JPH09296740A - Exhaust gas recirculation equipment for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To optimally control an exhaust gas recirculation(EGR) ratio according to running conditions of an internal combustion engine having an EGR equipment. SOLUTION: There are provided a master piston 2a for engine braking, which is operated by a rocker arm operated by a pushrod 1a in a different cylinder, as well as a master piston 2b for exhaust gas recirculation, which is operated by a rocker arm operated to open an exhaust valve 8 in its suction stroke by a pushrod 1b in the different cylinder and generates a pressure on oil supplied in an oil passage 5. An oil passage selector valve 11 is provided for selectively switching oil pressures generated by the engine brake master piston 2a and exhaust gas recirculation master piston 2b to each other with respect to the oil passage 5, and a cylinder 20 for changing the volume of the oil passage according to running conditions of an engine and a piston 20 which is displaced in the cylinder 20 by an actuator 22 are provided in the oil passage 5, to thereby vary the lift level of the exhaust valve 8 depending on the displacement of the piston 21.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an exhaust gas recirculation system for an internal combustion engine, which makes it possible to control an optimum EGR rate according to the operating condition of the engine.

[0002]

2. Description of the Related Art The applicant of the present application has filed a patent application 5-2 for an internal EGR system in which an exhaust gas discharged from a cylinder is sucked into the cylinder by utilizing a compression engine braking device.
It is provided by No. 11050. Its structure and operation are as follows.

In FIG. 16, 5 is an oil passage through which oil is supplied from a rocker shaft bracket (not shown) through a solenoid valve 3 and a control valve 4. 6 is an exhaust valve 8 of the cylinder 7 due to the pressure generated in the oil passage 5.
Is a slave piston 6 that opens. Reference numeral 10 denotes an exhaust brake valve.

1a is an inlet push rod of another cylinder, and 1b is an exhaust push rod of another cylinder. Reference numeral 2a is an engine braking master piston operated by a rocker arm operated by the inlet push rod 1a, and 2b is an exhaust gas recirculation master piston operated by a rocker arm operated by the exhaust push rod 1a. The engine brake master piston 2a and the exhaust gas recirculation master piston 2b generate pressure in the oil supplied to the oil passage 5 of the cylinder 7.

Reference numeral 11 is an oil passage switching valve for selectively switching the hydraulic pressure generated by the engine braking master piston 2a and the exhaust gas recirculation master piston 2b to the oil passage 5. The oil passage switching valve 11 includes a spool 12a for connecting and disconnecting the oil passage 5a on the engine braking master piston 2a side and the oil passage 5, an oil passage 5b on the exhaust gas recirculation master piston 2b side, and the oil passage 5b. The spool 12b that connects and disconnects with the passage 5 and the piston portion 12
It is composed of a spool valve shaft composed of c and c.

The switching operation mechanism of the oil passage switching valve 11 is
A spring 14 is provided at one end of the spool valve shaft, and a chamber 15 formed in front of the piston portion 12c at the other end is connected to a pressure source via an electromagnetic switching valve 16 to switch the electromagnetic switching valve 16. Thus, the spool valve is axially moved to open and close the oil passages 5a and 5b. 13a, 1
3b is a discharge passage.

FIG. 17 shows an example of the related arrangement of the above devices in an in-line 6-cylinder engine. The first cylinder # 1
(7) The opening control of the exhaust valve 8 is performed by the inlet push rod 1a and the exhaust push rod 1 of the second cylinder # 2.
b is responsible for controlling the opening of the exhaust valve 8 of the second cylinder # 2, and the inlet push rod 1a and the exhaust push rod 1b of the third cylinder # 3 are responsible for controlling the opening of the exhaust valve 8 of the third cylinder 3. The # 1 inlet push rod 1a and the exhaust push rod 1b are responsible.

The operation of the above device is shown in FIG. 16 and FIG. 16 by the example in which the opening control of the exhaust valve 8 of the first cylinder # 1 (7) is handled by the inlet push rod 1a and the exhaust push rod 1b of the second cylinder # 2. This will be described with reference to FIG. First, in the engine brake operation, the oil passage 5b on the exhaust gas recirculation master piston 2b side is closed, and the oil passage switching valve 11 is switched so that the oil passage 5a on the engine brake master piston 2a side and the oil passage 5 communicate with each other.

In this state, the master piston 2a for engine braking is operated by the inlet push rod 1a of the second cylinder # 2 in the intake stroke, and is supplied from the rocker shaft bracket to the oil passage 5 through the solenoid valve 3 and the control valve 4. A pressure is generated in the generated oil, and the generated hydraulic pressure opens the exhaust valve 8 of the cylinder 7 (first cylinder # 1) in the expansion stroke through the slave piston 6 to release compressed air from the exhaust port 9 and Eliminates the generation of pushing force and effectively utilizes the braking force.

The internal EGR closes the oil passage 5a on the engine braking master piston 2a side, and the oil passage switching valve 11 is switched so that the oil passage 5b on the exhaust gas recirculation master piston 2b side and the oil passage 5 communicate with each other. .

In this state, the exhaust gas recirculation master piston 2b is operated by the exhaust push rod 1b of the second cylinder # 2 in the exhaust stroke to pass from the rocker shaft bracket to the oil passage 5 through the solenoid valve 3 and the control valve 4. A pressure is generated in the supplied oil, and the generated hydraulic pressure causes the slave piston 6 to open the exhaust valve 8 of the cylinder 7 (first cylinder # 1) at the end of the intake stroke.

As a result, since the internal pressure of the exhaust pipe of the second cylinder # 2 is high during the exhaust stroke, part of the exhaust gas of the second cylinder # 2 is transferred to the cylinder 7 (first cylinder # 1) due to the pressure difference. It backflows to perform internal EGR action, reducing NOx and improving starting white smoke. This internal EGR action is effective in a turbo intercooler engine in which the exhaust pressure sharply increases during exhaust.

The operation stroke of the above-described device in an in-line 6-cylinder engine will be described with reference to FIG. The valve lifts are shown in the order of ignition # 1, # 4, # 2, # 6, # 3, # 5. The exhaust valve of the first cylinder # 1 is controlled by the exhaust push rod of the second cylinder # 2, and the exhaust valve of the first cylinder # 1 is opened near the bottom dead center (BDC) of the first cylinder # 1. Then, exhaust gas recirculation (EGR) is performed.

[0014]

The engine brake and the exhaust gas recirculation device are of a type in which the exhaust valve is pushed directly below by the exhaust cam or the hydraulic pressure is generated by the exhaust or exhaust cam to push it down. Basically, the valve opening timing and period could not be controlled, and the EGR rate could not be controlled. In addition, other internal EGR (Japanese Patent Laid-Open No.
3-40115), the EGR rate could not be controlled even in the internal combustion engine with an external EGR device.

An object of the present invention is to solve the above-mentioned conventional problems and to optimize the EGR in accordance with the operating condition of the engine.
To provide an exhaust gas recirculation device for an internal combustion engine capable of controlling the rate.

[0016]

SUMMARY OF THE INVENTION In order to achieve the above object, the characteristic feature of the present invention is that the master piston is actuated by the rocker arm actuated by the push rod of another cylinder when the engine brake is actuated, and the oil passage Pressure is generated in the oil that is being supplied to the engine, and the generated hydraulic pressure opens the exhaust valve of the engine cylinder near the compression top dead center via the slave piston to allow compressed air to escape from the exhaust port. In addition to the engine brake master piston that is operated by the operating rocker arm, the rocker arm that is operated by the push rod of another cylinder to open the exhaust valve in the intake stroke operates to pressurize the oil supplied to the oil passage. A master piston for exhaust gas recirculation that generates In the engine brake and exhaust gas recirculation device of an internal combustion engine provided with an oil passage switching valve for selectively switching the hydraulic pressure generated by the piston and the exhaust gas recirculation master piston to the oil passage, the operating condition of the engine in the oil passage A cylinder that changes the volume of the oil passage according to the above, and a piston that is displaced in the cylinder by an actuator are provided, the lift amount of the exhaust valve is made variable based on the displacement of the piston, and the exhaust gas recirculation rate is set to the engine. It is characterized in that it is optimally controlled in accordance with the driving situation of.

Further, when the engine brake is operated, the master piston is operated by the rocker arm operated by the push rod of the other cylinder to generate a pressure in the oil supplied to the oil passage, and the generated oil pressure causes the slave piston to transmit the oil. Open the exhaust valve of the engine cylinder near the compression top dead center to let compressed air escape from the exhaust port,
An engine brake master piston operated by a rocker arm operated by the push rod and an exhaust gas recirculation oil passage are provided, and a hydraulic pressure generated by the engine brake master piston and the exhaust gas recirculation oil passage is changed to the exhaust gas. In an engine brake and an exhaust gas recirculation device for an internal combustion engine provided with an oil passage switching valve that selectively switches to a recirculation oil passage, the oil pressure in the oil passage is adjusted in the exhaust gas recirculation oil passage in accordance with the operating condition of the engine. A hydraulic pressure generating means for controlling the exhaust valve is connected, the lift amount of the exhaust valve is variable based on the operating condition of the engine, and the exhaust gas recirculation rate is optimally controlled according to the operating condition of the engine. It is a feature.

Further, the hydraulic pressure generating means connects the accumulator for accumulating the hydraulic pressure generated by the hydraulic pressure generating pump device driven by the engine and the exhaust gas recirculation oil passage via a control valve.

Further, the camshaft is provided with a first exhaust cam for opening the exhaust valve in the exhaust stroke and a double-peak cam for the second exhaust cam for opening the exhaust valve for a certain period during the intake stroke. A feature is that a part of the exhaust gas is introduced into the cylinder due to the pressure difference between the intake and the exhaust while the second exhaust cam simultaneously opens the exhaust valve.

A supercharger comprising a compressor rotated by an exhaust turbine, a wastegate valve arranged in an exhaust bypass passage communicating an inlet and an outlet of the exhaust turbine, the compressor and an intake pipe of the engine. And an inertial supercharging device having an inertial supercharging control valve communicating with E
In an internal combustion engine including a GR device, at least one of the wastegate valve and the inertial supercharging control valve is controlled according to an operating condition of the engine, and the intake pressure by the inertial supercharging device and the wastegate valve are controlled. Thus, the exhaust pulse is changed to control the exhaust gas recirculation rate optimally according to the operating condition of the engine.

Further, a supercharger including an compressor rotated by an exhaust turbine having a variable nozzle and an EG
In an internal combustion engine equipped with an R device, the variable nozzle of the exhaust turbine is controlled according to the operating condition of the engine to change the supply pressure and the exhaust pulse, and the exhaust gas recirculation rate is adjusted to the operating condition of the engine. It is characterized by the fact that it is controlled optimally.

Further, in an internal combustion engine having an EGR device and a supercharger comprising a compressor with a variable nozzle rotated by an exhaust turbine, the variable nozzle of the compressor is controlled according to the operating condition of the engine to supply air. It is characterized in that the pressure and the exhaust pulse are changed to optimally control the exhaust gas recirculation rate according to the operating condition of the engine.

Further, in an internal combustion engine provided with an EGR device and a supercharger consisting of a compressor with a variable nozzle rotated by an exhaust turbine provided with a variable nozzle,
The variable nozzle of the exhaust turbine and the variable nozzle of the compressor are controlled according to the operating condition of the engine to change the supply pressure and the exhaust pulse, and the exhaust gas recirculation rate is optimally controlled according to the operating condition of the engine. It is characterized by doing so.

An inertia supercharging device having an inertia supercharging control valve for communicating the compressor with an intake pipe of the engine is provided, and the variable nozzle of the exhaust turbine, the variable nozzle of the compressor and the inertia supercharging control valve are provided. At least one
The exhaust gas recirculation rate is optimally controlled according to the operating condition of the engine by controlling the intake gas pressure and the exhaust pulse according to the operating condition of the engine.

Furthermore, an internal combustion engine equipped with a supercharger consisting of a compressor rotated by an exhaust turbine, a wastegate valve arranged in an exhaust bypass passage communicating an inlet and an outlet of the exhaust turbine, and an EGR device. In the above, a partition wall is provided in the center of the exhaust manifold, a butterfly valve is arranged to be openable and closable on this partition wall, and by opening and closing the butterfly valve, the exhaust gas recirculation rate is optimized according to the operating condition of the engine. It is characterized by being controlled.

The operating condition of the engine is controlled by a computer on the basis of detection signals of engine speed, load and water temperature.

[0027]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. Since the basic structure is the same as that of the conventional mechanism shown in FIG. 16, the structure of the main part obtained by improving this conventional mechanism will be described. With respect to claim 1, as shown in FIG. 1, a cylinder 20 is provided in the oil passage 5 in communication with the oil passage 5, and a piston 21 that is displaced by an actuator 22 is provided in the cylinder 20. The rotation speed signal A, the load signal B, and the water temperature signal C are input to the computer 23 for control according to the operating condition of the engine, and the displacement of the piston 21 changes the volume of the oil passage 5.

With the above structure, when the lift amount of the exhaust valve 8 during EGR is maximized, the advance amount of the piston 21 is maximized, and when the lift amount of the exhaust valve 8 is reduced, the piston 21 is retracted. As a result, when hydraulic pressure is applied by pushing up the master piston 2a, both the piston 21 and the slave piston 6 are pushed, and the lift amount of the exhaust valve 8 becomes small.

With respect to claim 2, as shown in FIG. 2, the exhaust push rod 1a and the exhaust gas recirculation master piston 2b of the conventional structure are eliminated, and the exhaust gas recirculation oil passage 5b is driven by the engine and discharged. A hydraulic pressure generating pump device 24 is connected to control the amount by the governor 25 and the valve opening timing by the timer 26.

Further, as shown in FIG. 3, the exhaust push rod 1a and the exhaust gas recirculation master piston 2b of the conventional construction are eliminated, and the accumulator for accumulating the hydraulic pressure generated by the hydraulic pressure generating pump device 27 driven by the engine. 28 and the exhaust gas recirculation oil passage 5b
Is connected via a control valve 29 controlled by the computer 23 (claim 3).

In the configuration shown in FIGS. 2 and 3, the EG
At the time of R, hydraulic pressure is introduced from the accumulator 28 under the control of the hydraulic pressure generation pump device 26 or the control valve 29 into the exhaust gas recirculation oil passage 5b, and the exhaust valve 8 is pushed down. At this time, in the hydraulic pressure generating pump device 24, the lift amount and the valve opening timing of the exhaust valve 8 are controlled by the governor 25, and the valve opening timing is controlled by the timer 26. The accumulator 28 is controlled by the control valve 29 controlled by the computer 23.

Regarding claim 4, as shown in FIG.
The first exhaust cam 80a that opens the exhaust valve on the camshaft 80 during the exhaust stroke, and the second exhaust cam 80b that has the same phase as the intake cam 80c and a small cam lift so that the exhaust valve is opened for a certain period during the intake stroke. Two mountain cams are provided, and a part of the exhaust gas is introduced into the cylinder due to the pressure difference between the intake and exhaust when the exhaust valve is simultaneously opened by the second exhaust cam 80b when the intake valve is opened. .

With the above structure, as shown in FIG.
The exhaust valve of the first cylinder # 1 is opened simultaneously with the intake valve by the second exhaust cam 80b, the exhaust gas of the second cylinder # 2 is introduced into the first cylinder # 1, and the exhaust valve of the second cylinder # 2 is opened. The second exhaust cam 80b opens the valve simultaneously with the intake valve to introduce the exhaust gas of the third cylinder # 3 into the second cylinder # 2.
The third exhaust valve is opened simultaneously with the intake valve by the second exhaust cam 80b, and the exhaust gas of the first cylinder # 1 is introduced into the third cylinder # 3 to recirculate the exhaust gas.

As for claim 5, as shown in FIG. 4, the internal EGR device 7 shown in FIG.
0, a supercharger 30 composed of a compressor 50 rotated by an exhaust turbine 40, a waste gate valve 32 provided in an exhaust bypass passage 31 communicating an inlet and an outlet of the exhaust turbine 40, and the compressor 50. Inertial supercharging device 3 having an inertial supercharging control valve 34 that communicates with an intake pipe of an internal combustion engine 60 via an intercooler 35.
3, the wastegate valve 32 and the inertia supercharging control valve 34 are operated by the computer 23 to which the engine speed signal A, the load signal B and the water temperature signal C are input. In accordance with the above, the intake air pressure by the inertial supercharging device 33 is changed, and the EGR rate is optimally controlled according to the operating condition of the engine.

According to the above construction, as shown in FIGS. 5 and 6, the waste gate valve 32 determines the magnitude of the exhaust pulse, and the inertial supercharging device 33 uses the supply pressure (air amount). As shown in FIGS. 5 and 6, when the waste gate valve 32 is opened, the exhaust pulse becomes small and the EGR rate decreases. Further, if the inertial supercharging device 33 is operated so as to lower the supply air pressure, it becomes easier to inhale the exhaust gas and the EGR rate increases. An optimum EGR rate can be obtained by controlling this according to the operating condition of the engine.

Regarding claim 6, as shown in FIG. 7, in this case as well, the internal combustion engine 60 is provided with, for example, the conventional internal E of FIG.
GR device 70 and exhaust turbine 40a with variable nozzle
(VGT) rotating supercharger 30 including a compressor 50, the compressor 50, and an internal combustion engine 60.
The exhaust turbine 40a with a variable nozzle is premised on a structure in which the intake pipe of the variable nozzle is communicated with the intake pipe of
The variable nozzle of No. 2 is controlled according to the operating condition of the engine by the computer 23 to which the engine speed signal A, the load signal B, and the water temperature signal C are input to change the supply pressure.
The EGR is optimally controlled according to the operating condition of the engine.

In this case, as shown in FIG. 9, the internal combustion engine 60 is provided with the conventional internal E shown in FIG.
A supercharger 30 including a GR device 70 and a variable nozzle compressor 50a (VGC) that is rotated by an exhaust turbine 40, and the variable nozzle compressor 50a.
A computer in which an engine speed signal A, a load signal B, and a water temperature signal C are input to the variable nozzle of the compressor with variable nozzle 50a on the premise that the internal combustion engine 60 and the intake pipe of the internal combustion engine 60 are connected to each other via an intercooler 35. 23, the air supply pressure is changed according to the operating condition of the engine, and the EGR rate is optimally controlled according to the operating condition of the engine.

As to claim 8, as shown in FIG.
Also in this case, the internal combustion engine 60 includes the conventional internal EGR device 70 shown in FIG. 16 and the exhaust turbine 40a with a variable nozzle.
On the premise that a supercharger 30 including a compressor 50a (VGC) with a variable nozzle that rotates by (VGT), the compressor 50a with a variable nozzle and the intake pipe of the internal combustion engine 60 communicate with each other via an intercooler 35, The variable nozzle of the exhaust turbine with variable nozzle 40a and the variable nozzle of the compressor with variable nozzle 50a are controlled by the computer 23 to which the engine speed signal A, load signal B, and water temperature signal C are input according to the operating condition of the engine. Then, the supply pressure and the exhaust pulse are changed to optimally control the EGR rate according to the operating condition of the engine.

In the configurations shown in FIGS. 7, 9 and 11,
As shown in FIGS. 8, 10, and 12, the compressor 5
0, compressor 50a with variable nozzle and internal combustion engine 60
The intake pipe may be connected to the intake pipe of the above by an inertial supercharging device 33 having an inertial supercharging control valve 34 via an intercooler 35 (claim 9).

According to the configurations shown in FIGS. 7 to 12,
The exhaust turbine with variable nozzle 40a (VGT) determines the magnitude of the exhaust pulse. If the variable nozzle is throttled, the exhaust pulse becomes large and the EGR rate increases. Further, the compressor 50a with a variable nozzle determines the magnitude of the supply air pressure (air amount), and if the variable nozzle attached to the diffuser portion is throttled, the supply air pressure (air amount) decreases, and the EGR
The rate increases. Further, the inertial supercharging device 33 also changes the supply air pressure (air amount), so that if the supply air pressure (air amount) is reduced, the EGR rate increases.

In claim 10, as shown in FIG. 21, the compressor 5 rotated by the exhaust turbine 40
The supercharger 30 formed of 0, the waste gate valve 32 disposed in the exhaust bypass passage 31 that communicates the inlet and the outlet of the exhaust turbine 40, and the EG according to claims 1 to 4.
In the internal combustion engine 60 including the R device, a partition wall 92 is provided in the center of the exhaust manifold 90, a butterfly valve 91 is openably and closably arranged on the partition wall 92, and the butterfly valve 91 is opened and closed to exhaust gas. The recirculation rate is optimally controlled according to the operating condition of the engine.

In the above structure, by opening and closing the butterfly valve 91, its volume changes (exhaust pressure changes). That is, as shown in FIG. 22, when the butterfly valve 91 is opened, the exhaust pressure drops and the EGR rate decreases. Further, when the butterfly valve 91 is closed, the exhaust pressure becomes high and the EGR rate increases.

Therefore, by controlling these EGR rates according to the operating conditions of the engine, an optimum EGR rate can be obtained as shown in FIGS. 13, 14 and 15.

In the above embodiment, the internal combustion engine 60 having the conventional internal EGR device 70 of FIG. 16 has been described.
The internal EGR device 70 is not limited to the conventional internal EGR device 70 of FIG. 16, and may be an internal EGR device using another mechanism, or is not limited to the internal EGR device.
It also applies to internal combustion engines equipped with a device.

[0045]

As described above, according to the present invention, EG
In an internal combustion engine equipped with an R device, the lift amount of the exhaust valve, the valve opening timing, and the period can be controlled according to the operating condition of the engine, an optimum EGR rate can be obtained, and NOx reduction and starting white smoke are conventionally generated. It has a special effect that further improvement can be obtained.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of the apparatus of the present invention.

FIG. 2 is a sectional view of the apparatus of the present invention.

FIG. 3 is a sectional view of the device of the present invention.

FIG. 4 is a circuit configuration diagram of a supply / exhaust system of the device of the present invention.

5 is a graph showing the EGR rate control of the device of the present invention in FIG.

6 is a graph showing the EGR rate control of the device of the present invention in FIG.

FIG. 7 is a circuit configuration diagram of an air supply / exhaust system of the device of the present invention.

FIG. 8 is a circuit configuration diagram of a supply / exhaust system of the device of the present invention.

FIG. 9 is a circuit configuration diagram of a supply / exhaust system of the device of the present invention.

FIG. 10 is a circuit configuration diagram of an air supply / exhaust system of the device of the present invention.

FIG. 11 is a circuit configuration diagram of a supply / exhaust system of the device of the present invention.

FIG. 12 is a circuit configuration diagram of an air supply / exhaust system of the device of the present invention.

FIG. 13 is an EGR of the device of the present invention in FIGS.
Graph showing rate control

FIG. 14 is an EGR of the device of the present invention in FIGS. 7 to 12;
Graph showing rate control

FIG. 15 is an EGR of the device of the present invention in FIGS. 7 to 12;
Graph showing rate control

FIG. 16 is a sectional view showing a conventional device.

FIG. 17 is a diagram showing a related arrangement configuration of a conventional device for a plurality of cylinders.

FIG. 18 is an explanatory diagram of the operation process of the conventional device.

FIG. 19 is a block diagram of an intake / exhaust cam of the device of the present invention showing an EGR generating means by intake / exhaust.

FIG. 20 is an operation stroke explanatory diagram of the intake / exhaust cam structure of FIG. 19;

FIG. 21 is a configuration diagram of an EGR rate control mechanism of the device of the present invention.

22 is a graph showing the EGR rate control of the device of the present invention in FIG.

[Explanation of symbols]

 1a Inlet push rod 1b Exhaust push rod 2a Engine brake master piston 2b Exhaust gas recirculation master piston 5 Oil passage 5b Exhaust gas recirculation oil passage 6 Slave piston 7 Cylinder 8 Exhaust valve 10 Oil passage switching valve 20 Cylinder 21 Piston 22 Actuator 23 Computer 24 Hydraulic pressure generation pump device 25 Governor 26 Timer 27 Hydraulic pressure generation pump device 28 Accumulator 29 Control valve 30 Supercharger 31 Exhaust bypass passage 32 Wastegate valve 33 Inertial supercharger 34 Inertial supercharge control valve 35 Intercooler 40 Exhaust Turbine 50 Compressor 40a Exhaust with variable nozzle Turbine 50a Compressor with variable nozzle 60 Internal combustion engine 70 Internal EGR device 80a First exhaust cam 80b Second Exhaust cam 80c Intake cam 90 Exhaust manifold 91 Butterfly valve 92 Partition wall

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁶ Identification code Internal reference number FI Technical display location F02B 37/16 F02B 37/12 302C 37/18 F02D 11/06 A 37/24 13/04 A 37 / 12 302 23/00 J F02D 11/06 P 13/04 F02M 25/07 550B 23/00 550C 550K F02M 25/07 550 550R F02B 37/00 303B 303C 37/12 301J 301Q (72) Inventor Yukihiro Tsuji Tokyo Hinodai 3-1, 1-1 Hino Motor Co., Ltd. In Hino Motor Co., Ltd. (72) Inventor Akira Saito 3-1, 1 Hinodai, Hino City, Tokyo Hino Motor Co., Ltd.

Claims (11)

[Claims] 1. When an engine brake is operated, a master piston is operated by a rocker arm that is operated by a push rod of another cylinder to generate a pressure in oil supplied to an oil passage, and the generated oil pressure causes a slave piston to transmit the pressure. The exhaust valve of the engine cylinder near the compression top dead center is opened so that compressed air can escape from the exhaust port, and in addition to the master piston for engine brake operated by the rocker arm operated by the push rod, the exhaust valve in the intake stroke Is provided with an exhaust gas recirculation master piston that operates by a rocker arm that is operated by a push rod of another cylinder so as to open, and that generates pressure in the oil that is being supplied to the oil passage, The oil pressure generated by the master piston for exhaust gas recirculation is In an engine brake and an exhaust gas recirculation device for an internal combustion engine provided with an oil passage switching valve for selectively switching to a passage, a cylinder for changing the volume of the oil passage in the oil passage according to an operating condition of the engine, and an actuator for A piston that displaces in the cylinder is provided, and the lift amount of the exhaust valve is variable based on the displacement of the piston, and the exhaust gas recirculation rate is optimally controlled according to the operating condition of the engine. An exhaust gas recirculation device for an internal combustion engine. 2. When the engine brake is operated, a master piston is operated by a rocker arm that is operated by a push rod of another cylinder to generate a pressure in oil supplied to an oil passage, and the generated oil pressure causes a slave piston to transmit the oil. An exhaust valve of the engine cylinder near the compression top dead center is opened to allow compressed air to escape from the exhaust port, and an engine brake master piston operated by a rocker arm operated by the push rod and an exhaust gas recirculation oil passage are provided. And an engine brake and exhaust gas of an internal combustion engine provided with an oil passage switching valve for selectively switching the oil pressure generated by the engine brake master piston and the exhaust gas recirculation oil passage to the exhaust gas recirculation oil passage. In the recirculation device, an operating condition of the engine is provided in the exhaust gas recirculation oil passage. The oil pressure generating means for controlling the oil pressure in the oil passage is connected according to the situation, the lift amount of the exhaust valve is made variable based on the operating condition of the engine, and the exhaust gas recirculation rate is optimized according to the operating condition of the engine. An exhaust gas recirculation device for an internal combustion engine, characterized in that it is controlled in accordance with the above. 3. The oil pressure generating means according to claim 2, wherein an accumulator for accumulating oil pressure generated by an oil pressure generating pump device driven by an engine and the exhaust gas recirculation oil passage are connected via a control valve. An exhaust gas recirculation device for an internal combustion engine as described. 4. A camshaft is provided with a first exhaust cam that opens an exhaust valve in an exhaust stroke and a double exhaust cam that opens an exhaust valve during an intake stroke only for a certain period. An exhaust gas recirculation apparatus for an internal combustion engine, wherein a part of exhaust gas is introduced into a cylinder by a pressure difference between intake and exhaust while a second exhaust cam simultaneously opens the exhaust valve. 5. A supercharger comprising a compressor rotated by an exhaust turbine, a wastegate valve arranged in an exhaust bypass passage communicating an inlet and an outlet of the exhaust turbine, the compressor and an intake pipe of the engine. Inertial supercharging device having an inertial supercharging control valve that communicates with EGR and EGR
In an internal combustion engine including a device, at least one of the wastegate valve and the inertial supercharging control valve is controlled according to an operating condition of the engine, and the intake air pressure by the inertial supercharging device and the wastegate valve are controlled by the wastegate valve. An exhaust gas recirculation apparatus for an internal combustion engine, wherein an exhaust pulse is changed to optimally control an exhaust gas recirculation rate according to an operating condition of the engine. 6. An internal combustion engine having an EGR device and a supercharger comprising a compressor rotated by an exhaust turbine having a variable nozzle, wherein the variable nozzle of the exhaust turbine is controlled in accordance with an operating condition of the engine. An exhaust gas recirculation device for an internal combustion engine, wherein the supply pressure and the exhaust pulse are changed to optimally control the exhaust gas recirculation rate in accordance with the operating condition of the engine. 7. An internal combustion engine including a supercharger, which comprises a compressor with a variable nozzle that is rotated by an exhaust turbine, and an EGR device, wherein the variable nozzle of the compressor is controlled according to the operating condition of the engine to supply air. An exhaust gas recirculation apparatus for an internal combustion engine, wherein the pressure and the exhaust pulse are changed to optimally control the exhaust gas recirculation rate according to the operating condition of the engine. 8. An internal combustion engine including a supercharger, which comprises a compressor with a variable nozzle that is rotated by an exhaust turbine equipped with a variable nozzle, and an EGR device, wherein the variable nozzle of the exhaust turbine and the variable nozzle of the compressor are provided. An engine of an internal combustion engine characterized in that the supply pressure and the exhaust pulse are changed by controlling according to the operating condition of the engine, and the exhaust gas recirculation rate is optimally controlled according to the operating condition of the engine. Brake and exhaust gas recirculation equipment. 9. An inertial supercharging device having an inertial supercharging control valve communicating between the compressor and an intake pipe of an engine, comprising: a variable nozzle of the exhaust turbine, a variable nozzle of the compressor and the inertial supercharging control valve. 7. An exhaust gas recirculation rate is optimally controlled according to the operating condition of the engine by controlling at least one of them according to the operating condition of the engine to change the supply pressure and the exhaust pulse. 9. An engine brake and an exhaust gas recirculation device for an internal combustion engine according to 7 and 8. 10. An internal combustion engine including: a supercharger including a compressor rotated by an exhaust turbine; a wastegate valve arranged in an exhaust bypass passage communicating an inlet and an outlet of the exhaust turbine; and an EGR device. In this case, a partition wall is provided in the center of the exhaust manifold, and a butterfly valve is arranged on the partition wall so that it can be opened and closed.By opening and closing the butterfly valve, the exhaust gas recirculation rate is optimized to match the operating conditions of the engine. An exhaust gas recirculation system for an internal combustion engine, characterized in that it is controlled. 11. The operating condition of the engine is controlled by a computer on the basis of detection signals of engine speed, load and / or water temperature.
An exhaust gas recirculation device for an internal combustion engine according to 5, 6, 7, 8, 9 and 10.