JP2003322007A - Hydraulic control device for internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve actuation responsiveness of a valve stopping mechanism 14 using working fluid discharged from a second phase changing mechanism 12. <P>SOLUTION: A V-type 8-cylinder internal combustion engine of a one-plane crankshaft type is composed in such a way that the cylinders on one bank can rest, a valve stopping mechanism 14 is provided, and the second phase changing mechanism 12 sharing an oil pump 10 is provided. When resting of the cylinders is started, the second phase changing mechanism 12 is simultaneously actuated to the advance side. A circulation oil passage 48 is provided to supply working fluid discharged from the second phase changing mechanism 12 at the time of this advance action to the valve stopping mechanism 14, thereby responsiveness of the valve stopping mechanism 14 is improved. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to two types of hydraulic actuating mechanisms that share a hydraulic power source and function independently of each other, and more specifically, the hydraulic pressure of an internal combustion engine provided with an intake valve phase changing mechanism and a valve stop mechanism. Regarding the control device.

[0002]

2. Description of the Related Art In the field of internal combustion engines, it is common practice to operate various hydraulic operating mechanisms using an oil pump used for circulating lubricating oil as a hydraulic source. Examples of such a hydraulic actuating mechanism include a valve stop mechanism that temporarily stops the opening and closing of intake and exhaust valves of some cylinders in accordance with engine operating conditions. The above valve stop mechanism is applied to a multi-cylinder internal combustion engine that performs so-called cylinder number control, in which some cylinders are deactivated and only some cylinders are operated at the time of partial load, etc. The intake / exhaust valves, and at least the intake valves, of the cylinder group are set to stop.

As a hydraulic actuating mechanism, there is also known a variable valve actuating mechanism which changes the opening / closing timing of the intake valve and the exhaust valve and the valve lift amount according to the engine operating conditions. As a hydraulic variable valve mechanism, in Japanese Patent Laid-Open No. 5-248217, by switching between a low-speed rocker arm and a high-speed rocker arm, the opening / closing timing of an intake valve or an exhaust valve is switched to two stages. A possible variable valve mechanism is disclosed,
A phase changing mechanism that retards the phase of the operating angle of the intake and exhaust valves (the phase with respect to the crankshaft) is also known and has already been put into practical use.

[0004]

The above-mentioned valve stop mechanism is
It can be used in combination with a variable valve mechanism, for example, a phase changing mechanism. However, when the valve stop mechanism and the phase changing mechanism are provided in this way, the engine operating conditions change and the operating state of all cylinders changes from a partial cylinder to a partial cylinder. When switching the valve stop mechanism to shift to the idle state, the phase change mechanism usually needs to operate at the same time as the engine operating conditions change, so the hydraulic pressure supplied to the valve stop mechanism is insufficient. As a result, the operation response may be deteriorated. A dedicated oil pump, accumulator, or the like may be provided in order to prevent such a decrease in operation responsiveness, but in this case, the configuration of the hydraulic circuit becomes complicated, resulting in an increase in weight and an increase in cost. There is a risk.

The present invention has been made in view of the above problems, and when a valve stop mechanism and a phase changing mechanism sharing a hydraulic pressure source are provided, the operation response of the valve stop mechanism is simple. The purpose is to improve.

[0006]

According to the present invention, an internal combustion engine is composed of a first cylinder group and a second cylinder group. First
The cylinder group includes a first phase changing mechanism that retards the phase of the operating angle of the intake valve, and is composed of a plurality of cylinders that burn at equal intervals so that stable operation can be performed when only the first cylinder group is operating. . In addition, the second cylinder group also includes a second phase changing mechanism that retards the phase of the operating angle of the intake valve, and temporarily opens and closes the intake valve by supplying hydraulic pressure from a hydraulic source shared with the second phase changing mechanism. It is equipped with a valve stop mechanism that stops it automatically. Therefore, for example, under a predetermined operating condition such as a partial load, the second cylinder group is in the idle state, and at the same time, the valve stop mechanism stops the opening and closing of the intake valve of the second cylinder group. The valve stop mechanism may stop both the intake valve and the exhaust valve. Further, in the hydraulic control device of the present invention, the hydraulic oil discharged from the second phase changing mechanism of the second cylinder group when the second phase changing mechanism of the second cylinder group operates toward the advance side is supplied to the valve stop mechanism. As described above, the return oil passage is provided between the second phase changing mechanism and the valve stop mechanism.

Therefore, if the second phase changing mechanism moves to the advance side almost at the same time when the valve stopping mechanism is switched to the valve stopped state, the hydraulic oil discharged from the second phase changing mechanism is sent to the valve stopping mechanism. Since the hydraulic pressure is supplied, the valve stop mechanism is switched immediately with the start of hydraulic pressure supply from the hydraulic pressure source. That is,
Normally, the operating oil discharged as it is is used to improve the operation response of the valve stop mechanism.

[0008]

According to the present invention, at the time of switching to the valve stop, the hydraulic oil discharged from the second phase changing mechanism is supplied to the valve stop mechanism through the return oil passage, so that a special hydraulic pressure such as an accumulator is separately provided. The operation response of the valve stop mechanism can be improved without using an auxiliary device.

[0009]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment in which the present invention is applied to a V-type 8-cylinder internal combustion engine will be described in detail below with reference to the drawings. First, the combustion interval and the like of the V-type 8-cylinder internal combustion engine will be described. FIG. 6 shows a cylinder arrangement of a V-type 8-cylinder internal combustion engine, in which the left bank 1 and the right bank 2 are arranged in a V-shape with a bank angle of 90 °. Left bank 1 is cylinder # 1,
It includes four cylinders of # 3 cylinder, # 5 cylinder, and # 7 cylinder, and the right bank 2 includes # 2 cylinder, # 4 cylinder, # 6 cylinder, and # 6 cylinder.
It includes four cylinders, eight cylinders. The V-type 8-cylinder internal combustion engine of this embodiment is of the so-called 1-plane crankshaft type in which the crankpins are arranged at 180 ° apart, and the ignition sequence of the 8 cylinders is shown in FIG. 7. Thus, “# 1 → # 4 → # 5 → # 2 → # 7 → # 6 → # 3 → #
8 → ”, and the respective combustion intervals are 90 °. Looking at this for each bank, in the left bank 1, the combustion interval of 180 ° is “# 1 → # 5 → # 7 → # 3 →”, and in the right bank 2, the combustion interval is also 180 °. “# 4 → # 2 → # 6 → # 8 →”. In other words, both banks burn at equal intervals. Therefore, in the present embodiment, one bank, for example, the four cylinders of the right bank 2 becomes the first cylinder group that is always in operation, and the other bank, that is, the four cylinders of the left bank 1 is the second cylinder group that can be deactivated depending on the operating conditions. Has become. When only the first cylinder group in the right bank is operated, as described above, “# 4 → # 2 → # 6 → # 8
→ ”is ignited at regular intervals of 180 °. Therefore,
Stable operation is possible with the cylinders of the left bank 1 in a deactivated state, and output can be improved by reducing exhaust interference.

The left bank 1, which is a deactivated cylinder, is provided with a valve stop mechanism for stopping the opening and closing of intake and exhaust valves when the cylinder is deactivated, as will be described later. Further, a phase changing mechanism is provided for each bank in order to optimize the phase of the operating angle of the intake valve according to the operating conditions. All of these mechanisms are driven by utilizing the hydraulic pressure of the lubricating oil of the internal combustion engine, and the hydraulic control device will be described below. In addition,
The phase changing mechanism of the right bank 2 that is always operating is the first phase changing mechanism, and the phase changing mechanism of the left bank 1 that can be paused is the second phase changing mechanism.
These are phase changing mechanisms, but they have basically the same configuration.

FIG. 1 is a schematic configuration diagram showing a hydraulic control device according to the present invention, and particularly shows a configuration on the left bank 1 side which can be stopped. As shown in the figure, this hydraulic control device supplies hydraulic pressure to the second phase changing mechanism 12 and the valve stop mechanism 14 as necessary, and controls the oil pump 10 that circulates lubricating oil to each part of the internal combustion engine. It is shared as a source. Then, a phase changing hydraulic control valve 16 for switching and controlling the hydraulic pressure supplied from the oil pump 10 to the second phase changing mechanism 12, and a valve for switching and controlling the hydraulic pressure supplied from the oil pump 10 to the second hydraulic pressure operating mechanism 14. A stop hydraulic control valve 18 is provided.

The structure of the second phase changing mechanism 12 is well known, and briefly described with reference to FIG. 2, the phase changing mechanism 12 rotates integrally with the cam sprocket 21 that rotates in synchronization with the crankshaft. Outer gear part 22
And is arranged coaxially inside the outer peripheral side gear portion 22,
An inner peripheral side gear part 24 which rotates integrally with an intake cam shaft 23 for driving an intake valve, and an outer peripheral side gear part 22 thereof.
And a substantially annular piston 25 that meshes with the inner and outer peripheral surfaces of the inner peripheral side gear portion 24 via a helical spline, and a return spring 26 that biases the piston 25 toward the retard side.
And are equipped with.

A retard angle side hydraulic chamber 27 and an advance angle side hydraulic chamber 28 face both end surfaces of the piston 25 in the axial direction, and the piston 25 moves in the axial direction according to the hydraulic pressure of these hydraulic chambers 27, 28. As a result, the phase of the intake camshaft 23 relative to the cam sprocket 21 changes, and the operating angle phase of the intake valve changes continuously.

The structure of the valve stop mechanism 14 is also known, and will be briefly described with reference to FIG. 3. When the oil pressure in the valve stop hydraulic chamber 31 is low, the spring force of a spring (not shown) causes a rod-shaped cup. The ring 33 projects to a position where the ring 33 engages with the auxiliary rocker arm 36a having the roller type cam follower 34, and the pressing force of the cam 35 passes through the auxiliary rocker arm 36a, the coupling 33 and the rocker arm 36, and the intake / exhaust valve 37 (the intake valve 37a and the intake valve 37a Exhaust valve 37
Then, the normal opening / closing operation is performed. On the other hand, when a predetermined operating hydraulic pressure is supplied to the valve stop hydraulic chamber 31, the piston 38 pushes the coupling 33 in the backward direction in which the coupling 33 is separated from the auxiliary rocker arm 36a against the spring force of the spring, and the auxiliary rocker arm 36a The rocker arm 36 is substantially separated. Therefore, the power transmission from the cam 35 to the rocker arm 36 is cut off, and the intake / exhaust valve 37 is stopped. That is, when the cylinder group of the left bank 1 is inactive, hydraulic pressure is supplied to the valve stop mechanism 14 and the intake / exhaust valve 37 is held closed.

Next, with reference to FIGS. 1 to 4, the circuit configuration of this hydraulic control device will be described. This circuit includes a first hydraulic pressure supply oil passage 41 for supplying hydraulic pressure from the oil pump 10 to the phase changing hydraulic control valve 16, and a second hydraulic pressure supply for supplying hydraulic pressure from the oil pump 10 to the valve stop hydraulic control valve 18. The oil passage 42, the retarding side control oil passage 43 connecting the phase changing hydraulic control valve 16 and the retard side hydraulic chamber 27, and the phase changing hydraulic control valve 16 connecting the advance side hydraulic chamber 28. The advance side control oil passage 44, the valve stop control oil passage 45 connecting the valve stop hydraulic control valve 18 and the valve stop hydraulic chamber 31, and the phase change hydraulic control valve 16 to the oil pan during the retard operation. A retard side drain oil passage 46 for discharging hydraulic oil to 11 and a valve stop drain oil passage 47 for discharging hydraulic oil from the valve-stop hydraulic control valve 18 to the oil pan 11 are provided.

The retard angle side hydraulic chamber 27 of the second phase changing mechanism 12 and the valve stop hydraulic chamber 31 of the valve stop mechanism 14 communicate with each other and are discharged from the retard angle side hydraulic chamber 27 during the advancing operation. A return oil passage 48 for supplying hydraulic oil to the valve stop hydraulic chamber 31 is provided. The recirculation oil passage 48 has a shape including the retard angle side control oil passage 43 and joins the valve stop control oil passage 45 on the downstream side. That is, the return oil passage 4
The tip of 8 is connected to a valve stop control oil passage 45 between the valve stop hydraulic control valve 18 and the valve stop hydraulic chamber 31.
Regardless of the opened / closed state of the valve stop hydraulic control valve 18, hydraulic oil can be supplied to the valve stop control oil passage 45.

A check valve 49 is disposed in the return oil passage 48 to prevent the reverse flow of the hydraulic oil in the direction from the valve stop mechanism 14 to the second phase changing mechanism 12. Further, in the return oil passage 48, the upstream side of the check valve 49 (the phase changing mechanism 1
(2 side) is provided with an advance side drain branch oil passage 50 that extends to the oil pan 11, and a control valve 51, which is a check valve, is provided in the advance side drain branch oil passage 50. ing. The opening load of the check valve 49 is set lower than the opening load of the control valve 51.
Opening a load of about 0.1 kgf / cm ^2, the valve opening force of the control valve 51 is set to about 0.3 kgf / cm ^2.

FIG. 8 shows a circuit configuration on the right bank 2 side which is always operating. As described above, the first phase changing mechanism 12 ′ is provided on the right bank 2 side. However, the first phase changing mechanism 12 ′ itself is the second phase changing mechanism 1 ′.
The configuration is exactly the same as that of No. 2 and the configuration of the hydraulic circuit is the same except for the portion of the return oil passage 48, and therefore, the same parts as those described above are designated by the same reference numerals. In this embodiment, the oil pump 10 serving as a hydraulic pressure source is shared with the hydraulic circuit on the left bank 1 side. From the oil pump 10 to the phase changing hydraulic control valve 16 as in the configuration on the left bank 1 side described above. A first hydraulic pressure supply oil passage 41 for supplying hydraulic pressure, a retard side control oil passage 43 connecting the phase change hydraulic control valve 16 and the retard side hydraulic chamber 27, a phase change hydraulic control valve 16 and an advance angle. The advance side control oil passage 44 connecting the side hydraulic chamber 28 and the phase changing hydraulic control valve 16 from the oil pan 1 during the retard operation.
1, a retard side drain oil passage 46 for discharging hydraulic oil is provided. The right bank 2 side does not have the return oil passage 48, and the hydraulic oil pushed out from the advance side hydraulic chamber 28 during the advance operation is passed through the advance side drain oil passage 52 and the phase changing hydraulic control valve. The oil is discharged from 16 to the oil pan 11.

Next, the operation of the embodiment configured as described above will be described.

In the first and second phase changing mechanisms 12 'and 12, the position of the spool 16a is controlled by variably controlling the duty ratio of the pulse signal given to the solenoid for driving the spool 16a of the phase changing hydraulic control valve 16. Is controlled to switch the direction of the hydraulic pressure acting on each of the phase changing mechanisms 12 ', 12 to change the position of the piston 25 and control the operating angle phase of the intake valve corresponding thereto.

Specifically, during the retarding operation for changing the operating angle phase of the intake valve to the retarding side, the phase changing hydraulic control valve 16 is used.
2A, the hydraulic pressure from the oil pump 10 is supplied to the retard side hydraulic chamber 27 via the first hydraulic pressure supply oil passage 41 and the retard side control oil passage 43. On the other hand, the hydraulic oil in the advance side hydraulic chamber 28 is discharged to the oil pan 11 through the advance side control oil passage 44 and the retard side drain oil passage 46. As a result, the piston 25 is pushed and moved to the retard side (left side in FIG. 2). Note that FIG.
(A) shows the lift characteristics of the intake valve and the exhaust valve in the most retarded state.

During the advancing operation for changing the operating angle phase of the intake valve to the advancing side, the spool position shown in FIG.
While the hydraulic pressure is supplied to the advance side hydraulic chamber 28 through the first hydraulic pressure supply oil passage 41 and the advance side control oil passage 44, the hydraulic oil in the retard side hydraulic chamber 27 is discharged through the retard side control oil passage 43. To be done. This hydraulic oil flows through the return oil passage 48 on the left bank 1 side.
Is discharged to the valve stop control oil passage 45 via the right bank 2
On the side, the oil pan 11 is connected by the advance side drain oil passage 52.
Is discharged to. As a result, the piston 25 is advanced (see FIG. 2).
To the right side of) and moved. Note that FIG. 2B shows the lift characteristics of the intake valve and the exhaust valve in the most advanced state.

When the operating angle phase of the intake valve is maintained at the current phase, the spool position is set as shown in FIG. 2 (c), and the spool 16a causes the retard side control oil passage 43 and the advance side control oil passage 44 to move. Both ports to be connected are closed, the hydraulic pressures in the hydraulic chambers 27 and 28 are locked, and the piston 2
5 is held at the current position.

By switching the hydraulic pressure supplied to the phase changing mechanisms 12 ', 12 via the phase changing hydraulic control valve 16 in this way, the operating angle phase of the intake valve is feedback-controlled to a characteristic according to the engine operating conditions. be able to.

On the other hand, in the valve stop mechanism 14 provided on the left bank 1 side, as shown in FIGS. 1 and 4, the position of the spool 18a of the valve stop hydraulic control valve 18 is switched according to the engine operating conditions. As a result, the valve opening / closing motion is temporarily stopped when the cylinder group on the left bank 1 side is switched between active and inactive. That is, when the cylinder group on the left bank 1 side is in operation, the spool is in the spool position shown in FIG. 4A, and the working oil in the valve stop hydraulic chamber 31 is controlled by the valve stop control oil passage 45 and the valve stop drain oil passage. It is discharged to the oil pan 11 through 47. On the other hand, when the cylinder group on the left bank 1 side is inactive, as shown in FIG.
In the spool position shown in (b), the second hydraulic oil supply passage 4
The oil pressure of the oil pump 10 is supplied to the valve stop hydraulic chamber 31 via the valve 2 and the valve stop control oil passage 45. As a result, the opening and closing of the intake valve and the exhaust valve are stopped, as described above.

Here, in this embodiment, when the valve stop is performed in the cylinder group on the left bank 1 side as described above, the left bank 1
The second phase changing mechanism 12 of the cylinder group on the side simultaneously operates toward the advance side. When the second phase changing mechanism 12 is thus advanced, the working oil is discharged from the retard side hydraulic chamber 27 to the return oil passage 48 as the piston 25 moves toward the advance side. The hydraulic pressure in the control oil passage 45 for valve stop is high to some extent. Therefore, under such a circumstance, when the valve stop hydraulic control valve 18 is switched so as to supply the hydraulic pressure to the valve stop mechanism 14, the hydraulic pressure introduced into the valve stop mechanism 14 quickly increases and the valve stop immediately. It is switched to the state. That is, from the oil pump 10 to the second hydraulic pressure supply oil passage 4
2. Valve stop hydraulic control valve 18 and valve stop control oil passage 4
In addition to the hydraulic oil supplied to the valve stop hydraulic chamber 31 via 5, the hydraulic oil is also supplied from the retard side hydraulic chamber 27 side via the return oil passage 48. Therefore, the retard angle side hydraulic chamber 27 functions as a kind of hydraulic accumulator, and the valve stop mechanism 14 can be provided without separately providing an accumulator or the like.
It is possible to improve the operation response of the.

Particularly, when the engine speed is low, the oil pump 10
Since the hydraulic pressure supplied from the engine is low, the operating response tends to decrease. However, according to the present embodiment, the hydraulic oil is also supplied from the retard side hydraulic chamber 27, so that the supplied pressure is low. It is possible to obtain good actuation response even in the operating region.

Furthermore, the return oil passage 48 joins with the valve stop control oil passage 45 connecting the valve stop hydraulic control valve 18 and the valve stop hydraulic chamber 31, and the valve stop hydraulic control valve 18 is joined. The hydraulic oil is directly supplied to the valve stop hydraulic chamber 31 without passing through the valve. Therefore, the operation response is surely improved.

Here, in the present embodiment, the cylinder group on the left bank 1 side becomes a deactivated cylinder when the valve is stopped. Therefore, it is not necessary to move the second phase changing mechanism 12 originally, but the right cylinder which is an operating cylinder. By positively continuing the same phase control as that of the cylinder group on the bank 2 side, the first phase changing mechanism 1 is operated at the time of switching the valve stop.
2 moves toward the advance side. That is, FIG.
Shows a relationship between an advance area H1 in which the first and second phase changing mechanisms 12 ', 12 are controlled to advance positions, and a cylinder stop area H2 in which the cylinder group on the left bank 1 side is stopped. The cylinder deactivation region H2 is included inside the advance region H1. That is, in this embodiment, in the partial load region,
While some of the cylinders are deactivated, the operating angle phase of the intake valves of the operating cylinders is advanced to expand the internal EGR, thereby improving fuel efficiency and reducing NOx.

Therefore, for example, as shown by the arrow A1 in FIG. 5, in a situation where the rotation speed increases from the low rotation and low load region near the idle, the cylinder group on the left bank 1 side is almost stopped (valve stop). At the same time, the first and second phase changing mechanisms 12 ′, 12
Tries to change to the advance side. Further, as shown by an arrow A2, in a situation where the rotation speed decreases from the high rotation and low load range in which all the cylinders are operating, the first and second phase changing mechanisms 12 ′, 12 are also advanced. Switching to the cylinder deactivation operation is started while changing to. Further, as shown by the arrow A3, in a situation where the torque decreases from the high load range, the control characteristics of the first and second phase changing mechanisms 12 ', 12 are basically within the advance angle region H1. However, since the phase control characteristic is set to a characteristic in which the high load side is relatively retarded as compared with the medium load region, the first and second phase changing mechanisms 12 are associated with the change of the arrow A3. ', 12 changes slightly to the advance side. Therefore, also when the first and second phase changing mechanisms 12 ', 12 are gradually changing to the advance side, the switching to the cylinder deactivation (valve stop) is started.

In this way, by controlling the phase of the left bank 1 side, which is a deactivated cylinder, in the same manner as the right bank 2 side, the second phase changing mechanism 12 simultaneously moves to the advance side when the valve is stopped. That is, since the operating oil is supplied to the valve stop hydraulic chamber 31 through the return oil passage 48, the operating responsiveness at the time of starting the cylinder deactivation operation is effective despite the simple structure. Can be improved.

When the cylinder deactivation operation is continued, the second phase changing mechanism 12 is operated in a situation where the hydraulic pressure on the downstream side of the check valve 49 is high and the check valve 49 cannot be opened. When operating to the angle side, the control valve 51 is opened so that the hydraulic oil in the retard side hydraulic chamber 27 can be reliably discharged to the oil pan 11 via the advance side drain branch oil passage 50. Has become.

When all cylinders are operating, the valve opening load of the check valve 49 is lower than the valve opening load of the control valve (check valve) 51, and the hydraulic pressure on the downstream side of the check valve 49 is low. When the phase changing mechanism 12 moves to the advance side, only the check valve 49 opens. Therefore, the hydraulic oil in the retard side hydraulic chamber 27 is discharged to the oil pan 11 via the return oil passage 48, the valve stop control oil passage 45 and the valve stop drain oil passage 47.

The present invention has been described above based on a preferred embodiment, but the present invention is not limited to this embodiment and includes various modifications and changes. For example, instead of the above control valve 51, an orifice for generating a pressure difference may be provided.

In the above embodiment, the phase control of the intake valve of the cylinder group on the left bank 1 side is always performed in the same manner as on the right bank 2 side.
It is also possible to positively move only the second phase changing mechanism 12 on the side toward the advance side so as to more reliably enhance the operation response of the valve stop mechanism 14.

[Brief description of drawings]

FIG. 1 is a configuration diagram showing a circuit configuration on a left bank side in a hydraulic control device according to an embodiment of the present invention.

FIG. 2 is an operation explanatory view of a phase changing mechanism and its hydraulic control valve.

FIG. 3 is a perspective view showing a valve stop mechanism.

FIG. 4 is an operation explanatory view schematically showing a valve stop hydraulic control valve.

FIG. 5 is a characteristic diagram showing an advance region and a cylinder deactivation region of the phase changing mechanism.

FIG. 6 is an explanatory diagram showing a cylinder arrangement of a V-type 8-cylinder internal combustion engine.

FIG. 7 is an explanatory diagram of a 1-plane crankshaft type ignition sequence.

FIG. 8 is a configuration diagram showing a circuit configuration on the right bank side.

[Explanation of symbols]

10 ... Oil pump (hydraulic power source) 12 ... Second phase changing mechanism 14 ... Valve stop mechanism 48 ... Return oil passage 49 ... Check valve 50 ... Advance side drain branch oil passage 51 ... Control valve

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Claims (7)

[Claims] 1. A first device for delaying the phase of an operating angle of an intake valve.
A first cylinder group including a plurality of cylinders that burns at equal intervals and a second phase changing mechanism that retards the phase of the operating angle of the intake valve, and is shared with the second phase changing mechanism. And a second cylinder group having a valve stop mechanism for temporarily stopping the opening and closing of the intake valve by the supply of hydraulic pressure from a hydraulic pressure source, the second phase of the second cylinder group. Between the second phase change mechanism and the valve stop mechanism, so that the hydraulic oil discharged from the second phase change mechanism is supplied to the valve stop mechanism when the change mechanism operates toward the advance side. A hydraulic control device for an internal combustion engine, characterized in that a return oil passage is provided in the. 2. A valve stop hydraulic control valve is provided between the hydraulic source and the valve stop mechanism, and a tip of the return oil passage is provided with the valve stop hydraulic control valve and the valve stop mechanism. The hydraulic control device for an internal combustion engine according to claim 1, wherein the hydraulic control device is connected to an oil passage between the two. 3. A check valve for preventing backflow of hydraulic oil from the valve stop mechanism to the second phase changing mechanism is disposed in the return oil passage. A hydraulic control device for an internal combustion engine as set forth in. 4. A control valve is provided in a drain branch oil passage branching upstream of the check valve in the return oil passage and discharging hydraulic oil, and a valve opening load of the control valve is equal to that of the check valve. The hydraulic control system for an internal combustion engine according to claim 3, wherein the hydraulic load is set to be higher than the valve opening load. 5. The first hydraulic pressure changing mechanism, the second hydraulic pressure changing mechanism, and the valve stopping mechanism share the same hydraulic pressure source. Control system for internal combustion engine. 6. The internal combustion engine is a V-cylinder internal combustion engine having one plain crankshaft, the cylinders of one bank constitute a first cylinder group, and the cylinders of the other bank constitute a second cylinder group. The hydraulic control device for an internal combustion engine according to any one of claims 1 to 5, characterized in that: 7. The second phase changing mechanism is controlled so as to change to an advance side when the valve stopping mechanism is switched to a valve stopped state. A hydraulic control device for an internal combustion engine as set forth in.