JPH11257040A - Hydraulic control valve for lubricating circuit of interal combustion chamber - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce pressure loss at an opening of a hydraulic control valve that is attached to a lubrication circuit and serves to maintain sufficient pressure of the lubricant supplied to the hydraulic drive unit in an operation state of an internal combustion chamber at a low lubricant pressure. SOLUTION: A hydraulic control valve 22 attached to the lubrication passage 18 leading to the portion requiring lubrication of the engine is composed of a fan-shaped valve body 25 pivotally rotatable around a valve axis 26 and a spring 34 that urges the valve axis 25 in the closing direction. The differential pressure generated between the front and rear portions of the valve body 25 increases the hydraulic pressure within another lubrication passage for the hydraulic drive unit separated from the lubrication passage 18 at a branch portion (not shown). As a result, the operation response of the hydraulic drive unit can be improved. When the valve body 25 is completely closed, minimum amount of the lubricant is allowed to flow through a bypass passage 25a leading to the portion requiring lubrication. As the valve body 25 is completely retracted into the space defined within the lubricant passage 18 at maximum opening degree, the pressure loss within the lubricant passage 18 becomes substantially zero.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic control device for a lubrication circuit of an internal combustion engine, and more particularly to a hydraulic control device which is driven by utilizing a part of pressurized lubricating oil circulating in the circuit. The present invention relates to a hydraulic control valve suitable for use in a lubrication circuit including a drive device.

[0002]

2. Description of the Related Art A variable valve timing mechanism (VV) for diverting a part of pressurized lubricating oil flowing through a lubrication circuit of an internal combustion engine to change the opening / closing timing of an intake valve or an exhaust valve.
A design for driving a hydraulic drive device such as T) has been conventionally performed. FIG. 11 shows an example of a variable valve timing mechanism as such a hydraulic drive device. This variable valve timing mechanism (VVT) 1 is applied to a six-cylinder engine 2 shown in FIG. In these figures, 3 is an intake valve or an exhaust valve, 4 is a camshaft, 5 is a hydraulic piston of the variable valve timing mechanism 1, 6 is a hydraulic switching valve (oil control valve, both OCV and OCV) for controlling the hydraulic pressure sent to the hydraulic piston 5. )
The spool 7 is moved left and right by a solenoid 8 to control switching of an oil path so as to supply pressurized lubricating oil to one of ports 9 and 10 of a hydraulic switching valve 6 connected to the hydraulic piston 5. It is supposed to. The port 11 of the hydraulic switching valve 6 is connected to a branch 13 in the lubrication circuit by a VVT oil passage 12 to receive a supply of pressurized lubricating oil.

As is apparent from FIG. 12, the lubrication circuit of the engine 2 is provided with an oil pump 15 for sucking lubricating oil from an oil pan 14 and pressurizing the oil pump 15 and adjusting the oil pressure on the discharge side to a substantially constant height. A relief valve type pressure regulating valve 16 for returning an excessive amount of lubricating oil to the oil pan 14, an oil filter 17 for filtering lubricating oil, and lubrication on the main stream side where the VVT oil passage 12 is branched at the branching section 13 described above. Oil passage 18
A main hole 19 to which the lubricating oil passage 18 connects;
Many lubricating oil supply passages such as a main journal oil passage 20 and a valve train oil passage 21 that branch off from the main hole 19;
It is composed of a number of lubricated points (not shown) connected to them and receiving a supply of pressurized lubricating oil, and a return oil path (not shown) for returning lubricating oil discharged from the lubricated points to the oil pan 14. You.

The lubricating oil of the oil pan 14 is oil pump 1
The oil is pressurized by the pressure regulator 5, adjusted to a constant oil pressure by the pressure adjusting valve 16, and supplied to the main hole 19 through the oil filter 17, the branch portion 13, and the main flow side lubricating oil passage 18.
The lubricating oil is supplied to the lubricating portion by a number of lubricating oil supply passages such as a main journal oil passage 20 and a valve train oil passage 21 branched from the main hole 19, and the lubricating oil is supplied to bearings, cams, sliding parts of pistons and cylinders, and the like. Lubricate or cool the lubrication points.

Further, a part of the lubricating oil pressurized in the branch portion 13 is diverted and supplied to the variable valve timing mechanism 1 which is one of the hydraulic drive devices by the VVT oil passage 12, and is operated by the solenoid 8. By opening and closing the ports 9 and 10 by the spool 7 in the hydraulic switching valve 6, pressurized lubricating oil is supplied to one of the working chambers on both sides of the hydraulic piston 5. Thereby, the rotation phase of the camshaft 4 with respect to the crankshaft (not shown) changes, and the opening / closing timing of the intake valve or the exhaust valve 3 changes. Even in the case where some hydraulic drive device other than the variable valve timing mechanism 1 is provided as in this example, the drive is similarly performed by pressurized lubricating oil diverted from a position such as the branch portion 13 of the lubrication circuit. Is supplied.

[0006]

SUMMARY OF THE INVENTION Such an engine 2
In the lubrication circuit of FIG. 1, when the oil temperature of the lubricating oil is high and the viscosity is low and the discharge amount of the oil pump 15 is reduced by operating the engine at a low rotational speed, the oil pump 15 , The oil pressure of the lubricating oil on the discharge side drops significantly. As a result, a situation may occur in which the oil pressure becomes lower than the set oil pressure of the pressure regulating valve 16 and the oil pressure in the branch portion 13 of the lubrication circuit does not reach the predetermined level.
Even in such a state, the lubricating circuit connected to the lubricating oil passage 18 on the mainstream side usually has a low oil pressure and a low viscosity lubricating oil. This is not a problem because the amount of oil necessary for lubrication of the lubricated portion is sufficiently secured. However, such a hydraulic pressure as the variable valve timing mechanism 1 connected to the VVT oil passage 12 branched at the branch portion 13 is used. In the drive device, the control responsiveness is deteriorated because the hydraulic piston 5 cannot be quickly moved to a target position or a relatively high oil pressure required to maintain the control position cannot be obtained. Later, there arises a problem due to insufficient hydraulic pressure such that a sufficiently high control stability cannot be obtained.

The present invention addresses the above-mentioned problems in the prior art and solves the above-mentioned problems. Therefore, even in an operating state in which the temperature of lubricating oil of an internal combustion engine is high and the number of revolutions is low, any hydraulic drive device attached to the lubrication circuit is required. It is possible to automatically adjust the oil pressure of the lubrication circuit to an appropriate level so that the oil pressure of the lubricating oil supplied to It is an object of the present invention to provide a hydraulic control valve in a lubrication circuit of an internal combustion engine that can be provided.

According to the present invention, a hydraulic control valve provided in a lubricating oil passage such as a lubricating circuit of an internal combustion engine or the like provided with the above-mentioned hydraulic drive device is completely opened to be fully opened. It is an object of the present invention to provide a hydraulic control valve having a novel structure that can be opened when the hydraulic control valve completely opens the oil passage and does not cause any flow resistance.

[0009]

According to the present invention, there is provided a hydraulic control device for a lubrication circuit for an internal combustion engine, as described in the claims.

According to the first aspect of the present invention, even when the lubricating oil pressure is low, the valve body of the hydraulic control valve is automatically biased by the urging means for urging the valve body toward the valve closing position. It moves in the valve closing direction, and the first and
Since the differential pressure of the lubricating oil pressure acting on the lubricating oil path is increased, the lubricating oil pressure of the second lubricating oil path is increased by the amount of the differential pressure, and the lubricating oil is preferentially supplied to the hydraulic drive device, The responsiveness of the operation of the hydraulic drive device at low hydraulic pressure can be improved. On the other hand, a bypass passage for the valve element is also provided in order to supply a minimum amount of lubricating oil to a portion where lubrication of the engine is required when the valve element assumes the closed position.

However, the most important feature of the present invention is that
When the hydraulic control valve is in the maximum open state, the valve body is completely retracted from the first lubricating oil passage so that the flow resistance in the first lubricating oil passage becomes substantially zero. The point is that it is composed. Thereby, in the maximum valve opening state, there is an effect that the pressure loss due to the hydraulic control valve becomes substantially zero. In order to completely retract the valve body from the first lubricating oil passage, in the hydraulic control valve according to claim 2, the valve can house the valve body inside the wall surface of the first lubricating oil passage. A chamber is formed.

[0013] In the hydraulic control valve according to the third aspect, the valve body includes a valve shaft perpendicular to the first lubricating oil passage at a position outside the first lubricating oil passage, It can rotate around the valve shaft and take any degree of opening, and when the valve body moves to the maximum valve opening position, it sinks into the valve chamber formed on the wall surface of the lubricating oil passage, It is configured to be able to retreat from the first lubricating oil passage.

The hydraulic drive device that receives the supply of the lubricating oil through the second lubricating oil passage may be of any type. In the hydraulic control valve according to the fourth aspect, the hydraulic drive device is a variable valve timing mechanism. Can be connected to the second lubricating oil passage. As a result, the control responsiveness of the variable valve timing mechanism is maintained at a high level in a low-load, low-speed operation state of the engine, or in an operation state in which the lubricating oil pressure decreases due to a low rotational speed even when the lubricating oil temperature is high. However, the supply of the lubricating oil to the portion of the engine connected to the first lubricating oil passage that requires lubrication is also reliably performed.

In the hydraulic control valve according to the present invention, a back pressure generated in a space formed behind the valve body in the valve chamber in which the valve body moves is provided to allow the back pressure to escape. In addition, the operation of the valve body is prevented from being affected.

In the hydraulic control valve according to the sixth aspect, since the entire hydraulic control valve is previously assembled as an integral temporary assembly outside and then assembled to the internal combustion engine, detailed components of the hydraulic control valve are provided. It is not necessary to attach the hydraulic control valve to the engine, the work of assembling the hydraulic control valve becomes easy, and the working efficiency is improved.

[0016]

DESCRIPTION OF THE PREFERRED EMBODIMENTS As a first embodiment of the present invention,
1 and 2 show the structure of a hydraulic control valve 22 which is a main part of the hydraulic control device. Engine 2 of FIG. 12 showing the prior art
As for the hydraulic control valve 22 of this embodiment, the hydraulic control valve 22 is inserted into the mainstream lubricating oil passage 18 between the branch portion 13 of the lubricating circuit and the main hole 19. FIG.
FIG. 13 shows the overall configuration of a lubrication circuit in which the hydraulic control valve 22 is inserted at the above-mentioned position. However, the present invention does not relate to the system configuration itself of the lubrication circuit as shown in FIG. 13 but mainly has a feature in the structure of the hydraulic control valve 22. Therefore, the hydraulic control valve itself according to the present invention is applicable not only to the lubrication circuit of the internal combustion engine provided with the hydraulic drive device but also to a general hydraulic drive device.

The lubricating oil passage 18 shown in FIGS. 12 and 13 is usually formed inside the engine block 23.
Although the present invention is characterized by the structure of the hydraulic control valve 22 itself, it does not have any other features, that is, the basic structure of the internal combustion engine itself or the structure of the hydraulic drive device. The structure of the lubricating circuit in the internal combustion engine as the prior art shown in FIGS. 11 and 12 can be used in the embodiment of the present invention, and the description thereof will be the same in the description of the embodiment of the present invention. Duplicate description will be omitted by using reference numerals.

Hydraulic control valve 22 in the first embodiment
As shown in FIGS. 1 and 2, at least a part of the mainstream lubricating oil passage 1 is bored in the engine block 23.
8, a substantially semicircular valve chamber 24 formed across
A generally fan-shaped valve element 25 that can rotate while sliding in a liquid-tight manner in the valve chamber 24,
The valve shaft 26 is fixed by being inserted through a hole 25b of the valve body 25 so that the valve shaft 26 can rotate inside. The valve shaft 26 is provided outside the lubricating oil passage 18. The detailed shape of the valve body 25 used in the first embodiment is shown in FIG.

One end 26a of the valve shaft 26 is inserted into a hole 23a formed in the engine block 23 and is rotatably supported. The other end 26b of the valve shaft 26 passes through a hole 27a of the valve fixing plate 27. And is rotatably supported by a valve fixing plate 27. The valve fixing plate 27 shown in detail in FIG. 4 is seated in a liquid-tight manner via an O-ring 28 at the bottom of a circular hole 23b formed in the engine block 23, and has a male screw formed on the outer periphery. Annular fixing ring 2
9 is fixed by screwing into a female screw formed in the circular hole 23b.

After screwing the fixing ring 29 into a circular hole 23b formed in the engine block 23 and fixing it, a substantially circular valve mounting lid 32 as shown in FIG. Between the two holes 23
It is attached by a method such as press fitting or screwing so as to cover b. In the spring chamber 33 formed by the valve mounting lid 32 and the circular hole 23b, the coil spring 3 as shown in FIG.
4 is attached, and one end 34 a thereof is connected to the hole 27 of the valve fixing plate 27.
b and locked. At the other end 26b of the valve shaft 26, a spring mounting plate 35 shaped as shown in detail in FIG.
a, and is fixed by caulking or the like.
The other end 34b of the above-described coil spring 34 is inserted and locked in 5b.

As shown in FIGS. 2 and 3, a notched bypass passage 25 is formed in a part of the outer periphery of the fan-shaped valve body 25.
a, the lubricating oil passage 18 is not completely shut off by the hydraulic control valve 22 even when the valve body 25 assumes the maximum valve closing position, and the lubricating oil passage 18 is moved to a portion where lubrication of the internal combustion engine is required. The minimum lubricating oil supply is ensured. As shown in FIG. 8, a circular hole 2 formed in the engine block 23 for receiving the hydraulic control valve 22 is provided.
On the bottom surface of 3b, a back pressure release passage 36 such as a groove is provided to release back pressure generated in the valve chamber 24 when the valve body 25 rotates in the semicircular valve chamber 24. .

In the illustrated structure of the hydraulic control valve 22 of the first embodiment, the valve shaft 26 of the valve body 25 is
a, and after the spring mounting plate 35 is fixed to the end 26b of the valve shaft 26, the spring mounting plate 3
The coil spring 34 mounted between the valve 5 and the valve fixing plate 27 is assembled in advance as a temporary assembly outside, and the assembly is inserted into the valve chamber 24 and the circular hole 23b formed in the engine block 23. Insert and fix ring 29
And the valve mounting lid 32,
Integrating the fixing ring 29 and the valve mounting lid 32,
Furthermore, if the valve control plate 22 is also integrated externally in advance and the entire hydraulic control valve 22 is configured as a temporary assembly, the hydraulic control valve 22 for the engine block 23
Installation becomes very simple.

Since the hydraulic control valve 22 according to the first embodiment provided in the main flow side lubricating oil passage 18 has the above-described configuration, when the engine 2 is in operation, the upstream and downstream sides of the valve body 25 are disposed. The valve body 25 automatically rotates in the valve chamber 24 in accordance with the pressure difference of the lubricating oil, that is, the magnitude of the oil pressure in the lubricating oil passage 18 acting on the hydraulic control valve 22, and the valve shaft 26 and the spring are mounted. The valve spring is elastically deformed by winding or unwinding the coil spring 34 via the plate 35, so that the valve opening position is set according to the magnitude of the hydraulic pressure. As a result, the lubricating oil passage 18 on the mainstream side is narrowed to some extent, so that the amount of lubricating oil flowing as hydraulic oil to the VVT oil passage 12 (generally, an oil passage to a hydraulic drive device) branched from the branch portion 13 Increases and the lubricating oil pressure supplied to the VVT 1
The pressure difference before and after.

This operation will be described in more detail with reference to FIGS. FIG. 9 shows that the valve body 25 is operated by the urging force of the spring 34 because the engine 2 is operated at a low rotational speed and the hydraulic pressure acting on the hydraulic control valve 22 is low.
Shows a state in which is rotated to the maximum valve closing position. In this state, a relatively small amount of lubricating oil flow required for lubrication of the lubricated portion is generated in the main flow side lubricating oil passage 18 by only the bypass passage 25a having a predetermined cross-sectional area. ing.

As shown in FIG. 9, the hydraulic control valve 22 is in the maximum closed position, and the main flow side lubricating oil passage 18 is in the hydraulic control valve 2 position.
In a state where the lubricating oil from the branch portion 13 is supplied to the main hole 19 only by the second bypass passage 25a, the main passage-side lubricating oil passage 18 has a pressure loss caused by the limited cross-sectional area of the bypass passage 25a. As a result, the pressure and the flow rate of the lubricating oil in the oil passage supplied to the hydraulic drive device such as the VVT oil passage 12 divided at the branch portion 13 are increased since the flow resistance becomes appropriate. become. Thus, even if the engine 2 rotates at a low speed in a state where the temperature of the lubricating oil is high and the discharge pressure of the oil pump 15 is reduced, it is possible to supply the required hydraulic pressure and oil amount to the hydraulic drive device. Will be possible.

On the other hand, when the discharge pressure of the oil pump 15 increases in an operating state in which the engine 2 rotates at a high speed, the differential pressure across the valve body 25 of the hydraulic control valve 22 increases, so that the valve body 25 The valve 34 rotates against the urging force of the spring 34 and takes a valve opening position having a size corresponding to the differential pressure.
As a result, the amount of lubricating oil sent from the branch portion 13 to the main hole 19 through the lubricating oil passage 18 on the mainstream side and the inside of the hydraulic control valve 22 is increased, and a hydraulic drive such as the variable valve timing mechanism (VVT) 1 is used. It serves to keep the amount of lubricating oil supplied to the device approximately constant.

When the lubricating oil pressure discharged from the oil pump 15 further increases, the valve body 25 of the hydraulic control valve 22 is completely pushed into the valve chamber 24 as shown in FIG.
The lubricating oil passage 18 no longer partially blocks the main flow side lubricating oil passage 18, and the lubricating oil passage 18 substantially eliminates flow resistance and pressure loss.

Needless to say, the lubricating oil passage 1 exceeds a predetermined value.
When the oil pressure in the VVT oil passage 8 and the VVT oil passage 12 and, consequently, the branch portion 13 rises, the pressure regulating valve 16 opens, so that the lubricating oil pressure in those oil passages does not rise to an abnormally high pressure.

A hydraulic control valve 37 of the first embodiment shown in FIGS. 1 to 10 in which a part of the shape and structure of the hydraulic control valve 22 is changed is shown in FIG. 14 as a second embodiment of the present invention.
And FIG. Portions in which the hydraulic control valve 37 has the same structure as the hydraulic control valve 22 are denoted by common reference numerals, and description thereof is omitted.

The features of the hydraulic control valve 37 of the second embodiment are as follows.
The point that the shape around the valve chamber is simplified compared to the case of the first embodiment, and that the bypass passage and the back pressure relief passage are formed by the structure of the fan-shaped valve body that is easy to process. FIG.
As shown in FIG. 5, in the hydraulic control valve 37 of the second embodiment, the hydraulic control valve 22 of the first embodiment shown in FIGS.
, A substantially semicircular valve chamber 38 having no back pressure release passage or the like is formed. The valve chamber 38 forms at least a space in the wall of the engine block 23 having a size and a shape that allows the fan-shaped valve element to be completely immersed when the hydraulic control valve 37 is fully opened.

The fan-shaped valve element according to the second embodiment corresponds to the simplified semicircular valve chamber 38 shown in FIG.
The valve body 39 having the shape and structure shown in FIG. The valve body 39 has walls 39a and 39c extending radially from the valve shaft 26.
And two fan-shaped walls 39d, 39 connecting those walls
e, and has a hollow shape with a circumferential portion opened. Bypass passage 39 to ensure minimum lubricating oil level
In the example of FIG. 15A, the corner of the fan-shaped valve body 39 is simply cut out, but in the example of FIG.
A bypass hole 39f is also formed in 9a. Needless to say, either the bypass passage 39a or the bypass hole 39f formed by the notch may be provided. In addition, valve room 3
Escape passages for the back pressure generated in the radial wall 3
A back pressure relief hole 39g is formed in 9c. Note that 39
h is a hole provided in the valve body 39, and the valve shaft 26 is
9h is inserted and fixed.

Since the hydraulic control valve 37 of the second embodiment has such a structure, the same operation and effect as those of the hydraulic control valve 22 of the first embodiment can be obtained, but there is an advantage that the manufacture becomes simpler. . In the second embodiment, the shape of the valve body 39 is more complicated than that of the valve body 25 in the hydraulic control valve 22 of the first embodiment, but the valve body 39 is processed into a shape as shown in FIG. 15 before assembly. Is relatively easy and can be very easily manufactured using the die casting method.

[Brief description of the drawings]

FIG. 1 is a vertical sectional side view showing a first embodiment of the present invention.

FIG. 2 is a vertical sectional front view taken along line II-II of FIG.

FIG. 3 shows a valve element according to the first embodiment.
(A) is a front view, (b) is a bottom view.

FIG. 4 shows a valve fixing plate according to the first embodiment,
(A) is a plan view and (b) is a front view.

FIGS. 5A and 5B show a valve mounting lid according to the first embodiment, wherein FIG. 5A is a plan view and FIG. 5B is a front view.

FIGS. 6A and 6B show a spring according to the first embodiment, wherein FIG. 6A is a front view and FIG. 6B is a side view.

FIGS. 7A and 7B show a spring mounting plate according to the first embodiment, wherein FIG. 7A is a plan view and FIG. 7B is a front view.

FIG. 8 is a vertical sectional front view taken along line VIII-VII1 of FIG. 1;

FIG. 9 is a vertical sectional front view showing a state where the hydraulic control valve is closed.

FIG. 10 is a vertical sectional front view showing a state where the hydraulic control valve is opened.

FIG. 11 is a partially cutaway perspective view showing a variable valve timing mechanism (VVT) which is an example of a hydraulic drive device.

12 is a perspective view conceptually showing a lubrication circuit of a six-cylinder engine provided with the variable valve timing mechanism of FIG.

FIG. 13 is a system configuration diagram showing the overall configuration of a lubrication circuit for an internal combustion engine including the hydraulic control valve of the present invention.

FIG. 14 is a longitudinal sectional front view showing a second embodiment of the present invention.

FIG. 15 shows a valve element according to the second embodiment,
(A) is a front view, (b) is a bottom view.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Variable valve timing mechanism (VVT) 2 ... Engine 12 ... VVT oil passage (oil passage of hydraulic drive device, 2nd lubricating oil passage) 13 ... Branch part of lubricating oil passage 15 ... Oil pump 18 ... Mainstream lubrication Oil passage (first lubricating oil passage) 22 hydraulic control valve (first embodiment) 23 engine block 24 valve chamber 25 fan-shaped valve element (first embodiment) 26 valve shaft 34 coil spring 36 ... Back pressure relief passage 37 ... Hydraulic control valve (Second embodiment) 38 ... Valve chamber 39 ... Sector-shaped valve element (Second embodiment) OCV ... Hydraulic switching valve for variable valve timing mechanism VVT ... Variable valve timing mechanism

Claims (6)

[Claims] 1. An internal combustion engine having a hydraulic drive device driven by lubricating oil pressure, wherein a first lubricating oil for supplying pressurized lubricating oil to a portion of the internal combustion engine requiring lubrication is provided.
A lubricating oil passage, a second lubricating oil passage for supplying pressurized lubricating oil to the hydraulic drive device, and a lubricating oil pressurized by an oil pump through the first lubricating oil passage and the second lubricating oil passage. A lubricating circuit including a lubricating oil passage branch for distributing the lubricating oil to the first lubricating oil passage. A force for urging the valve body toward the valve-opening position by a differential pressure of the lubricating oil pressure acting on the upstream and downstream first lubricating oil passages, and a force for urging the valve body toward the valve-closing position The valve body automatically moves to a position where the urging force of the urging means is balanced to take a valve-opening position in accordance with the differential pressure, so that the first lubricating oil passage is supplied to the second lubricating oil passage. When the lubricating oil pressure higher than the oil passage can be supplied and the valve body takes the maximum valve opening position The valve element is configured to retreat from the first lubricating oil path so that the flow resistance in the first lubricating oil path becomes substantially zero, and the valve element is moved to a valve closing position. , A predetermined cross-sectional area for connecting the first lubricating oil passage on the upstream side and the downstream side of the valve body to allow a minimum necessary amount of lubricating oil to pass through a portion requiring lubrication. A hydraulic control valve in a lubrication circuit for an internal combustion engine, comprising a bypass passage having: 2. The valve body is capable of retracting into a valve chamber formed inside a wall surface of the first lubricating oil passage when the valve body assumes a maximum valve opening position. The hydraulic control valve according to claim 1, wherein: 3. The valve body includes a valve shaft that is perpendicular to the first lubricating oil passage at a position outside the first lubricating oil passage, and rotates around the valve shaft. And the valve body is immersed in a valve chamber formed on a wall surface of the lubricating oil passage when the valve body moves to the maximum valve opening position, and the first lubricating oil is removed. The hydraulic control valve according to claim 2, wherein the hydraulic control valve can be retracted from the oil passage. 4. The hydraulic control valve according to claim 1, wherein the hydraulic drive device is a variable valve timing mechanism. 5. A passage for releasing back pressure generated in a space formed behind the valve body in a valve chamber in which the valve body moves, is provided. Hydraulic control valve described in the above. 6. A hydraulic control valve including the valve body is mostly
After being assembled in advance as a temporary assembly outside,
The hydraulic control valve according to any one of claims 1 to 5, wherein the hydraulic control valve is integrally attached to the internal combustion engine.