JPH0116338B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an electronic accumulator fuel injection device for an internal combustion engine, particularly for use in a diesel engine.

(Prior Art) Generally, an electronic pressure accumulation type fuel injection device for an internal combustion engine is equipped with an electronic control unit (hereinafter referred to as "ECU").
This ECU operates the injection device based on command signals determined based on sensor signals sent from various sensors that detect engine operating conditions such as engine speed and engine load, and adjusts fuel injection amount, injection timing, etc. are doing.

(Problem to be solved by the invention) Used in such a fuel injection device
Since ECUs are mainly composed of microcomputers, their circuit configurations and wiring are complex, and failures are likely to occur in the circuits and wiring. like this
If a failure occurs in the ECU, the engine cannot be operated until the ECU is repaired, and in the case of a vehicle in particular, there is no choice but to leave the vehicle in the middle of operation. Therefore, some fuel injection systems equipped with conventional ECUs have double or triple safety circuits inside the ECU.
There are systems designed to minimize ECU failures (for example, Japanese Patent Application Laid-open No. 119955/1983).

However, providing such a safety circuit complicates the configuration and increases costs.
Moreover, even if a safety circuit is provided, ECU failure cannot be completely avoided. Therefore, until the electrical system around the ECU is repaired in case of an emergency,
There has been a desire for a fuel injection device that would enable emergency operation of vehicles.

The present invention has been made in view of the above circumstances, and allows fuel injection to be carried out under highly accurate electronic control by the ECU under normal conditions.
To provide an electronic pressure accumulation type fuel injection device for an internal combustion engine, which enables emergency operation of a vehicle, etc. by controlling with a fuel injection control system that does not depend on the ECU when a failure occurs in the ECU. The purpose is to

(Means for Solving the Problems) In order to achieve the above object, the electronic pressure accumulation type fuel injection device for an internal combustion engine of the present invention has a pressure receiving surface F ₂ d in the middle portion, a needle valve F ₂ b at one end, and Valve body F 2 biased by spring F ₃ in the direction in which the needle valve F ₂ b closes _.
is slidably arranged in the valve body storage hole _F4 of the nozzle holder _F1 , and the needle valve F2b is slidably disposed in the valve body storage hole _F4 of the nozzle holder _F1 .
A first pressurized space F ₄ b is provided in a portion corresponding to the tip of the
A second pressurized space is provided in a portion corresponding to the pressure receiving surface F ₂ d.
F ₄ c is provided with a third pressurized space F ₄ e in a portion corresponding to the end F ₂ a on the side opposite to the needle valve, and further the nozzle holder F ₁
an injection nozzle device F having an injection port F ₄ d communicating with the first pressurized space F ₄ b at the tip thereof; and a double-headed piston having a large diameter piston head at one end and a small diameter piston head at the other end. The double-headed piston A ₁ is arranged so that it can reciprocate within the cylinder A _{5 .}
The reciprocating movement of the piston head defines a first pressure chamber _A2 by the large diameter piston head and a second pressure chamber _A3 by the small _diameter piston head.
is connected to the first pressurized space F ₄ b of the injection nozzle device F and connected to the third pressurized space F ₄ e via a stop valve J; a first pump B that supplies hydraulic oil to the first pressure chamber _A2 of the pressure booster A; a second pump C that is driven by the engine and supplies fuel oil to the second pressure chamber _A3 of the pressure booster A; a hydraulic oil supply device D that supplies hydraulic oil to the second pressurized space F ₄ c of the nozzle device F via the electromagnetic switching valve E; It includes an electronic control device G that supplies a command signal to the electromagnetic switching valve E, and a speed governor H connected to the first pump B and the second pump C, and when the electronic control device G is in normal operation, the injection nozzle Controlling the oil pressure supplied to the second pressurized space F ₄ c of the device F to perform fuel injection control,
When the electronic control device G is not operating, the stop valve J is closed to supply fuel oil only into the first pressurized space F 4 b, and the first pressurized space F ₄ b is supplied with fuel oil corresponding to the operation of the speed governor H. The fuel injection is performed by controlling the injection timing by the first pump B and controlling the injection amount by the second pump C.

(Function) When the electronic control unit G is operating normally,
Fuel injection control is performed by controlling the oil pressure supplied to the second pressurized space F ₄ c of the injection nozzle device F. When the electronic control device G malfunctions, the stop valve J is closed, so that fuel oil is supplied only into the first pressurized space F ₄ b of the injection nozzle device F, and the governor H injection timing control by the first pump B and the second pump C corresponding to the operation of the
Fuel injection is performed by controlling the injection amount.

(Example) Hereinafter, one example of the electronic pressure accumulation type fuel injection device for an internal combustion engine of the present invention will be described based on the drawings.

FIG. 1 is an overall configuration diagram of an electronic pressure accumulation type fuel injection device for an internal combustion engine according to the present invention, and this fuel injection device includes a pressure booster A, first and second pumps B and C, and a hydraulic oil supply device D. , an electromagnetic switching valve E, an injection nozzle device F, an electronic control unit (ECU) G, a speed governor H, and a stop valve J.

Pressure intensifier A is a double-headed piston having a large diameter piston head at one end and a small diameter piston head at the other end.
A ₁ is slidably disposed within a cylinder A ₅ .
The first pressure chamber _A2 on the large-diameter piston head side is communicated with the first pump B, and the second pressure chamber A2 on the small-diameter piston head side communicates with the first pump B.
Pressure chamber _A3 is connected to second pump C and injection nozzle device F.
are connected to each other. Furthermore, of cylinder A ₅ ,
A gap _A4 defined by the movement of the double-headed piston _A1 in one direction is located on the side opposite to the first pressure chamber _A2 of the space in which the large-diameter piston head is housed.
The first pressure chamber _A2 and the first pump B communicate with each other via the communication path. Note that the relief valve K is a solenoid valve, and its solenoid _K1 is controlled by an electronic control device G.
electrically connected to.

The first pump B includes a plunger B 2 slidably disposed within a plunger barrel B ₁ having a first through hole B ₁ a in the peripheral wall and a second through hole B _{1 b} in one end wall. The first through hole B ₁ a is connected to the tank D ₁ and the second through hole B ₁ b is connected to the first through hole B 1 b.
They are respectively communicated with pressure chamber _A2 . Plunger B ₂
The upper end portion is cut out, and a belt-shaped annular protrusion B ₂ a is formed that extends substantially over the entire circumference and partially extends at an angle with respect to the axis. The annular protrusion B ₂ a is
As shown in FIG. 2, it consists of a flat portion a and an inclined portion b, and the width of this annular protrusion B ₂ a is constant over its entire length. The other end of the plunger _B2 is in contact with the camshaft L of the engine, and as the camshaft L rotates,
The plunger reciprocates in the axial direction within the plunger barrel _B1 , engages with the adjustment rod _B3 , and rotates as the adjustment rod _B3 is displaced. The adjusting rod _B3 is connected to the speed governor H, and is displaced by the operation of the speed governor H, and can also be displaced by the energization/deenergization of a solenoid _B4 fitted around it. has been done. solenoid
When B ₄ is energized, plunger B ₂ always engages the annular protrusion.
so that the flat part a of B ₂ a can slide at an angular position that matches the first through hole B ₁ a of the plunger barrel B ₁ ;
Plunger _B2 and adjustment rod _B3 are engaged.

Similarly to the first pump B, the second pump C has the first,
A plunger _C2 is slidably disposed within a plunger barrel _{C1 having} second through holes C1a _{and C1b} , respectively. The first through hole C ₁ a communicates with a fuel tank (not shown), and the second through hole C ₁ b communicates with the second pressure chamber A ₃ . The plunger C ₂ has an inclined notch C ₂ a whose width gradually increases at its upper end, and the plunger C ₂ of the first pump B has an inclined notch C 2 a whose width gradually increases.
Similarly, it reciprocates in the axial direction due to the rotation of the camshaft L, and rotates in response to the displacement of the adjusting rod _C3 due to the operation of the speed governor H and solenoid _C4 .

The hydraulic oil supply device D basically includes a tank _D1 that stores hydraulic oil, a hydraulic oil pump _D2 that pumps up the hydraulic oil from the tank _D1 , and a motor _D3 that drives the hydraulic oil pump _D2 . The discharge port of the hydraulic oil pump _D2 is connected to the inlet of the electromagnetic switching valve E via a first oil passage _D5 interposed with a filter _D4 ,
The tank _D1 is connected to the electromagnetic switching valve E via the second oil passage _D6 .
connected to the outlet of the

The electromagnetic switching valve E consists of a 4-port 2-position spool valve, and when the solenoid _E1 is energized, it is switched to the first position and the injection nozzle device F and the oil path are connected.
When _the solenoid _E1 is deenergized, it is switched to the first position and the injection nozzle device F is brought into communication with the oil passage _D6 .

The injection nozzle device F includes a nozzle holder _F1 and a valve body slidably housed in the nozzle holder _F1 .
F ₂ and a spring F ₃ that biases the valve body F ₂ in the valve closing direction. Valve body _F2 is at one end (lower end in the figure)
needle valve F ₂ b and the small diameter part of the end opposite to the needle valve (other end)
Consisting of F ₂ a and a large diameter part F ₂ c in the middle, the large diameter part
The diameter difference between F ₂ c and needle valve F ₂ b forms a pressure receiving surface F ₂ d. A valve body storage hole _F4 having _a diameter corresponding to the shape of the valve body _F2 is formed in the nozzle holder F1, and the valve body _F2 is slidably housed in the valve body storage hole _F4 . ing. The large diameter part F ₄ a of the valve body storage hole F ₄ is formed longer on the small diameter part F _{2 a side than the large diameter part F 2 c} of the valve body F ₂ ,
Spring F ₃ is stored in that space. The valve body storage hole F ₄ has first and second pressurized spaces in a portion corresponding to the tip of the needle valve F ₂ b and a portion corresponding to the pressure receiving surface F ₂ d.
F ₄ b and F ₄ c are formed respectively. First pressurized space
F ₄ b is communicated with the second pressure chamber A ₃ of the pressure intensifier A. An injection port F ₄ d communicating with the first pressurized space F ₄ b is formed at the tip of the nozzle holder F ₁ .
The second pressurized space F ₄ c is communicated with the hydraulic oil supply device D via the electromagnetic switching valve E. Valve body storage hole F ₄
A third pressurized space F ₄ e is formed in a portion corresponding to the end F ₂ a on the side opposite to the needle valve. This third pressurized space
F ₄ e is the second pressure chamber of pressure intensifier A via stop valve J.
It is connected to _A3 . In addition, the third pressurized space F ₄ e
is a second valve that opens in conjunction with the closing operation of stop valve J.
It is communicated with a relief tank T via a stop valve J'.

The electronic control device G includes a sensor G ₁ disposed in a communication path between the first pump B and the first pressure chamber A ₂ of the pressure intensifier A;
Various sensors G ₂ , G ₃ , G ₄ installed on the engine,
and each solenoid K ₁ , B ₄ , C ₄ , E ₁ respectively.

The speed governor H starts operating in conjunction with the closing operation of the stop valve J by an appropriate means (not shown), and controls the adjustment rod B ₃ of the first pump B and the adjustment rod C ₃ of the second pump C. Displace according to engine speed.

Next, the operation of the electronic pressure accumulation type fuel injection device for an internal combustion engine configured as described above will be explained. First, during normal operation of the electronic control device G, the solenoid _B4 of the first pump B is always energized, and the adjusting rod _B3 is fixed at a fixed position. Therefore, the plunger _B2 is connected to the flat part a of the annular protrusion _B2a (see Fig. 2).
While being held at an angular position that matches the first through hole B ₁ a of the plunger barrel B ₁ , it slides within the plunger barrel B ₁ in accordance with the rotation of the camshaft L. In this way, hydraulic oil is sent from the first pump B to the first pressure chamber _A2 of the pressure intensifier A at a constant timing.
Also, from the second pump C to the second pressure chamber of the pressure intensifier A
Oil is sent to A ₃ in the same manner as the first pump B, and an amount of fuel oil corresponding to the engine operating condition is sent to the second pressure chamber A ₃ at a constant timing. The oil supply timing of the second pump C is determined by the phase of the cam of the camshaft L that the plunger _C2 comes into contact with.
By making the phase of the cam for the plunger _B2 of the first pump B different, the oil feeding timing of the first pump B is advanced.

The hydraulic pressure led from the first pump B to the first pressure chamber _A2 of the pressure intensifier A presses the large-diameter piston head of the double-headed piston _A1 , and the hydraulic oil in the gap _A4 flows through the relief valve K. As the fuel is released, the double-headed piston _A1 descends to compress the fuel in the second pressure chamber _A3 , and the large-diameter piston head of the first pressure chamber _A2 , the second pressure chamber _A3 , and the small-diameter piston head are separated. The fuel pressure is increased according to the pressure receiving area ratio of the second pressure chamber.
A occurs within ₃ . The relief pressure of the relief valve K is variably controlled by a solenoid _K1 controlled by the electronic control device G by changing the set load of its operating spring.

The fuel oil pressurized in the second pressure chamber _A3 of the pressure intensifier A is then transferred to the third pressurized space of the injection nozzle device F.
F ₄ e and the first pressurized space F ₄ b. That is,
During normal operation of the electronic control device G, the third pressurized space
Since the stop valve J provided in the communication path to F ₄ c is always open, the pressurized fuel is supplied to the third pressurized space F ₄ e. Then, the hydraulic pressure in the third pressurized space F ₄ e presses the valve body F ₂ in the valve closing direction (downward in the figure), and the hydraulic pressure in the first pressurized space F ₄ b presses the valve body F _{2 .} This is almost equal to the force pushing the valve in the valve opening direction (upward in the figure), but since the spring F ₃ urges the valve body F ₂ toward the injection port F ₄ d, that is, in the valve closing direction, the valve body F ₂ is held in the open position, and this injection port F ₄ d is closed by needle valve F ₂ b. In order to open the injection port F ₄ d, that is, to perform fuel injection, the electromagnetic switching valve E is switched by the electronic control device G, and the second pressure is removed from the tank D ₁ of the hydraulic oil supply control D. Hydraulic oil is sent into the pressure space F ₄ c, and the hydraulic pressure applied to the pressure receiving surface F ₂ d of the valve body F ₂ pushes up the valve body F ₂ against the pressing force of the spring F ₃ . That is, by switching the electromagnetic switching valve E to the first position by energizing the solenoid _E1 , the first oil passage _D5 and the second pressurized space _F4c are communicated with each other, and the hydraulic oil pump _D2 is activated. The hydraulic oil in the tank D ₁ is then supplied into the second pressurized space F ₄ c. _The valve body F ₂ rises and opens due to the hydraulic pressure in the second pressurized space F ₄ c, and the needle valve F ₂ b opens the injection port F ₄ d.
The fuel oil in the first pressurized space F ₄ b is injected into the combustion chamber (not shown) of the engine. Thereafter, by switching the electromagnetic switching valve E to the second position, the second pressurized space F ₄ c is cut off from the first oil passage D ₅ and simultaneously communicated with the second oil passage D ₆ . 2. The hydraulic oil in the pressurized space F ₄ C is returned to the tank D ₁ again, and this causes the second pressure to push up the valve body F ₂ against the pressing force of the spring F ₃ .
The hydraulic pressure in the pressurized space F ₄ c disappears, and the valve body F ₂ descends and closes due to the pressing force of the spring F ₃ , and the injection port F ₄ d is closed by the needle valve F ₂ b and injection starts. finish. Therefore, the switching timing and valve opening time of the electromagnetic switching valve E determine the opening/closing timing and opening time of the injection port F ₄ d, and the fuel injection timing and injection amount are determined exclusively by the solenoid E _1. It relies on the operation of an electronic control unit G that sends command signals.

The electronic control device G operates from the first pump B to the pressure intensifier A.
A sensor that detects the working oil pressure to the first pressure chamber _A2
C ₁ and _other sensors installed on the engine to detect the operating status of the engine (e.g., engine speed, engine load, top dead center position of the engine piston, etc.)
Sensor signals from C ₄ are provided to provide command signals to solenoid E ₁ based on their respective sensor signals.

Next, if a failure occurs in the electronic control device G or its wiring system, each solenoid B ₄ in the first and second pumps B and C, the electromagnetic switching valve E, and the relief valve
C ₄ , E ₁ , K ₁ are not supplied with command signals from the electronic control unit G, and therefore each of these solenoids
B ₄ , C ₄ , E ₁ , and K ₁ are all deactivated. On this occasion,
Based on the operation of an appropriate fault display device (not shown) in conjunction with the operation of the electronic control device G, by manual operation by the driver of the vehicle, etc., or by an appropriate automatic switching means (not shown) that operates when the electronic control device G malfunctions. , close the stop valve J provided in the communication path to the third pressurized space F ₄ e. Then, in conjunction with the closing operation of this stop valve J, the second stop valve J' is opened, and the hydraulic pressure in the third pressurized space F ₄ e flows into the relief tank T, so that the third pressurized Hydraulic pressure in space F ₄ e is in the relief tank T
The pressure is reduced to the inside pressure. At the same time, the first pump B
As the solenoid _B4 is deenergized, the regulating rod _B3 is displaced by the speed governor H, so the plunger _B2 of the first pump B is rotated in accordance with the displacement of the regulating rod B3, and the plunger _B3 is rotated in accordance with the displacement of the regulating rod B3. At the inclined part b of the protrusion B ₂ a (see Figure 2),
The plunger moves up and down to match the first through hole _B1a of the plunger barrel _B1 . Therefore, the timing of supply of hydraulic oil to the pressure booster A is controlled by the speed governor H. Similarly to the first pump B, the second pump C also supplies a regulated amount of fuel to the pressure intensifier A by the speed governor H, and the fuel compression work in the pressure intensifier A is carried out by the first and second pumps. This is carried out with the hydraulic oil supply timing and fuel injection amount from the pumps B and C, respectively, and the fuel pressurized in this way is fed under pressure to the first pressurized space F ₄ b of the injection nozzle device F.

As mentioned above, during normal operation of the electronic control device G, during control by the electronic control device G, the oil pressure in the third pressurized space F ₄ e of the injection nozzle device F and the first pressurized space F ₄ Assuming that the oil pressures in b are equal, the second pressurized space F ₄ c with respect to the pressing force of spring F ₃
The injection port F ₄ d is opened and closed by adjusting the oil pressure inside. In the event of a failure of the electronic control device G, it becomes impossible to adjust the oil pressure in the second pressurized space _F4c , so the stop valve J is closed as described above, and the second stop valve J' is also closed. Open the valve and open the third pressurized space
The oil supply from the pressure intensifier A to F ₄ e is cut off, and the hydraulic pressure in the third pressurized space F ₄ e is released, so that the hydraulic pressure in the first pressurized space F ₄ b is exclusively applied to the spring F ₃ . In other words, when the hydraulic pressure in the first pressurized space _F4b overcomes the pressing force of the _{spring F3} , the valve body _F2 opens, the injection port _F4d opens, and the first pressurized space The hydraulic pressure in F ₄ b is
When the valve body F 2 is defeated by the pressing force of F ₃ , the valve body F ₂ closes and the injection port F ₄ d is closed.

By changing the control of fuel injection to control by the speed governor H in this way, it is possible to ensure the minimum operating ability of the internal combustion engine even when the electronic control device G fails.

(Effects of the Invention) As described above, the electronic pressure accumulation type fuel injection device for internal combustion engines of the present invention has a pressure receiving surface F ₂ d in the middle part and a needle valve at one end.
F ₂ b respectively, and the needle valves F ₂ b each have a spring F ₃ .
A valve body _F2 biased in the direction of closing the valve is slidably disposed within the valve body storage hole _F4 of the nozzle holder _F1 ,
The valve body storage hole F ₄ has a first pressurized space F 4 b in a portion corresponding to the tip of the needle valve F ₂ b, and a first pressurized space F ₄ b in a portion corresponding to the tip of the needle valve F 2 b.
A second pressurized space F ₄ c is provided in a portion corresponding to F ₂ d, and a third pressurized space F ₄ e is provided in a portion corresponding to the opposite end F ₂ a of the nozzle holder F ₁ . An injection nozzle device F having an injection port F ₄ d communicating with the first pressurized space F ₄ b at its tip, and a double-headed piston A having a large diameter piston head at one end and a small diameter piston head at the other end. ₁ is disposed in a reciprocating manner in a cylinder _A5 , and the reciprocating movement of this double-headed piston _A1 creates a first pressure chamber A2 inside by a large-diameter piston head and a second pressure chamber _A2 by a small-diameter piston head. A pressure chamber A ₃ is defined respectively, the second pressure chamber A ₃ is connected to the first pressurized space F ₄ b of the injection nozzle device F, and a stop valve J is connected to the third pressurized space F ₄ e. a first pump B driven by an engine to supply hydraulic oil to the first pressure chamber A2 of the pressure intensifier A; and a _first pump B driven by the engine to supply hydraulic oil to the first pressure chamber A2 of the pressure intensifier A; 2nd pump C that supplies fuel oil to chamber A ₃
, a hydraulic oil supply device D that supplies hydraulic oil to the second pressurized space F ₄ c of the injection nozzle device F via the electromagnetic switching valve E, and a hydraulic oil supply device D that supplies the hydraulic oil to the second pressurized space F 4 c of the injection nozzle device F, and the first pump B and the first pump an electronic control device G that supplies command signals to the two pumps C and the electromagnetic switching valve E; and a speed governor H connected to the first pump B and the second pump C; when the electronic control device G is in normal operation; , controls the oil pressure supplied to the second pressurized space F ₄ c of the injection nozzle device F to perform fuel injection control, and when the electronic control device G is inactive, closes the stop valve J and performs the fuel injection control. Fuel oil is supplied only into the first pressurized space F ₄ b, and fuel injection is performed by controlling the injection timing by the first pump B and controlling the injection amount by the second pump C in response to the operation of the speed governor H. It was designed to do this.

Therefore, in the event of a failure of the electronic control device G, the supply of hydraulic oil and fuel oil by the first and second pumps B and C should be controlled in accordance with the operation of the speed governor H, and the fuel should be injected. As a result, the minimum operating capacity of the internal combustion engine can be ensured, and emergency operation of vehicles, etc. is possible.

[Brief explanation of drawings]

FIG. 1 is an overall configuration diagram of an electronic pressure accumulation type fuel injection device for an internal combustion engine showing an embodiment of the present invention, and FIG. 2 is a developed view of an annular protrusion of a plunger of a first pump of the same device. A...Pressure booster, _A1 ...Double-headed piston, _A2 ...
...First pressure chamber, A ₃ ...Second pressure chamber, B...First
Pump, C...Second pump, E...Solenoid switching valve,
F... Injection nozzle device, F ₁ ... Nozzle holder,
F ₂ ... Valve body, F ₃ ... Spring, F ₂ b ... Needle valve, F ₂ d ...
...Pressure receiving surface, F ₄ ... Valve body storage hole, F ₄ b ... First pressurized space, F ₄ c ... Second pressurized space, F ₄ d ... Injection port,
F ₄ e...Third pressurized space, G...Electronic control device, H
...Governor, J...Stop valve.

Claims (1)

[Claims] 1. A valve body F 2 which has a _pressure receiving surface F ₂ d in the middle part and a needle valve F ₂ b at one end, and is biased by a spring F ₃ in a direction in which the needle valve F ₂ b closes. It is slidably arranged in the valve body storage hole _F4 of the nozzle holder _F1 , and the valve body storage hole _F4 has a first pressurized space in a portion corresponding to the tip of the needle valve _F2b . F ₄ b, a second pressurized space F ₄ c in a portion corresponding to the pressure receiving surface F ₂ d, and an end F ₂ a on the opposite side of the needle valve.
A third pressurized space F ₄ e is provided in the corresponding portion, respectively.
Furthermore, an injection nozzle device F is provided with an injection port F ₄ d communicating with the first pressurized space F ₄ b at the tip of the nozzle holder F ₁ , and a large diameter piston head at one end and a small diameter piston head at the other end. A double-headed piston _A1 , each having _a
The reciprocating motion of this double-headed piston _A1 defines a first pressure chamber _A2 inside by the large-diameter piston head and a second pressure chamber _A3 by the small-diameter piston head. A ₃ is connected to the first pressurized space F ₄ b of the injection nozzle device F, and the third
A pressure intensifier A connected to the pressurized space F ₄ e via a stop valve J, and a first pressure intensifier A driven by the engine.
a first pump B that supplies hydraulic oil to the pressure chamber _A2 ;
The second pressure chamber of the pressure intensifier A is driven by the engine.
A second pump C that supplies fuel oil to A ₃ ; and a hydraulic oil supply device D that supplies hydraulic oil to the second pressurized space F ₄ c of the injection nozzle device F via an electromagnetic switching valve E.
and the first pump B depending on the operating state of the engine.
An electronic control device G that supplies command signals to a second pump C and an electromagnetic switching valve E, and a speed governor H connected to the first pump B and second pump C, and normal operation of the electronic control device G. Sometimes, the fuel injection control is performed by controlling the oil pressure supplied to the second pressurized space F ₄ c of the injection nozzle device F, and the electronic control device G
When inactive, the stop valve J is closed to supply fuel oil only into the first pressurized space F ₄ b, and the first pump B injects fuel oil in response to the operation of the speed governor H. An electronic pressure accumulation type fuel injection device for an internal combustion engine, characterized in that fuel injection is performed by timing control and injection amount control by the second pump C.