JPS6358247B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention includes an injector device that increases the pressure of fuel oil and injects it using a hydraulic servo mechanism, and a hydraulic valve drive device that controls the opening and closing of an intake valve and an exhaust valve. The present invention relates to an electronic hydraulic control device for an internal combustion engine in which hydraulic control of an intake and exhaust valve device is performed by an electronic control device.

As a conventional example of this type of electro-hydraulic control system for an internal combustion engine, it is known that the hydraulic power source for the injector device and the intake/exhaust valve device are provided separately. If hydraulic power sources are provided separately, each hydraulic power source must be equipped with its own parts such as a hydraulic oil tank, filter, and hydraulic pump, which increases the cost and complicates the structure due to the increase in the number of parts. In addition, there was a problem that the device became larger.

In addition, conventional electro-hydraulic control systems for internal combustion engines generally use hydraulic oil with a higher viscosity than engine lubricating oil or fuel oil, so viscous resistance in the operating parts and resistance in the oil passages are reduced. Another problem is that the responsiveness of the injector device and the intake/exhaust valve device deteriorates due to a decrease in the performance of the solenoid coil due to an increase in the temperature of the hydraulic oil.

In view of the problems of the conventional electro-hydraulic control device for an internal combustion engine as described above, the present invention aims to reduce costs, simplify the structure, and reduce the size and weight of the device by standardizing the hydraulic power source. The main purpose of this system is to improve the responsiveness of the injector device and intake/exhaust valve device by using a portion of the fuel oil as hydraulic fluid for the hydraulic actuator. A fuel oil supply device having a fuel supply pump driven by an engine, an injector unit that increases the pressure of fuel oil fed from the fuel oil supply device by a hydraulic servo mechanism and injects it from a nozzle valve, and operates the hydraulic servo mechanism. an injector device having a solenoid valve section that controls the flow of hydraulic oil;
A hydraulically driven intake valve device including a hydraulic valve driving device having a valve operating mechanism that opens and closes an intake valve using hydraulic pressure and a solenoid valve that controls the flow of hydraulic oil that operates the valve operating mechanism. and a hydraulically driven exhaust valve device having substantially the same configuration as the hydraulically driven intake valve device, a solenoid coil of a solenoid valve portion of the injector device, a solenoid coil of a solenoid valve portion of the intake valve device and the exhaust valve device. and an electronic control device having a microcomputer that controls the internal combustion engine appropriately according to the operating state of the internal combustion engine, and a part of the fuel oil that is force-fed from the fuel supply pump of the fuel oil supply device to the injector section side of the injector device. The present invention is characterized in that it is used as hydraulic oil for the hydraulic servo mechanism of the injector device and the valve operating mechanisms of the intake valve device and the exhaust valve device.

Hereinafter, the electro-hydraulic control device for an internal combustion engine of the present invention will be explained with reference to the system diagram shown in FIG.
This electro-hydraulic control device for an internal combustion engine is an internal combustion engine 6.
8, an injector device T that injects fuel oil, a hydraulically driven intake valve device X having a hydraulic valve drive device, and a hydraulically driven exhaust valve. Equipment Y
(details not shown) and an electronic control device R that controls an injector device T, an intake valve device X, and an exhaust valve device Y according to the operating state of the internal combustion engine.

The fuel oil supply device S pressurizes the fuel oil in the fuel tank 71 to an appropriate pressure by the fuel supply pump 69, and supplies the fuel oil to the first fuel supply pipe 73 and the second fuel supply pipe 7.
4 to the injector device T, intake valve device X, and exhaust valve device Y.
In the figure, 70 is a filter, 75 is a pressure regulating valve,
Reference numeral 72 denotes an accumulator or collecting pipe for regulating the pressure of the fuel oil pumped from the fuel supply pump 69.

The injector device T includes an injector section 32 that increases the pressure of fuel oil and injects it by a hydraulic servo mechanism 33 in the injector turbo day 1, and a solenoid valve section 31 that controls the flow of hydraulic oil of the hydraulic servo mechanism 33. are doing. This hydraulic servo mechanism 33 is composed of a large-diameter servo piston 4 and a small-diameter plunger 3, and is connected to a fuel oil inlet 22 formed on the side of the injector turbo day 1 via a solenoid valve section 31, which will be described in detail later. By appropriately controlling the introduction and discharge of fuel oil introduced into the servo piston chamber 5 by the solenoid valve section 31, the fuel oil in the fuel oil inlet 22 is supplied to the fuel oil filling oil passage 23. Valve 21
This high-pressure fuel oil is introduced into the oil reservoir chamber 20 through the high-pressure fuel oil passage 24 and the nozzle valve 2 is opened by the hydraulic pressure of the fuel oil. The valve is configured to inject from nozzles 19, 19, . . . . Further, a part of the fuel oil is introduced into the nozzle valve seat insertion hole 17 provided on the back pressure side of the nozzle valve 2 via the fourth hydraulic oil passage 34, and the opening pressure of the nozzle valve 2 is increased. teeth,
It is set by the hydraulic pressure in the nozzle valve seat insertion hole 17 and the spring force of the nozzle valve biasing spring 16. The leaked oil from the servo piston 4 is returned to the fuel tank 71 via the fourth discharge oil passage 30.

The solenoid valve section 31 is a hydraulic servo mechanism 3
A spool valve 7 that controls the flow of fuel oil introduced into the servo piston chamber 5 as hydraulic oil No. 3, and an active core 9 driven by the suction force of a solenoid coil 12 are arranged coaxially. ing. By being displaced in the axial direction, the spool valve 7 has two land portions 7a, 7.
b, a first hydraulic oil passage 25 that communicates the fuel oil inlet 22 and the spool chamber 8, and a second hydraulic oil passage 2 that communicates the spool chamber 8 and the servo piston chamber 5.
6 and the third hydraulic oil passage 29 that connects the spool chamber 8 and the fuel tank 71 are opened and closed as appropriate to control the flow of the hydraulic oil. That is, when the spool valve 7 is pulled upward, the first hydraulic oil passage 25 and the second hydraulic oil passage 26 communicate with each other, and the fuel oil flows from the fuel oil inlet 22 into the servo piston chamber 5.
(Fig. 1, the illustrated position; hereinafter, this valve position will be referred to as the first valve position), and conversely, if the hydraulic oil is pushed downward, the hydraulic oil second oil passage 26 and the hydraulic oil third oil passage 29 communicate with each other, and the fuel oil in the servo piston chamber 5 is discharged to the fuel tank 71 side (the valve position in this case is referred to as the second valve position).
2 and the spring force of the first spring 14 provided on the active core 9 side and the second spring 15 provided on the spool valve 7 side. That is, in this embodiment, the spring force of the first spring 14 on the active core 9 side is set larger than that of the second spring 15 on the spool valve 7 side.
When the attraction force of the solenoid coil 12 has disappeared (in other words, when the current supply to the solenoid coil 12 has been cut off), the spool valve 7 and the active core 9 are integrally connected to the spring force of the first spring 14. When the spool valve 7 is pressed downward due to the difference in the spring force of the second spring 15 and an attractive force is generated in the solenoid coil 12 (in other words, the solenoid coil 12 is energized). case), first, the active core 9 is pulled upward against the spring force of the first spring 14 by the suction force, and then the spool valve 7 is pulled up against the spring force of the first spring 14.
The spring force of the spring 15 pushes it upward and sets it to the first valve position. The stroke of the active core 9, that is, the operating stroke of the active core 9 is adjusted by setting the upward movement limit of the active core 9 using an adjusting bolt 13 provided on the upper surface 9a side of the active core 9. Further, the leaked oil from the spool valve 7 is returned to the fuel tank side from the first discharge oil passage 27 via the oil passage hole 11 provided in the active core 9 and the second discharge oil passage 28.

The intake valve device
A hydraulic valve drive device 61 is installed to open and close the intake valve 3 using hydraulic pressure.
6 is opened and closed by the spring force of a valve spring 39 and the hydraulic pressure of a hydraulic valve drive device 61. The hydraulic valve drive device 61 includes an intake valve 3 in a cylinder body 42 fixed to the cylinder head 35 side by fixing bolts 59, 59, . . .
6 in the valve opening direction by hydraulic pressure, and a solenoid valve section 63 that controls the flow of hydraulic oil introduced into the working chamber 43 of the piston 44. This solenoid valve section 63 has almost the same configuration as the solenoid valve section 31 of the injector device T, and has an active core 47 driven by the attraction force of the solenoid coil 48 and a spool valve 45 disposed coaxially. And this spool valve 45,
A second spring 5 attached to the spool valve 45 side
1 and the active core 47 side, and the two land portions 45a,
45b, the hydraulic oil inlet 52 and the piston chamber introduction oil passage 5
3 and piston chamber discharge oil passage 54 as appropriate to move the piston 44 up and down.
It is designed to open and close the valve. That is, in this embodiment, the spring force of the first spring 50 is
The spring force is set to be larger than the spring force of the spring 51, and when the solenoid coil 48 is de-energized, the spool valve 45 is pushed down by the difference in the spring force between the first spring 50 and the second spring 51, and the piston chamber is closed. The introduction oil passage 53 and the piston chamber discharge oil passage 54 are made to communicate with each other to discharge the hydraulic oil from the working chamber 43 (hereinafter, the valve position of the spool valve 45 in this case will be referred to as the first valve position), and conversely, the solenoid coil 48 is energized, its suction force pulls up the active core 47 against the spring force of the first spring 50, and the spool valve 45 is pushed upward by the spring force of the second spring 51. The hydraulic oil inlet 52 and the piston chamber introduction oil passage 53
The valve position of the spool valve 45 in this case will be referred to as the second valve position hereinafter. Note that the stroke of the active core 47 is adjusted by the screwing amount of the adjustment bolt 49. In addition, leakage oil from the spool valve 45 is drained from the first discharge oil path 56 to the active core 4.
7 through the oil passage hole 64 provided in the second discharge oil passage 55.
The leaked oil from the piston 44 is returned to the fuel tank 71 side from the third discharge oil passage 57.

Since the exhaust valve device Y has the same configuration as the intake valve device X, detailed illustration and explanation thereof will be omitted.

The electronic control device R includes a rotational phase angle sensor 6 mounted close to the flywheel 67 of the internal combustion engine 68.
6 and the signal from the rotational phase angle sensor 66 to set the energization start timing, energization cutoff timing, etc. of the solenoid coil 12 of the injector device T, the solenoid coil 48 of the intake valve device X, and the exhaust valve device Y. It has a microcomputer 65 that controls the amount and timing of fuel injection, the rotational speed of the internal combustion engine 68, and the timing of opening and closing the intake and exhaust valves.

Next, the operation of the electro-hydraulic control system for the internal combustion engine of the illustrated embodiment will be explained. When the internal combustion engine 68 is operated, first, the fuel oil in the fuel tank 71 is pressurized to an appropriate pressure by the fuel supply pump 69. A part of it passes through the first fuel supply pipe 73 to the fuel oil inlet 22 of the injector device T, and the other part passes through the second fuel supply pipe 74 as hydraulic oil to operate the intake valve device X. The oil is fed under pressure to the oil inlet 52 and the hydraulic oil inlet (not shown) of the exhaust valve device Y.

A part of the fuel oil pressure-fed to the fuel oil inlet 22 side of the injector device T flows from the fuel oil filling oil passage 23 into the plunger chamber 6 of the hydraulic servo mechanism 33 as fuel oil, and the other part flows into the plunger chamber 6 of the hydraulic servo mechanism 33. From the third hydraulic oil passage 34 to the nozzle valve seat insertion hole 1
7 and hydraulic oil from the first oil passage 25 to the servo piston chamber 5
It is divided into two parts and supplied to each of them. If the solenoid coil 12 is now energized, the active core 9 is pulled upward by the absorption force of the solenoid coil 12, and the spool valve 7 is set to the first valve position. When the spool valve 7 is set to the first valve position, the first hydraulic oil passage 25 and the second hydraulic oil passage 26
Because the fuel oil inlet 22 communicates with the hydraulic oil 1st
Hydraulic oil is introduced into the servo piston chamber 5 through the oil passage 25 and the second hydraulic oil passage 26, and the plunger 3 is moved downward together with the servo piston 4 by the hydraulic oil pressure in the servo piston chamber 5. , the fuel oil in the plunger chamber 6 is increased in pressure and the nozzles 19,1 are
The fuel is injected into the cylinder from 9... (Fuel injection stroke, Figure 1, position shown).

When the power to the solenoid coil 12 is cut off, the attraction force of the solenoid coil 12 disappears, so the active core 9 and the spool valve 7 are connected to the first spring 1.
4 and the second spring 15, the spool valve 7 is pushed downward, and the spool valve 7 is set to the second valve position. When the spool valve 7 is set to the second valve position, the second hydraulic oil passage 26 and the third hydraulic oil passage
The servo piston 4 is moved upward by the pressure of the fuel oil introduced into the plunger chamber 6 by pushing open the supply valve 21 from the fuel oil filling oil path 23, and the servo piston 4 At the same time, the hydraulic oil in the plunger chamber 5 is discharged to the fuel tank 71 side, and the plunger chamber 6 is filled with fuel oil (fuel filling process). By repeating this fuel injection stroke and fuel filling stroke, the internal combustion engine 68 is continuously operated.

The amount of fuel injected is controlled by the microcomputer 65 by adjusting the energization cutoff time of the solenoid coil 12 and changing the amount of fuel charged. That is, if the energization interruption time is increased, the amount of fuel charged increases, and the amount of fuel injection increases accordingly.

The fuel injection timing is adjusted by controlling the start timing of energization of the solenoid coil 12 based on the signal from the rotational phase angle sensor 66. For example, when performing an advance angle operation, the energization start timing is advanced.

Further, the rotational speed of the internal combustion engine 68 is controlled by changing the time interval of the energization cycle to the solenoid coil 12. For example, when increasing the rotational speed, the time interval between energization cycles is reduced.

In this injector device T, since fuel oil with low viscosity (for example, high-quality oil such as light oil or kerosene) is used as the hydraulic oil for the hydraulic servo mechanism 33, the spool valve 7 or the hydraulic servo mechanism 33
The operating resistance is small, and the fuel injection characteristics can be controlled in a responsive manner to changes in the operating state of the internal combustion engine 68 (improved responsiveness).

In addition, in the illustrated embodiment, the leaked oil from the spool valve 7 is made to flow through the oil passage hole 11 provided in the active core 9 and discharged to the fuel tank 71 side. 9. That is, the temperature rise of the solenoid coil 12 can be suppressed, and thereby the suction force characteristics of the solenoid coil 12 can be maintained stably and favorably over a long period of time. On the other hand, the solenoid coil 48 of the intake valve device X and the solenoid coil (not shown) of the exhaust valve device Y are energized or de-energized depending on the operating stroke of the internal combustion engine 68. That is, the solenoid coil 48 of the intake valve device X is energized near the end of the exhaust stroke, and de-energized at the beginning of the compression stroke. That is, the solenoid coil 48
When energized, the active core 47 is pulled upward by the suction force and the spool valve 45 is set to the second valve position, so hydraulic oil is introduced into the working chamber 43 and the piston 44 moves downward. The intake valve 36 is opened accordingly. On the other hand, when the power to the solenoid coil 48 is cut off, the spool valve 45 is set to the first valve position, and the intake valve 36 is closed by the spring force of the valve spring 39.

On the other hand, the solenoid coil of the exhaust valve device Y is energized near the end of the expansion stroke to open the exhaust valve, and is deenergized at the beginning of the suction stroke to close the exhaust valve.

Since both the intake valve device X and the exhaust valve device Y use fuel oil as the hydraulic oil for the hydraulic valve drive device 61, the operating resistance due to the viscosity of the hydraulic oil is small, as in the case of the injector device T. Accordingly, the intake valve 36 and the exhaust valve can be opened and closed with good response according to the operating state of the internal combustion engine 68, and the intake characteristics and exhaust characteristics of the internal combustion engine 68 are improved.

Furthermore, in this electro-hydraulic control device, the structure of the solenoid valve section 31 of the injector device T, the structure of the solenoid valve sections of the intake valve device X and the solenoid valve section 61, and the solenoid valve section of the exhaust valve device Y are almost the same. Each part of the injector device T, intake valve device X, and exhaust valve device Y is compatible with each other, so the number of types of parts can be reduced, and the structure can be simplified and costs can be reduced.

Next, to explain the effects of the present invention, the electro-hydraulic control device for an internal combustion engine of the present invention has hydraulic oil supplied to the hydraulic servo mechanism of the injector device and the hydraulic valve drive device of the intake valve device and the exhaust valve device. By supplying both the fuel oil and the fuel oil injected into the cylinder from the injector device from the same hydraulic source, the hydraulic source is shared, so in the case of a conventional electronic hydraulic control device with multiple hydraulic sources In comparison, there are fewer parts such as hydraulic pumps and filters,
This has the effect of simplifying the structure of the device, reducing its size and weight, and reducing its cost.

Further, the electronic hydraulic control device of the present invention uses light oil or kerosene with low viscosity as fuel oil, and a portion of this fuel oil is used in the hydraulic servo mechanism of the injector device and the valve operating mechanism of the intake valve device and the exhaust valve device. Because it is used as a hydraulic oil, the viscosity resistance of the operating parts is lower than when using high viscosity engine lubricating oil as the hydraulic oil, and the temperature of the hydraulic oil is lower due to viscosity resistance. Since the suction force characteristics of the solenoid coil do not deteriorate due to an increase in the solenoid coil, the responsiveness of the injector device, intake valve device, and exhaust valve device improves, which improves the injection characteristics and intake and exhaust characteristics of the internal combustion engine. It also has the effect of making it possible to achieve this.

[Brief explanation of the drawing]

FIG. 1 is a system diagram of an electro-hydraulic control device for an internal combustion engine according to an embodiment of the present invention. 2... Nozzle valve, 12... Solenoid coil, 31... Solenoid valve section, 32... Injector section, 33... Hydraulic servo mechanism, 36...
...Intake valve, 48...Solenoid coil, 61...
Hydraulic valve drive device, 62... Valve mechanism section, 63...
... Solenoid valve section, 65 ... Microcomputer, 68 ... Internal combustion engine, 69 ... Fuel supply pump, R ... Electronic control device, S ... Fuel oil supply device, T ... Injector device, X ... Intake valve Device, Y...Exhaust valve device.

Claims (1)

[Claims] 1. A fuel oil supply device S having a fuel supply pump 69 driven by an internal combustion engine 68, and a hydraulic servo mechanism 33 to increase the pressure of the fuel oil pumped from the fuel oil supply device S and inject it from the nozzle valve 2. Injector section 32 and the hydraulic servo mechanism 3
an injector device T having a solenoid valve section 31 that controls the flow of hydraulic oil that operates the valve 3; a valve mechanism section 62 that opens and closes the intake valve 36 by hydraulic pressure; Solenoid valve section 6 that controls the flow of hydraulic oil
3, a hydraulically driven intake valve device X including a hydraulic valve drive device 61 having a
Hydraulically driven exhaust valve device Y having almost the same configuration as
The solenoid coil 12 of the solenoid valve section 31 of the injector device T, the solenoid coil 48 of the solenoid valve section 63 of the intake valve device X and the exhaust valve device Y are controlled as appropriate according to the operating state of the internal combustion engine 68. and an electronic control device R having a microcomputer 65 for controlling a part of the fuel oil that is pressure-fed from the fuel supply pump 69 of the fuel oil supply device S to the injector section 32 side of the injector device T. The hydraulic servo mechanism 33 of T
An electro-hydraulic control system for an internal combustion engine, characterized in that it is used as hydraulic oil for a valve operating mechanism section 62 of the intake valve device X and the exhaust valve device Y.