of the engine 1, a throttle body 11 including a throttle valve 10 and an intake manifold 14 including a surge tank 12 and a branch pipe 13 are disposed from the upstream side.
In the intake system of the engine 1, the intake passage 8 is formed by the passage in the throttle body 11, the passage in the intake manifold 14, and the intake port 15 of the cylinder head 3.
In the exhaust system of the engine 1, the exhaust passage 9 is formed by an exhaust port 16 of the cylinder head 3 and a passage in an exhaust manifold (not shown) or an exhaust pipe (not shown).
Further, an intake valve 17 for opening and closing the downstream end of the intake passage 8 is provided, and an exhaust valve 18 for opening and closing the upstream end of the exhaust passage 9 is provided.
The piston 6 is connected to a crankshaft 20 via a connecting rod 19 as shown in FIG.
The engine 1 is provided with an oil supply device 21.
The oil supply device 21 includes an oil jet 22 that injects oil toward the lower surface of the piston 6 of the engine 1, and an oil flow rate adjustment device 24 disposed in an oil passage 23 on the upstream side of the oil jet 22. ing.
That is, the oil jet 22 is disposed in the crank chamber 25 in the vicinity of the piston 6 of the engine 1 and is directed to the lower surface of the piston 6.
The oil passage 23 is provided to connect the oil jet 22 and the oil strainer 26 in the oil pan 5, and an oil pump 27 that pumps oil to the oil jet 22 side is provided in the oil passage 23. doing.
At this time, the oil flow rate adjusting device 24 is arranged on the upstream side of the oil jet 22, that is, in the oil passage 23 between the oil jet 22 and the oil pump 27.

The oil flow rate adjusting device 24 includes an outer cylinder part 30 having an oil inlet 28 and an oil outlet 29, and is slidably disposed in the outer cylinder part 30. The oil inlet 28 and the oil outlet 29 are connected to each other. A movable valve 31 that moves and switches to either an open position for communication or a closed position for non-communication between the oil inlet 28 and the oil outlet 29, and the movable valve 31 is either an open position or a closed position. And a pressure chamber 33 that is disposed between the outer cylinder portion 30 and the movable valve 31 and communicates with the intake system of the engine 1. According to the change, the movable valve 31 is operated to either the open position or the closed position to adjust the oil flow rate flowing through the oil passage 23.
More specifically, as shown in FIGS. 1A and 1B, the oil flow rate adjusting device 24 includes the outer cylinder portion 30 formed of a cylindrical member.
The outer cylinder portion 30 is provided with the oil inlet 28 and the oil outlet 29.
The movable valve 31 is slidably disposed on the outer cylinder portion 30.
At this time, the movable valve 31 includes an internal passage 34 that connects the oil inlet 28 and the oil outlet 29 in a sliding state.
Further, in the oil flow rate adjusting device 24, the pressure chamber 33 is formed on one side in the sliding direction of the movable valve 31 in the outer cylinder portion 30 (upper side in FIG. 1), and the intake pressure pipe 35 is interposed. The pressure chamber 33 communicates with the intake system of the engine 1, that is, the surge tank 12 of the intake manifold 14.
Thereby, the oil flow rate adjusting device 24 is opened and closed according to the intake pressure, and the oil flow rate according to the engine load is supplied to the oil jet 22.
When the load is low, piston cooling is not performed, and deterioration of fuel consumption can be prevented by preventing cooling loss and incomplete combustion.
When the load is high, the piston is cooled to prevent abnormal combustion and improve the durability of the parts.

The oil flow adjusting device 24 is applied with a negative pressure as an intake pressure related to the pressure chamber 33. When the negative pressure is larger than a predetermined pressure, the movable valve is overcome by the negative pressure by overcoming the urging force of the elastic member 32. 31 operates and closes the oil passage 23. On the other hand, when the negative pressure is smaller than a predetermined pressure, the movable member 31 is actuated by the elastic member 32 to open the oil passage 23. Yes.
That is, in the oil flow rate adjusting device 24, a recess 36 is formed on the other side in the sliding direction of the movable valve 31 in the outer cylinder portion 30 (lower side in FIG. 1), and the recess 36 is formed by a compression coil spring. The elastic member 32 is disposed.
For this reason, when the intake pipe negative pressure of the intake manifold 14 is applied as the intake pressure related to the pressure chamber 33 of the movable valve 31, and the intake pipe negative pressure is larger than a predetermined pressure, (a) of FIG. As shown, the intake pipe negative pressure overcomes the urging force of the elastic member 32, and the movable valve 31 is actuated by the intake pipe negative pressure to close the oil passage 23.
When the intake pipe negative pressure is not applied as the intake pressure related to the pressure chamber 33 of the movable valve 31, the elastic member 32 maintains the spring original shape as shown in FIG. The oil passage 23 is opened so as to allow the internal passage 34 to communicate with the oil inlet 28 and the oil outlet 29, so-called “normally open” state.
As shown in FIG. 3, the open / close state of the movable valve 31 varies depending on the intake pipe negative pressure applied as the intake pressure of the pressure chamber 33 of the movable valve 31 and the urging force of the elastic member 32. doing.
That is, among the loads related to the movable valve 31, the engine load is smaller than the load due to the urging force of the elastic member 32 and the tensile load when the intake pipe negative pressure is “large” becomes “large”. The elastic member 32 pulled by the intake pipe negative pressure extends to operate the movable valve 31, and the oil flow rate adjusting device 24 is closed.
On the other hand, among the loads related to the movable valve 31, the engine load is larger than the load due to the urging force of the elastic member 32, and the tensile load when the intake pipe negative pressure is “small” is “small”. In this case, the pulling force due to the negative pressure of the intake pipe is reduced and the movable valve 31 is returned to the original position by the biasing force of the elastic member 32, and the oil flow rate adjusting device 24 is opened. .
Thereby, the oil flow rate adjusting device 24 can be opened and closed according to the intake pressure.
When the natural intake type engine 1 is under a low load such as idling, the oil flow rate adjusting device 24 can be closed using a high, that is, a large intake pipe negative pressure, and unnecessary piston cooling can be avoided. it can.
In addition, since it is necessary to cool the piston when the load is high, in such a case, it is close to the throttle fully open and the intake pipe negative pressure is small or does not occur. The piston can be cooled by the oil jet 22.

In other words, the oil injection is switched on and off by opening or closing the oil passage 23 by the operation of the movable valve 31 of the oil flow rate adjusting device 24.
The movable valve 31 is opened and closed by the intake pipe negative pressure applied as the intake pressure of the pressure chamber 33 of the movable valve 31 and the biasing force of the elastic member 32.
That is, the oil injection between the low load region and the high load region is switched using the fact that the intake negative pressure is different between the low load region and the high load region, and the urging force of the elastic member 32 and the intake air related to the pressure chamber 33 The movable valve 31 is operated by the intake pipe negative pressure applied as a pressure, the oil inlet 28 and the oil outlet 29 are communicated or blocked by the internal passage 34, and the oil injection is switched on / off. Is what you do.
For this reason, the following effects can be acquired by switching oil injection and a stop in a high load area | region and a low load area | region.
(1) Cooling loss and incomplete combustion caused by unnecessary piston cooling at low load can be prevented, and fuel consumption deterioration can be improved.
(2) Oil injection can be switched on and off with a simple and inexpensive configuration without adding complicated control and mechanism such as electronic control.

4 to 6 show a second embodiment of the present invention.
In the second embodiment, portions that perform the same functions as those of the first embodiment will be described with the same reference numerals.

  The feature of the second embodiment is that the oil supply device 41 applies a positive pressure as the intake pressure.

That is, in the oil supply device 41, the engine 1 of the first embodiment described above is used for the engine configuration.
The difference from the first embodiment is that a supercharger 42 is disposed upstream of the throttle body 11 having the throttle valve 10 as shown in FIG.
At this time, the oil supply device 41 includes an oil jet 22 that injects oil toward the lower surface of the piston 6 of the engine 1, and an oil flow rate adjustment device 43 that is disposed in the oil passage 23 upstream of the oil jet 22. And.

The oil flow rate adjusting device 43 is applied with a positive pressure as an intake pressure related to the pressure chamber 33. When the positive pressure is lower than a predetermined pressure, the oil flow adjusting device 43 is urged by an elastic member 44 and the movable valve 45 is operated, When the passage 23 is closed and the positive pressure is larger than a predetermined pressure, the movable valve 45 is operated with the positive pressure by overcoming the urging force of the elastic member 44 and the oil passage 23 is opened.
That is, the oil flow rate adjusting device 43 slides in the outer cylinder portion 30 and the outer cylinder portion 30 having the oil inlet 28 and the oil outlet 29 as shown in FIGS. 5 (a) and 5 (b). The movable valve 45, which is arranged so as to move and switch between an open position in which the oil inlet 28 and the oil outlet 29 are in communication and a closed position in which the oil inlet 28 and the oil outlet 29 are not in communication. The elastic member 44 that urges the movable valve 45 to an open position or a closed position, and a pressure chamber that is disposed between the outer cylinder portion 30 and the movable valve 45 and communicates with the intake system of the engine 1. 33.
At this time, in the oil flow rate adjusting device 43, a concave portion 36 is formed on the other side in the sliding direction of the movable valve 45 in the outer cylinder portion 30 (lower side in FIG. 5), and a tensile coil spring is formed in the concave portion 36. The elastic member 44 is disposed.
Therefore, when a positive pressure is not applied as the intake pressure related to the pressure chamber 33 of the movable valve 45, the movable valve 45 is closed by the biasing force of the elastic member 44 as shown in FIG. The oil passage 23 is urged in the direction, so that the oil passage 23 is in a closed state, that is, a “normally closed” state.
When a positive pressure is applied as the intake pressure related to the pressure chamber 33 of the movable valve 45, the pressure chamber 33 to which the positive pressure is applied is enlarged as shown in FIG. The elastic member 44 is pressed in the compressing direction, and the oil passage 23 is opened so that the oil passage 28 and the oil outlet 29 communicate with the internal passage 34.
As shown in FIG. 6, the open / close state of the movable valve 45 changes depending on the strength of the positive pressure applied as the intake pressure in the pressure chamber 33 of the movable valve 45 and the biasing force of the elastic member 44. ing.
That is, when the positive pressure applied as the intake pressure related to the pressure chamber 33 of the movable valve 45 is “0” or less, the movable valve 45 is biased in the closing direction by the biasing force of the elastic member 44. The oil flow rate adjusting device 43 is in a closed state.
Conversely, when the positive pressure applied as the intake pressure related to the pressure chamber 33 of the movable valve 45 rises, the elastic member 44 is compressed against the urging force of the elastic member 44, and the movable valve 45 45 is moved in the opening direction to open the oil flow rate adjusting device 24.
Thereby, the oil flow rate adjusting device 43 can be opened and closed according to the intake pressure.
When the engine 1 with the supercharger 42 is operating at “high load = supercharging region”, the piston 1 is cooled, so in such a case, positive pressure is used to ensure The oil flow control device opens and the piston can be cooled with an oil jet.
Since no positive pressure is generated at low load, the oil flow rate adjusting device does not open and unnecessary piston cooling does not have to be performed.

DESCRIPTION OF SYMBOLS 1 Engine 5 Oil pan 6 Piston 7 Combustion chamber 8 Intake passage 11 Throttle body 12 Surge tank 14 Intake manifold 15 Intake port 16 Exhaust port 19 Connecting rod 20 Crankshaft 21 Oil supply device 22 Oil jet 23 Oil passage 24 Oil flow rate adjustment device 25 Crank Chamber 26 Oil strainer 27 Oil pump 28 Oil inlet 29 Oil outlet 30 Outer cylinder portion 31 Movable valve 32 Elastic member 33 Pressure chamber 34 Internal passage 35 Intake pressure piping 36 Concave portion

Claims (3)

  In an oil supply apparatus that includes an oil jet that injects oil toward a piston of an engine and includes an oil flow rate adjusting device in an oil passage upstream of the oil jet, the oil flow rate adjusting device includes an oil inlet and an oil outlet. An outer cylinder part, a movable valve that is slidably disposed in the outer cylinder part, and has an internal passage that allows the oil inlet and the oil outlet to communicate with each other; and the outer cylinder part A pressure chamber formed between the movable valve and the engine, and an elastic member that urges the movable valve in the same direction as the sliding direction of the movable valve. The movable valve is arranged such that its sliding direction is orthogonal to the oil inlet and the oil outlet, and when the intake pressure of the engine is applied to the pressure chamber, When the movable valve is in a non-sliding position, the oil inlet and the oil outlet communicate with each other via the internal passage, or when the engine intake pressure is applied to the pressure chamber, The oil passage is moved to a position where the movable valve slides against the biasing force of the elastic member, and the oil inlet and the oil outlet are not communicated with each other by a side wall of the movable valve. An oil supply device that adjusts the flow rate of oil flowing through the oil. The outer cylinder portion is disposed in the middle of the oil passage, and the oil passage is upstream with respect to the outer cylinder portion and upstream of the oil passage communicating with an oil pump, and the outer cylinder portion A downstream oil passage that communicates with the oil jet and communicates the upstream oil passage with the oil inlet of the outer cylinder portion, while the downstream side The oil supply device according to claim 1, wherein the oil passage is communicated with the oil outlet of the outer cylinder portion . The oil supply apparatus according to claim 2 , wherein the oil inlet and the oil outlet are arranged so as to face each other in a straight line .

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