JP3257365B2 - Sub-chamber engine with exhaust gas recirculation system - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a sub-chamber engine with an exhaust gas recirculation device.

[0002]

BACKGROUND ART Fukushitsushiki engines, particularly in pre-combustion chamber diesel engine for a vehicle, in order to reduce the NO _x is detrimental components in the exhaust gas, so as to reflux a part of exhaust gas to the intake side Exhaust recirculation device (hereinafter, sometimes E
GR device) is widely used. Normal EGR
The device extracts the exhaust gas extracted from the exhaust passage of the engine,
It is configured to be guided to an intake passage of the engine, mixed with intake air, and supplied into a cylinder. Therefore, compared with the case where exhaust gas recirculation (hereinafter, referred to as EGR in some cases) is not performed, fresh air to be sucked in is reduced by the amount of recirculated exhaust gas, and the excess air ratio is correspondingly reduced. Due to this, there is a disadvantage that smoke is easily generated. In particular, N
Emissions of O _x excess air ratio is reduced during many high load, since smoke when performing EGR is greatly deteriorated,
Sufficient NO _x reduction effect can not be performed EGR had is not trouble obtained.

In order to solve the problem of the sub-chamber engine equipped with the above-mentioned ordinary EGR device, fresh air is sucked into a cylinder in an intake stroke and an intake valve is closed, and then exhaust gas is pumped into the sub-chamber. Such a configuration is disclosed in Japanese Patent Application Laid-Open No. 4-16665.
No. 6 discloses this. In this proposed configuration, as means for pumping exhaust gas into the sub-chamber, a piston reciprocatingly driven in conjunction with the crankshaft of the engine, a cylinder in which the piston is slidably fitted, and a reed valve, respectively. A reciprocating pump device called a sub-cylinder having a suction valve and a discharge valve is provided, and pressurized exhaust gas discharged from the pump device is supplied to sub-chambers of a plurality of cylinders, respectively. There is a disadvantage that the structure becomes extremely complicated, including the piping to be made, and the manufacturing cost increases.
There were problems such as loss of engine power consumed for driving the reciprocating pump device and loud noise generated by pump operation.

[0004]

[0008] The present invention has been made in view of the above circumstances, without intake of fresh air by performing the EGR is reduced, thus substantially reducing the desired engine of the NO _x manner in all operating ranges, output, fuel consumption, etc. engine performance, and smoke performance can is carried out effectively EGR without damaging significantly, whereby it is possible to effectively reduce the NO _x in the exhaust gas structure It is a primary object to provide a simple and inexpensive sub-chamber engine. Another object of the present invention is to reduce the required driving force of a movable wall member such as a piston and a diaphragm for supplying combustion gas into a sub-chamber during a compression stroke of each cylinder of an engine, so that the output loss of the engine is small, and An object of the present invention is to provide an EGR device-equipped sub-chamber engine in which operation noise accompanying driving of members is small.

[0005]

To achieve the above object, the present invention provides a sub-chamber communicating with a main combustion chamber in a cylinder through an injection hole, and a sub-chamber connected to the sub-chamber through a communication passage. A variable volume combustion gas storage chamber with a movable wall member inside,
A valve device for controlling the communication between the auxiliary chamber and the combustion gas storage chamber is interposed said communication passage, a first actuator for opening and closing the valve device, to the movable wall member of the combustion gas reservoir A second actuator operatively connected to increase or decrease the volume of the combustion gas storage chamber, and controlling the first and second actuators in accordance with an operating state of the engine so that the sub-chamber within the sub-chamber during a desired period of the expansion stroke is controlled. the exhaust gas causes to flow into the combustion gas reservoir chamber through the communicating passage, the desired period of the compression stroke the volume of the combustion gas reservoir
It reduces proposed pre-combustion chamber engine with exhaust gas recirculation apparatus characterized by comprising a control device operative to supply the combustion gas in the combustion gas storage chamber to said auxiliary combustion chamber via said communication passage Is what you do.

According to a second aspect of the present invention, the movable wall member is provided.
Is slidable into the combustion gas storage chamber, which is cylindrical.
A piston fitted to the actuator, wherein the actuator is
When energized by the control device, the piston
Drive to reduce the volume of the combustion gas storage chamber
The solenoid and the above controller deenergize the solenoid
When the movable wall member is driven in the opposite direction,
Return spring that increases the volume of the combustion gas storage chamber
Characterized by being an electromagnetic actuator having
You. The invention according to claim 3 is that the control device controls the first and second actuators such that the exhaust gas in the sub-chamber is supplied to the combustion gas storage chamber in the middle stage of the expansion stroke. Features.

According to a fourth aspect of the present invention, the control device comprises:
The first actuator is controlled in accordance with the load and the number of revolutions of the engine to change a valve opening timing in an expansion stroke of the valve device. Furthermore, the invention of claim 5 is characterized in that the pressure at the end of the inflow of the combustion gas flowing from the sub-chamber into the combustion gas storage chamber during the expansion stroke increases the pressure of the combustion gas in the combustion gas storage chamber into the sub-chamber during the compression stroke. The pressure is set higher than the in-cylinder pressure at the end of the supply. Further, according to the invention of claim 6 , when the engine is operated at high speed and high load, the valve device is opened near the compression top dead center to temporarily communicate the sub-chamber with the combustion gas storage chamber, thereby substantially reducing the combustion chamber volume. It is characterized in that it is configured to increase the number.

In carrying out the present invention, the valve device is
The communication path is closed by the first actuator.
Closed position to cut off communication between the sub-chamber and combustion gas storage chamber
And opening the communication passage, the sub-chamber and the combustion gas storage chamber
That is selectively driven to any of the open positions
It is preferably a tally valve or a slide valve,
Further, the second actuator is controlled by the control device.
When energized, the movable wall member is driven in one direction to
A solenoid that reduces the volume of the combustion gas reservoir;
When the solenoid is deenergized by the controller,
The movable wall member is driven in the opposite direction to move the combustion gas storage chamber.
Electromagnetic with return spring to increase volume
An actuator is desirable. Furthermore, the present invention
In the implementation of the above, the movable wall member has a cylindrical shape.
Piston slidably fitted in the combustion gas storage chamber
Is preferred. However, the movable wall member is
The gas storage chamber is installed in the gas storage chamber.
Increase the volume of the storage chamber and displace it in the opposite direction.
A diaphragm that reduces the volume of the diaphragm may be used.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be specifically described below with reference to the accompanying drawings. First, in the main part configuration diagram of FIG. 1, reference numeral 10 denotes a crankcase showing only a part thereof, and 12 denotes a cylinder liner formed in the crankcase 10 or fitted in the crankcase 10. The piston is slidably fitted to the cylinder 14. The top surface of the piston 12 cooperates with the lower surface of a cylinder head 18 mounted on the crankcase 10 via a head gasket 16 to form a cylinder 14.
A recess 20 forming a main combustion chamber therein is provided.

The cylinder head 18 is provided with a bell-shaped sub-chamber or swirl chamber 22 in this embodiment. The sub-chamber 22 is provided with a main combustion through an injection hole 26 obliquely provided in a base 24. Communicate with the room. A fuel injection valve 28 is disposed in the upper part of the dome shape of the sub chamber 22 at an angle to the axis of the sub chamber substantially parallel to the axis of the cylinder 14, and is adjacent to the fuel injection valve 28. The glow plug 30 is disposed.

A cylinder-shaped combustion gas storage chamber 32 is provided in the cylinder head 18 on the side of the dome-shaped top of the sub-chamber 22. The combustion gas storage chamber 32, the sub-chamber top, Are connected by a communication path 34. In the communication passage 34, the combustion gas storage chamber 32
A valve device 36 for controlling the communication between the fuel cell and the sub-chamber 22 is provided. In this embodiment, the valve device 36 is shown as a rotary valve including a valve body 38 having a cylindrical shape as a whole, and a valve hole 40 projecting diametrically in the valve body 38, The rotary valve 36 is a first actuator 4 composed of an appropriate rotary or swing actuator.
By means of 2, it is swiveled around a valve axis extending in a direction perpendicular to the plane of the drawing of FIG.

A movable wall member 4 is provided in the combustion gas storage chamber 32.
The movable wall member is shown as a piston slidably fitted in the combustion gas storage chamber in the illustrated embodiment. An armature 46 is fixed to the piston 44, and the armature 46 cooperates with a solenoid 48 and a return spring 50. When the solenoid 48 is deenergized, the piston 44 connected to the armature 46 is displaced to the right position shown in FIG. 1 by the return spring 50, and the combustion gas storage chamber 32 has the maximum internal volume. . When the solenoid 48 is energized, the armature 46 compresses the return spring 50 and moves to the left,
The piston 44 is displaced to the left position indicated by the one-dot chain line in the figure, and the combustion gas storage chamber 32 is in the state of the minimum internal volume.
The solenoid 48, the armature 46 and the return spring 50 constitute a second electromagnetic actuator 52 for driving a movable wall member or a piston 44. The combustion gas storage chamber 32 is formed by the movable wall member 44.
A variable volume chamber whose inner volume is controlled is formed.

The first actuator 42 and the second actuator 52 are controlled by a control unit or control device 54 including a microcomputer. The control unit or control device 54 includes a temperature sensor 56 for detecting the temperature of the cooling water of the engine. Cooling water temperature information T
w, rotational speed information Ne of a rotational speed sensor 58 for detecting the rotational speed of the engine, and a fuel supply amount of a fuel injection pump (not shown) for supplying fuel to the fuel injection valve 28 of each cylinder of the engine. Fuel supply amount information Lp of a lever position sensor 60 for detecting the position of the control lever
And the crank angle information θc of the crank angle sensor 62 for detecting the rotation angle of the crank shaft of the engine, that is, the crank angle, and the like, and supplies a drive output to the first actuator 42 and the second actuator 52 of each cylinder.

The operation of the sub-chamber engine with the EGR device will be briefly described with reference to the schematic configuration diagram of FIG. 1 and the in-cylinder pressure diagram of FIG. Curve P shown by the solid line in FIG. 2 ₀ indicates the pressure in the cylinder of the not provided with a combustion gas reservoir 32 normal pre-combustion chamber engine (cylinder pressure). In the above conventional engine, in the intake stroke of the piston 12 as indicated by the solid line P ₀ is lowered in the cylinder 14, the intake from the intake valve Vi open is sucked in the subsequent compression stroke, the intake valve Vi There intake air is compressed by the piston 12 moves upward after closing crank angle theta _1. The compressed intake air flows into the sub-chamber 22 from the injection hole 26 to form a vertical swirling flow. At the end of the compression stroke, fuel is injected from the fuel injection valve 28 as shown by the dotted line in FIG. 1, and the fuel spray mixes with the compressed and high-temperature intake air and ignites. Premix combustion is performed.

The combustion gas in the sub-chamber 22 flows from the injection hole 26 into the main combustion chamber in the cylinder 14 to perform diffusion combustion. Piston 12-cylinder pressure during the expansion stroke or combustion stroke exceeds the compression top dead center is lowered as shown, at the end of the expansion stroke, the exhaust is made the exhaust valve Ve is opened in the crank angle theta _4, exhaust At the end of the stroke, the intake valve Vi is opened, and the above cycle is repeated thereafter.

In the sub-chamber engine according to the present invention, in the middle stage of the expansion stroke, for example, at the crank angle θa in FIG.
The valve device 36 that has been closed during the compression stroke is released by the control unit or the control device 54 to the first actuator 4.
By being driven, 2 is released as shown in FIG. At this time, since the solenoid 48 of the second actuator 52 that has been energized in the previous stroke is deenergized,
The piston 44 located at the left position is the return spring 5
The elastic gas is pushed in the right position, that is, the direction in which the volume of the combustion gas storage chamber 32 increases, and at the same time, by opening the valve device 36, the combustion gas in the sub chamber 22 passes through the communication passage 34. The piston 44 flows into the combustion gas storage chamber 32 to move the piston 44 to the right position shown by the solid line in the figure.
Next, after a time set by the control unit or the control device 54 according to the operating state of the engine, that is, at a time point indicated by the crank angle θb in FIG. 2, the first actuator 42 is driven, and the valve device 36 The communication path 34 is closed by being rotated approximately 90 ° from the communication position in FIG. Due to the inflow of the combustion gas from the sub-chamber 22 into the combustion gas storage chamber 32, the in-cylinder pressure Pc slightly decreases as shown by a dotted line in FIG.

The subsequent exhaust and intake strokes are substantially similar to previous engines. Next, on the crank angle theta ₁ enters the compression stroke the intake valve Vi is closed, or after closing (FIG. 3 former is illustrated), by a control unit or controller 54, the first actuator 4
2 is driven to open the valve device 36, and the solenoid 48 of the second actuator 52 is energized substantially simultaneously. By the urging of the solenoid 48, the armature 46 compresses the return spring 50 and is displaced leftward in FIG. 1, and the piston 44 transfers the combustion gas filled in the combustion gas storage chamber 32 to the auxiliary gas through the communication passage 34. It is fed into the chamber 22 and is displaced to the left position indicated by the dashed line in the figure. At a crank angle theta ₂ which the piston 44 reaches the left position, by a control unit or controller 54, is closed first actuator 42 is driven valve 36 again. As the combustion gas in the combustion gas storage chamber 30 is supplied into the sub chamber 22 in the compression stroke, the in-cylinder pressure Pc becomes
It rises slightly as shown by the dotted line in FIG.

The above control unit or control device 5
The operation modes of FIG. 4 are summarized in the flowchart of FIG. When the program starts, initialization at step S ₁ is performed, the valve device 36 is closed, the piston 44 forming the movable wall member is set to the right position B by deenergizing the solenoid 48 of the second actuator 52.
Next, in step S _2, the crank angle θc is read, in step S _3, the crank angle θc is, whether between the crank angle theta ₁ and theta ₂ are examined in the compression stroke.

Step S ₃ . If YES in step proceeds to S _4, the first actuator 42 is driven valve 36 is opened as described above, at the same time the second actuator 52 is energized piston 44 driving the left position A Then, the combustion gas in the combustion gas storage chamber 32 is supplied to the sub chamber 22. When the crank angle θc is NO through the crank angle theta _2, in step S _5, whether the crank angle θc enters between the crank angle theta ₃ and theta ₄ in the expansion stroke, it is determined. Crank angle θc
However, since it is naturally determined to be NO until θ ₃ exceeds θ ₂ , the step proceeds to S ₆ , the first actuator 42 is driven, and the valve device 36 is closed.

[0020] If it is determined as YES in step SS _5, the process proceeds to step _{S 7,} the control lever position Lp and the engine speed Ne of the fuel injection pump which represents the engine load is read, followed by, in step _{S 8,} the engine Starting crank angle θa for setting the amount of exhaust gas flowing into the combustion gas storage chamber 32 according to the operating state of the engine
(Opening timing of valve device 36) and inflow end crank angle θb
(Close timing of the valve device 36) is set. That is, when the movable wall member or the piston 44 shown in FIG. 1 is displaced to the right stroke end, the combustion gas storage chamber 32 has such a volume that the maximum EGR amount required by the engine is obtained. However, an appropriate EGR amount is determined by the opening / closing crank angle θ of the valve device 36 in accordance with the engine load Lp and the rotation speed Ne.
a and θb.

Next, in step S _9, the crank angle θc is checked whether equal to or greater than the θa is. When the NO is not reached yet .theta.a, it is maintained in the course valve 36 closed, when the YES became more .theta.a, the process proceeds to step S _10, with the valve device 36 is opened, the second actuator 52 Deactivated. Therefore, the piston 44
Moves rightward due to the pressure of the combustion gas flowing from the sub chamber 22 and the spring force of the return spring 50. Step S ₁₁
In step S, if it is determined that the crank angle θc has reached θb set according to the operating state of the engine,
_{At 12} , the valve device 36 is operated by the first actuator 42.
Is closed, and a set amount of exhaust gas is stored in the combustion gas storage chamber 32, and the program returns.

The pressure of the combustion gas stored in the combustion gas storage chamber 32 is substantially determined by the pressure of the combustion gas in the sub-chamber 22 at the inflow end timing θb, even if some inflow inertia is considered. In the in-cylinder pressure diagram of FIG. 2, the end timing of the combustion gas recirculation in the stroke is such that the supply of the combustion gas is terminated at a time when the in-cylinder pressure during the compression stroke is lower than the in-cylinder pressure at the crank angle θb. it is preferable to set the crank angle theta _2, which makes it possible to reduce the required pumping capacity to the second actuator 52, it becomes possible to recirculate the combustion gases with a small actuator.

According to the configuration of the present invention, the combustion gas stored in the combustion gas storage chamber 32 from the sub chamber 22 in the middle stage of the expansion stroke is returned to the sub chamber 22 after the intake valve Vi is closed in the compression stroke. Therefore, the intake of fresh air from the engine does not decrease, and the problem of smoke generation due to the reduction of the excess air ratio can be effectively eliminated. In addition, since EGR is performed only in the sub-chamber 22, premix combustion is performed. Is suppressed, NO _x is reduced, and diffusion combustion in the main combustion chamber is promoted, so that generation of smoke is also suppressed from this point. As a result of the above, the operating range of the engine capable of performing the EGR is expanded, and in substantially any operating state of the engine,
While effectively suppressing the generation of smoke, will be able to carry out the appropriate amount of EGR at the right time, there is an advantage that reduction of the NO _x is extremely effectively achieved.

Further, according to the structure of the present invention, a sub-cylinder for pumping exhaust gas, that is, an extremely complicated and expensive reciprocating pump device and accompanying piping and joints are required as in the above-mentioned proposed device. However, the combustion gas storage chamber 32 having a small volume of about 0.5 to 1.0% with respect to the exhaust capacity of the cylinder 14 and a small movable wall member or a piston 44 housed in the storage chamber. Since all the components, such as the small-capacity second actuator 52 for driving the movable wall member and the valve device 36 such as a small rotary valve, are composed of a simple, compact and lightweight member, the manufacturing cost is low and the operation is low. It has the advantages of low noise and low power loss of the engine consumed for driving the movable wall member, and can be disposed inside or adjacent to the cylinder head 18 having a complicated structure. There is also over the scan advantage.

Further, the combustion gas is stored in the combustion gas storage chamber 32 in the middle stage of the expansion stroke, and the auxiliary chamber 22 is stored in the compression stroke.
In addition to reflux, in the event a large amount high speed and high load operation of NO _x, in-cylinder pressure diagram of Figure 2, the crank angle theta ₃ near the compression top dead center, the temporarily open the valve device 36 When the second actuator 52 is deenergized to allow the combustion gas to flow from the sub-chamber 22 into the combustion gas storage chamber 32, the combustion chamber volume of the sub-chamber 22 temporarily increases, and the combustion temperature decreases. However, this has the added advantage of further reducing NOx _emissions . As indicated by a dotted line near the compression top dead center in the in-cylinder pressure diagram of FIG. 2, the temporary opening of the valve device 36 and the second actuator 52
, A slight pressure drop occurs at the peak portion of the in-cylinder pressure diagram.

In the above embodiment, the valve device 36 is exemplified as a rotary valve suitable for installation in a narrow space. However, as shown in FIG. The valve body 36 'is provided, and the valve body 3' is provided.
A slide valve that opens and closes the communication passage 34 by driving the 6 'in the direction of the arrow (the direction perpendicular to the plane of FIG. 1) by the first actuator 42 including a cam or other driving means may be used, and furthermore, it is allowed in the arrangement space. For example, a poet valve or the like may be used. Although a piston is illustrated as the movable wall member 44, a diaphragm, a bellows, or the like may be used instead of the piston. In addition, as the second actuator 52, an electromagnetic actuator having a simple structure and easy arrangement is exemplified, but an air cylinder, a hydraulic cylinder, or another appropriate actuator can be used instead. Note also, the flow chart of FIG. 4 described above can also be added appropriately modified, for example, the crank angle theta ₁ at step S ₃ and S _5, theta _2,
The theta ₃ and through? _4, it can be changed according to the operating state of the respective engines, loading this case the engine load in step S ₇ Lp and the engine speed Ne, the step S
It is preferably performed simultaneously with reading of the crank angle θc of ₂ .

[0027]

As described above, the sub-chamber engine with the exhaust gas recirculation device according to the present invention has a sub-chamber communicating with the main combustion chamber in the cylinder through the injection hole, and a communication passage in the sub-chamber. a combustion gas storage chamber of variable volume equipped with connected movable wall member therein via a valve device for controlling the communication between is interposed aforementioned connecting channel the auxiliary chamber and the combustion gas reservoir, the A first actuator for opening and closing the valve device, and a combustion gas storage chamber.
A second actuator operatively connected to the movable wall member to increase or decrease the volume of the combustion gas storage chamber; and controlling the first and second actuators in accordance with an operation state of the engine to thereby provide a desired period of an expansion stroke. the sub chamber of the exhaust gas together to flow into the said combustion gas reservoir chamber through the communicating passage, the desired period of the compression stroke of the combustion gas reservoir volume to
Reduce the product characterized by comprising the combustion gas reservoir chamber of said combustion gas and a control device operable to supply to the secondary chamber through the communication passage, N in the exhaust gas
EGR can be performed in substantially all operating regions of the engine in which Ox needs to be reduced without significantly impairing engine performance such as output fuel efficiency and smoke performance, thereby effectively reducing NOx. It is possible to provide an inexpensive sub-chamber type engine with a simple structure, and furthermore, it is possible to provide an engine of this kind which consumes less power of the engine for operating the EGR device and has low operation noise. There is.

Further , in the present invention, the control device includes:
The first actuator according to the engine load and the number of revolutions
The valve opening timing during the expansion stroke of the valve device.
By adjusting the engine operating conditions.
A small amount of EGR can be performed, and NO in exhaust gas
_x can be effectively reduced and smoke is effectively generated
There is an advantage that can be suppressed. Further, the control device may be
In the middle stage of the stretching process, the exhaust gas in the sub-chamber
The first and second actuators
The engine output, almost sacrifice engine power.
Exhaust gas into the storage chamber
There are advantages that can be. Also, during the expansion stroke,
End of combustion gas flowing into the combustion gas storage chamber from the sub chamber
At the end of the combustion gas storage chamber during the compression stroke.
Pressure at the end of the supply of combustion gas into the subchamber
High by being set Ri, the actual required reduction of the NO _x
Smoke in qualitatively all engine operating conditions
Effective EGR without significant performance degradation
There is an advantage that the exhaust gas performance can be improved.
Furthermore, during high-speed and high-load operation of the engine, compression
Open the valve device near the point and open the sub chamber and combustion gas storage chamber.
To temporarily increase the volume of the combustion chamber.
With the arrangements to increase, the occurrence of the NO _x
The effect of EGR and the
An effect that can further suppress the generation of the NO _x I cooperation with.

[0029] In carrying out the present invention, the valve device
However, the communication path is closed by the first actuator.
Shut off to shut off the communication between the sub chamber and the combustion gas storage chamber.
Position and open the communication passage to open the sub-chamber and combustion gas storage
Selectively driven to any of the open positions to communicate with the chamber
By using a rotary valve or a slide valve,
The valve arrangement in the narrow space of the cylinder head
Has the additional advantage of being easier,
When the eta is energized by the control device,
The moving wall member is driven in one direction to increase the volume of the combustion gas storage chamber.
And a solenoid that reduces the
When the solenoid is deenergized, move the movable wall member in the opposite direction.
Litter for driving to increase the volume of the combustion gas storage chamber
With an electromagnetic actuator having a spring
By doing so, it is compact, lightweight, inexpensive and has low operating noise.
There are additional advantages that can provide a smaller EGR device. further
Further, the movable wall member has a cylindrical combustion gas storage.
It consists of a piston slidably fitted in the reservoir.
Alternatively, the movable wall member is provided in the combustion gas storage chamber.
And the capacity of the storage chamber is
And increase the volume of the reservoir by displacement in the opposite direction.
By being constituted by a decreasing diaphragm,
The above-mentioned second actuator is small and lightweight, inside the cylinder head.
Additional space that can be placed in or around
There is a point.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram showing one embodiment of the present invention.

FIG. 2 is a diagram showing a comparison between the in-cylinder pressure of a normal sub-chamber engine and the in-cylinder pressure of a sub-chamber engine according to the present invention.

FIG. 3 is a partial cross-sectional view showing a modification of the valve device 36 in the engine shown in FIG.

FIG. 4 is a flowchart showing an operation mode of a control unit or a control device in FIG. 1;

[Explanation of symbols]

10 ... Crankcase, 12 ... Piston, 14 ... Cylinder, 18 ... Cylinder head, 22 ... Sub chamber, 24 ... Base,
26 injection hole, 28 fuel injection valve, 32 combustion gas storage chamber, 34 communication path, 36 valve device, 42 first actuator, 44 movable wall member (piston), 46 armature, 48 solenoid , 50 ... return spring,
52: second actuator, 54: control unit or control device.

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ identification code FI F02B 19/08 F02B 19/08 Z (58) Investigated field (Int.Cl. ⁷ , DB name) F02M 25/07 580 F02M 25 / 07 570 F02B 17/00 F02B 19/08

Claims (6)

(57) [Claims] 1. A variable-volume combustion gas storage chamber connected to a main combustion chamber in a cylinder via an injection hole and connected to the sub-chamber through a communication passage and having a movable wall member therein. When,
A valve device for controlling the communication between the auxiliary chamber and the combustion gas storage chamber is interposed said communication passage, a first actuator for opening and closing the valve device, to the movable wall member of the combustion gas reservoir A second actuator operatively connected to increase or decrease the volume of the combustion gas storage chamber, and controlling the first and second actuators in accordance with an operating state of the engine so that the sub-chamber within the sub-chamber during a desired period of the expansion stroke is controlled. the exhaust gas causes to flow into the combustion gas reservoir chamber through the communicating passage, the desired period of the compression stroke the volume of the combustion gas reservoir
Reduced so by the combustion gas reservoir chamber of pre-combustion chamber engine with exhaust gas recirculation system of the combustion gases, characterized by comprising a control device operable to supply to the secondary chamber through the communication passage. 2. The movable wall member has a cylindrical shape.
A piston slidably fitted in the combustion gas storage chamber
Yes, the actuator is energized by the controller
When the piston is driven in one direction, the combustion
Solenoid for reducing the volume of a gas storage chamber and the above control
When the solenoid is deenergized by the device, the movable wall
Drive the members in the opposite direction to increase the volume of the combustion gas storage chamber.
Electromagnetic actuator with increased return spring
The sub-chamber engine with an exhaust gas recirculation device according to claim 1, wherein the engine is a heater. 3. The control device controls the first and second actuators such that exhaust gas in the sub-chamber is supplied to a combustion gas storage chamber in a middle stage of an expansion stroke. A sub-chamber engine with an exhaust gas recirculation device according to claim 1. 4. The control device according to claim 1 , wherein the load and the rotation of the engine are controlled.
Controlling the first actuator according to the number of turns,
Specially, it changes the valve opening timing in the expansion stroke of the device.
A sub-chamber engine with an exhaust gas recirculation device according to claim 1.
N. 5. A combustion gas storage from said sub-chamber during an expansion stroke.
The pressure at the end of the inflow of the combustion gas flowing into the chamber is the compression stroke.
At the time, the combustion gas in the combustion gas storage chamber is
That the pressure was set higher than the in-cylinder pressure at the end of supply.
The sub-chamber engine with an exhaust gas recirculation device according to claim 1.
N. 6. When the engine is operated at high speed under high load, the compression
Open the valve device near the dead center and open the sub chamber and combustion gas storage chamber.
To temporarily reduce the volume of the combustion chamber
2. The method according to claim 1, wherein the number of the occupants is increased.
The sub-chamber engine with the exhaust gas recirculation device according to the above.