JPH07109183B2 - Injection control device for accumulator fuel injection device for diesel engine - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an injection control device for a pressure-accumulation fuel injection device for a diesel engine, and in particular, the injection start timing can be easily controlled only by a fuel supply system, and The present invention relates to an injection timing control device of a pressure-accumulation fuel injection device for a diesel engine, which is capable of improving control accuracy of injection start timing.

<Prior Art> Generally, a pressure accumulating fuel injection device for a diesel engine is
For example, as shown in FIG. 1 or FIG. 6, a pressure accumulation type fuel injector 7 and a fuel supply system for supplying fuel to this are provided.

The pressure-accumulation fuel injector 7 is a fuel injector that injects fuel that has been accumulated and accumulated at a high pressure such as 700 to 1200 atm, and is, for example, as shown in FIG. 1, FIG. 2, and FIG. A fuel inlet 11 for receiving fuel from the outside, a valve closing pressure chamber 12, a check valve 13, and a fuel pressure accumulating chamber which are sequentially connected to the fuel inlet 11.
14, the injection valve 15 and the injection hole 16, and the valve closing spring 43, the injection valve 15 is urged to open the valve by the internal pressure of the fuel pressure accumulating storage chamber 14, while the urging force and closing of the valve closing spring 43. The valve pressure chamber 12 is configured to be biased to be closed by the internal pressure of the valve chamber 12. Then, the fuel injection valve 15 supplies high-pressure fuel of, for example, 700 to 1200 atm from the fuel supply system in a state in which the injection valve 15 is closed by the valve closing spring 43 that opposes the internal pressure of the fuel pressure accumulating storage chamber 14. After press-fitting into the fuel pressure storage chamber 14 via the fuel inlet 11, the valve closing pressure chamber 12 and the check valve 13, the internal pressure of the fuel pressure storage chamber 14 is released by depressurizing the internal pressure of the valve pressure storage chamber 12. The injection valve 15 is opened by weakening the valve closing force, which is the internal pressure of the valve closing pressure chamber 12 and the urging force of the valve closing spring 43, rather than the valve force, and the fuel in the fuel pressure accumulating chamber 14 is injected from the injection hole 16 Is configured to let.

The fuel supply system is designed to inject fuel at a high pressure as described above into the pressure-accumulation fuel injector 7 at a predetermined timing.
It is usually configured as follows. That is, the first
As shown in FIG. 6 and FIG. 6, fuel is pumped from the fuel tank 1 by a fuel pump (feed pump) 2, and the pressure of the pumped fuel is regulated by a pressure regulator 3 in accordance with, for example, the engine speed. Further, after the amount is adjusted by the amount adjusting device 4 according to the load condition of the engine, the pressure is fed by the pressure feed pump (transfer pump) 5, and the fuel discharged from the pressure feed pump 5 is, for example, 700 to 1200 atm by the fuel injection pump 6. It is configured to pressurize the accumulator fuel injector 7 by pressurizing it to a high pressure above a predetermined pressure. In addition, the fuel injection pump 6
Is usually a plunger pump,
An inlet valve 10 is provided on the upstream side of the pump chamber 9 through which the plunger 8 moves in and out to prevent backflow to the side, and the outlet side of the pump chamber 9 is connected to the fuel inlet 11 of the pressure accumulating fuel injector 7.

By the way, in the pressure-accumulation type fuel injection device for diesel engine configured as described above, the injection control device configured to open the injection valve 15 by depressurizing the internal pressure of the valve closing pressure chamber 12 at a predetermined timing. Is required.

Conventionally, the fuel injection pump 6 is also used as an injection control device of a pressure-accumulation fuel injection device for a diesel engine. That is, after the fuel is stored in the pressure-accumulation fuel injector 7, the plunger 8 is withdrawn from the pump chamber 9 to increase the volume of the pump chamber 9 and release the internal pressure of the valve closing pressure chamber 12 to the pump chamber 9. It is configured to open the injection valve 15 by reducing the valve closing biasing force of the injection valve 15 rather than the valve opening biasing force.

<Problems to be Solved by the Invention> In such a fuel injection control device for a conventional pressure-accumulation fuel injection device, a cam for driving the plunger 8 to counter the internal pressure of the pump chamber 9 received by the plunger 8 or a cam for driving the plunger 8 It is necessary to provide a relatively large contact area with the interlocking transmission mechanism. Therefore, it is difficult to form a cam profile that causes the plunger 8 to rise rapidly, which imposes a great limitation in increasing the rate of rise of the plunger. Further, the inertia of the plunger 8 also gives a certain limit to the rising speed of the plunger 8. The restriction on the rising speed of the plunger 8 imposes a large restriction on the expansion rate of the volume of the pump chamber 9, and the pressure reduction gradient of the internal pressure of the valve closing pressure chamber 12 cannot be made steeper than a certain level. In addition, the range of variation in control of the injection start timing caused by some reason such as mechanical vibration caused by striking of a driving device for driving the driving device or components in the driving device becomes large.

Then, as a result of earnestly researching, the present inventor has solved such conventional problems and improved the control accuracy of the injection start timing control. Hereinafter, the invention is referred to as a prior invention) was invented prior to the present invention.

That is, in this prior invention, as shown in FIG. 6, an injection start command valve (here, the inlet valve 10 of the fuel injection pump 6 is also used) is provided in the valve closing pressure chamber 12 of the pressure accumulating fuel injector 7. A technical means is provided in which a pressure release passage 17 is connected via an injection start command means 18 for opening and closing the injection start command valve 10 at a predetermined timing.

In this prior invention, the injection start command valve 10 is composed of a spool valve that is biased to be closed by the internal pressure of the flow path on the upstream side thereof, and the injection start command means 18 and a timing setting valve 19 linked to the crankshaft. The pressure reducing chamber 20 is connected to the flow passage on the upstream side of the injection start command valve 10 via the timing setting valve 19, and after the fuel is injected from the fuel injection pump 6 into the pressure accumulating fuel injector 7, Timing setting valve by crankshaft angle
By opening the valve 19, the flow passage on the upstream side of the injection start command valve 10 and the decompression chamber 20 are communicated with each other to reduce the internal pressure of the flow passage on the upstream side of the injection start command valve 10, and as an injection start command valve. The inlet valve 10 is opened to reduce the internal pressures of the pump chamber 9 and the valve closing pressure chamber 12.

In this case, since the injection start command means 18 opens the inlet valve 10 as the injection start command valve at a predetermined timing to reduce the internal pressure of the valve closing pressure chamber 12, the valve is closed more rapidly than the conventional example. The internal pressure of the pressure chamber 12 can be reduced, which is more advantageous in increasing the engine speed, and the injection start timing can be easily controlled only by the fuel supply system. Further, by appropriately setting the shape of the valve hole of the inlet valve 10 or the timing setting valve 19, the valve opening amount of the inlet valve 10 as the injection start command valve is changed by the stroke of the spool, and the pump chamber 9 and the valve closing pressure chamber The internal pressure of 12 is controlled over time, and during the ignition lag period from the start of injection to the ignition, the valve opening amount of the injection valve is kept small to reduce the fuel injection amount, and the injection valve is suddenly increased after ignition. It can be fully opened to inject a large amount of fuel within a short time.

In this prior invention, the inlet valve 10 of the fuel injection pump 6 as an injection start command valve is provided in the vicinity of the pressure accumulating fuel injector 7, whereas the timing setting valve 19 is a mechanism for interlocking this with the crankshaft. In order to simplify the above, a position that is supported at the shaft end of the crankshaft (or a rotary shaft such as a valve camshaft that is interlocked with the crankshaft) and is located far away from the cylinder head to which the pressure accumulating fuel injector 7 is mounted. It is located in. Further, the decompression chamber 20 is also arranged at a position apart from the pressure accumulation type fuel injector 7 in order to shorten the distance from the timing setting valve 19, such as being built in the timing setting valve 19.

However, when the path length from the valve closing pressure chamber 12 to the pressure reducing chamber 20 is long in this way, the flow path resistance between them becomes large, and the pump chamber 9 and the fuel inlet after the injection start command valve 10 are opened.
11 and the pressure reduction gradient of the internal pressure of the valve closing pressure chamber 12 becomes relatively slow, the control sensitivity is enhanced, and the range of variation of the valve opening start timing control of the injection valve 15 is narrowed to enhance the control accuracy. It turns out that dissatisfaction still remains above.

The present invention has been made in view of the above circumstances, and is for a diesel engine in which the injection start timing can be easily controlled only by the fuel supply system and the injection start timing control accuracy can be improved. An object of the present invention is to provide an injection control device for a pressure accumulation type fuel injection device.

The injection control device of the pressure-accumulation type fuel injection device for a diesel engine according to the present invention is configured as follows, as shown in FIGS. 1 to 3, for example.

First, as a prerequisite configuration, a pressure-accumulation type fuel injector for a diesel engine is provided with a pressure-accumulation type fuel injector (7) and a fuel supply system for supplying fuel to the pressure-accumulation type fuel injector (7). A fuel injection pump (6) for injecting the stored fuel into a pressure-accumulation fuel injector (7),
And an inlet valve (10) for opening and closing the inlet side of the fuel injection pump (6).
Fuel inlet (11) communicating with the pump chamber (9) of the valve, the valve closing pressure chamber (12), the check valve (13), the fuel pressure accumulating chamber (14), and the injection valve (15) that are sequentially connected to the fuel inlet (11). And an injection hole (16) and a valve closing spring (43). The injection valve (15) is biased to open by the internal pressure of the fuel pressure accumulating chamber (14) while the valve closing spring (43) is closed. ) And the internal pressure of the valve closing pressure chamber (12) to close the valve, and by pushing the plunger (8) of the fuel injection pump (6) into the pump chamber (9), The fuel inlet (1
1), after press-fitting into the fuel pressure storage chamber (14) through the valve closing pressure chamber (12) and the check valve (13), the internal pressure of the valve closing pressure chamber (12) is depressurized at a predetermined timing. Thus, the valve closing biasing force of the injection valve (15) is made weaker than the valve opening biasing force to open the injection valve (15).

Then, as a characteristic configuration, an injection start command valve (21) and an injection start decompression chamber (22) arranged close to the valve closing pressure chamber (12) of the pressure accumulating fuel injector (7). Are sequentially connected to the fuel injection pump (6) and the valve closing pressure chamber (12) through the inlet valve (10), and the injection start command valve (21) is connected to the injection start command valve (21) by the internal pressure. 21) and inlet valve (1
The pressure receiving chamber (36) for urging the valve body (29) of (0) to close and the valve opening pressure chamber (35) for urging the valve body (29) to open are provided, and the injection start command valve ( 21) is provided with an injection start command means (18) for opening the valve at a predetermined injection start time, and the injection start command means (18) supplies fuel from the fuel injection pump (6) to the pressure accumulation type fuel injector (7). A timing setting valve (19) opened at a predetermined time point after press fitting and a decompression chamber (20) communicating with the pressure receiving chamber (36) via the timing setting valve (19) are provided. The timing setting valve (19) is linked to the crankshaft of the engine, and by opening the timing setting valve (19), the pressure receiving chamber (36) communicates with the decompression chamber (20), and the internal pressure of the pressure receiving chamber (36) is increased. The injection start command valve (21) is opened by depressurizing the
The valve is opened by the internal pressure of 5) and the internal pressure of the valve closing pressure chamber (12) is released into the decompression chamber (22) for starting injection.

<Operation and Effect of the Invention> Since the present invention is configured as described above, the following operation and effects are achieved.

(A) Improvement of control accuracy of ignition fuel injection start timing Since the injection start command valve (21) and the injection start decompression chamber (22) are arranged close to the valve closing pressure chamber (12), the valve closing pressure is increased. The resistance of the flow path from the chamber (12) to the injection start decompression chamber (22) is small, and the decompression gradient of the valve closing pressure chamber (12) becomes steep.

As a result, the response sensitivity from the opening of the injection start command valve (21) to the pressure reduction of the valve closing pressure chamber (12) becomes sensitive, and the variation in the opening timing of the injection valve (15) decreases. The control accuracy of the injection start timing of the fuel injection for ignition is improved.

(B) High-speed rotation of engine The injection start command valve (21) is opened at the pressure (P ₀ ′) in the valve opening pressure chamber (35) due to the pressure reduction in the valve closing pressure receiving chamber (36). The pressure (P ₀ ) in the valve closing pressure receiving chamber (36) is the fuel injection pump (6).
Is increased to a high pressure by the discharge pressure of, and the pressure (P ₀ ′) in the valve opening pressure chamber (35) that balances with this is also increased.

Since the pressure (P ₀ ) in the valve closing pressure receiving chamber (36) is high and has a high energy density, pressure release to the pressure reducing chamber (20) is rapid when the timing setting valve (19) is opened. Go to
The injection start command valve (21) is strongly and rapidly opened by the high pressure with high energy density of the valve opening pressure chamber (35).

Therefore, the valve opening response speed from the start of depressurization of the valve closing pressure receiving chamber (36) to the opening of the injection start command valve (21) becomes very fast. Moreover, the valve opening speed from the opening start to the opening end of the injection start command valve (21) becomes much higher than the valve opening speed of the timing setting valve (19).

As a result, the injection start command valve (21) opens and the valve closing pressure chamber (12) starts when the timing setting valve (19) starts to open.
The injection delay time until the time when the injection valve (15) opens and the fuel injection starts after the pressure of the pressure is reduced to the injection decompression chamber (22) is greatly shortened. .

That is, when the valve is opened using the electric actuator, the energy density of the electromagnetic force generated in the electric actuator is relatively low, and the motion delay due to the static inertia of the working shaft of the electric actuator occurs. The valve opening response speed and the valve opening speed of the injection start command valve (21) are both slow, and the injection delay time is long.

In comparison with this, in the present invention, the valve opening force of the injection start command valve (21) is high in energy density at high pressure, and
Since there is no motion delay due to the static inertia of the working shaft of the electric actuator, the valve opening response speed of the injection start command valve (21) becomes very fast.

Moreover, since the timing setting valve (19) is linked to the crankshaft of the engine, the opening timing of the timing setting valve (19) is mechanically and accurately determined by the rotation angle of the crankshaft. , Timing setting valve (19)
Unlike the case where the valve is opened by the electric actuator, the delay of the valve opening timing due to the operation delay time of the operation shaft of the electric actuator can be eliminated.

As described above, there is no opening delay of the timing setting valve (19) with respect to the rotation angle of the crankshaft, and the opening response speed and opening speed of the injection start command valve (21) described above are high pressures with high energy density. Since the injection delay time is greatly shortened by driving the engine at very high speed, the maximum engine speed is released from the constraint due to the operation delay time of the electric actuator, and the engine is rotated at a sufficiently high speed. Can be converted.

(C) Simplification of configuration and improvement of durability The timing setting valve (19) controls opening / closing in conjunction with the crankshaft, and the injection start command valve (21) receives the discharge pressure of the fuel injection pump (6). By supplying / discharging to / from the chamber (36) and controlling opening / closing, an electric actuator, an electric control device for driving and controlling the actuator, and a battery for supplying electric power to these are unnecessary, and the configuration is simplified. You can

Further, since the injection control device of the present invention does not require a battery, it can be used for a general-purpose engine of a type not equipped with a battery or a work engine.

Further, the electric actuator, the electric control device for driving and controlling the actuator, and the fuel injection failure due to the malfunction or failure of the battery can be completely eliminated, so that the durability is excellent.

<Example 1> An example of the present invention will be described below with reference to Figs.

FIG. 1 is an equivalent circuit diagram of a pressure-accumulation fuel injection device for a diesel engine according to the present invention, and FIG. 2 is a vertical cross-sectional view of a unit injector used in the fuel injection device in an initial state. FIG. 4 is a vertical cross-sectional view of the main part of the unit injector when the injection start command valve is opened, and FIG. 4 is a timing diagram for explaining the operation of the unit injector and the injection start command means.

As shown in FIG. 1, the pressure-accumulation type fuel injection device for a diesel engine includes a fuel tank 1, a metering unit M, and a unit injector U.

The metering unit M includes a fuel pump 2, a pressure regulator 3, a metering device 4, and a pressure pump 5.

The unit injector U includes an edge filter 27,
A fuel injection pump 6 and an accumulator fuel injector 7 are incorporated.

The pressure-accumulation fuel injection device for a diesel engine further includes an injection control device that controls the fuel injection start timing and injection characteristics of the pressure-accumulation fuel injector 7, and this injection control device will be described later. It is provided across the metering unit M and the unit injector U.

The fuel system that supplies fuel to the pressure-accumulation fuel injector 7 regulates the pressure of the fuel pumped from the fuel tank 1 by the fuel pump 2 by the pressure regulator 3 so as to increase or decrease in direct proportion to the engine speed, for example. The amount of fuel supplied by the pressure device 3 is adjusted by the amount adjusting device 4 so as to increase or decrease in direct proportion to, for example, the load of the engine, and then the pressure pump 5 supplies the fuel injection pump 6 via the edge filter 27. It is configured to be pressure-fed, to be pressurized to a high pressure of, for example, 700 to 1200 atm by the fuel injection pump 6, and to be press-fitted into the pressure accumulating fuel injector 7.

As shown in FIG. 2 and FIG. 3, the fuel injection pump 6 is
Is a plunger 8 inserted into a plunger insertion hole 24 formed in a recess from the top surface (right surface in FIG. 2) of the body 23 of the unit injector U, and the lower portion of the plunger insertion hole 24 is partitioned by the plunger 8. The pump chamber 9 and the inlet valve 10 are provided.

The inlet valve 10 can be provided independently of the plunger 8, but in this case, it is incorporated in the plunger 8 in order to reduce the size of the unit injector U. That is, a substantially cylindrical valve chamber 28 whose upper end and lower end are slightly expanded is formed inside the plunger 8, and a spool 29 is slidably fitted in the valve chamber 28. . This spool 29
Is a hollow cylinder with a closed top,
The reference numeral 32 indicates the edge filter 27 side (upstream side) at all times via the inlet passage portion 31 that penetrates the intermediate height portion of the peripheral wall of the spool 29 and the inlet passage portion 30 that penetrates the intermediate height portion of the peripheral wall of the plunger 8. ). The inlet valve 10 includes an inlet valve hole 33 formed in the lower half portion of the peripheral wall of the spool 29 and an outlet 34 formed in the lower half portion of the peripheral wall of the plunger 8, so that the spool 29 is slightly smaller than the top dead center. The inlet valve hole 33 communicates with the outlet 34 to open the valve when the height is lower than a predetermined height, and the inlet valve hole 33 is shut off from the outlet 34 and closed when the spool 29 is positioned higher than that. Like so.

Inside the valve chamber 28, there is a valve-opening pressure chamber 35 in the upper part and a pressure-accumulating chamber 36 for adjusting the plunger stroke in the lower part.
It is divided by each. And spool 29
Is urged in the valve closing direction by the internal pressure P _{0 of} the hollow portion 32 communicating with the upstream side of the inlet valve 10 and the pressure accumulating chamber 36, and the internal pressure of the valve opening pressure chamber 35.
It is biased in the valve opening direction by P ₀ ′. The valve opening pressure chamber 35 has a hollow portion formed by a communication hole 37 formed in an upper portion of the peripheral wall of the spool 29 when the spool 29 is located at the top dead center.
When the spool 29 is located at the bottom dead center, the spool 29 is communicated with the hollow portion 32 through the communication hole 37 and the passage 38 formed in the upper portion of the peripheral wall of the plunger 8. Made of

An injection pipe insertion hole 25 is formed in the body 23 of the unit injector U in parallel with the plunger insertion hole 24, and the injection pipe 26 of the accumulator fuel injector 7 is fitted and supported in the injection pipe insertion hole 25. .

In the lower half of the injection pipe 26, the valve closing pressure chamber 12 and the check valve chamber
36 and a part of the fuel pressure accumulating storage chamber 14 (hereinafter referred to as the first fuel pressure accumulating storage chamber) 14a are coaxially arranged in a vertical direction in a series to form a series, and a lower end portion of the first fuel pressure accumulating storage chamber 14a (second
The valve seat surface 40 of the injection valve 15 is formed on the peripheral surface of the left end portion in the drawing).

The valve stem 42 of the injection valve 15 penetrates through the first fuel pressure accumulating and storing chamber 14a, the check valve chamber 39 and the valve closing pressure chamber 12, and the upper end thereof is closed in the upper half of the injection pipe 26. It is inserted into the valve spring chamber 41.

The valve body 13a of the check valve 13 is slidably fitted in the check valve chamber 39 interposed between the valve closing pressure chamber 12 and the first fuel pressure accumulating injection chamber 14a. The valve closing spring 1 is directed toward the valve seat 13b formed by the enlarged diameter portion formed at the intermediate height of the valve stem 42 of the injection valve 15.
Uplifted by 3c. Therefore, this check valve 13
13a is the internal pressure of the valve closing pressure chamber 12 (= the internal pressure of the pump chamber 9).
The internal pressure P _{2 of} the first fuel pressure accumulating injection chamber 14a is biased by the valve opening at P ₁ ).
Is closed and the fuel is injected by the fuel injection pump 6 so that the internal pressure P ₁ of the valve closing pressure chamber 12 becomes the first fuel pressure accumulation injection chamber 14
It will be opened only when the internal pressure P ₂ of a exceeds.

An injection valve is provided inside the valve closing spring chamber 41 through the valve stem 42.
A valve closing spring 43 for urging 15 in the valve closing direction is inserted.

Therefore, the injection valve 15 is biased in the valve closing direction by the biasing force of the valve closing spring 43 and the internal pressure P ₁ of the valve closing pressure chamber 12, and is opened by the internal pressure P _{2 of} the first fuel pressure accumulating and storing chamber 14a. After the supply of fuel from the fuel injection pump 6 is completed and the check valve 13 is closed, the internal pressure P ₁ of the valve closing pressure chamber 12 is reduced and the above-mentioned valve closing force is opened. If it becomes smaller than the force, it will be opened.

The upper end of the valve closing spring chamber 41 is closed by a spring seat 44 that sets the urging force of the valve closing spring 43 and a valve opening restrictor 45 that sets the maximum valve opening amount of the injection valve 15. The lower end of 41 is communicated with the valve opening pressure chamber 35 of the inlet valve 10 via a pressure transmission passage 46 and a passage 38 formed in the plunger 8. Further, a cap 47 that covers the spring seat 44 and the valve opening restrictor 45 is screwed onto the upper end portion of the injection pipe 26. The cap 47 and the spring seat
A space 48 formed between the valve opening limiter 45 and the valve opening limiter 45 communicates with the valve closing spring chamber 41 via a communication passage 49 provided in the valve opening limiter 45. With this structure, the space 48 formed between the cap 47, the spring seat 44, and the valve opening restrictor 45 is closed together with the valve closing spring chamber 41 in the valve opening pressure chamber 35 of the inlet valve 10.
It plays the role of a valve-opening pressure stabilization accumulator that absorbs the sudden pressure fluctuations.

The remaining portion of the fuel pressure accumulating chamber 14 (hereinafter referred to as the second fuel pressure accumulating chamber) 14b is formed in an annular shape over the intermediate height portion of the injection pipe 26 and the body 23 portion around it.
The second fuel pressure accumulating storage chamber 14b is provided with a check valve 50 and a pressure setting valve 5
It is connected via 1 to the first fuel pressure accumulator and injection chamber 14a.

This check valve 50 has the _second internal pressure P ₂ of the first fuel pressure accumulating injection chamber 14a
When the pressure becomes higher than the residual pressure of the fuel pressure accumulating chamber 14b (for example, about 700 atm), the valve is opened to move from the first fuel pressure accumulating injection chamber 14a to the second
It is configured to allow the fuel to flow into the fuel pressure accumulating storage chamber 14b and prevent the backflow from the second fuel pressure accumulating storage chamber 14b to the first fuel pressure accumulating injection chamber 14a. In addition, the pressure setting valve
The valve 51 opens when the internal pressure P ₃ of the second fuel pressure accumulating chamber 14b rises above a predetermined residual pressure to open the flow of fuel between the second fuel pressure accumulating chamber 14b and the first fuel pressure accumulating chamber 14a. acceptable, so that the internal pressure P ₃ of the second fuel accumulator reservoir 14b is pressure P ₃ of the is reduced to a predetermined residual pressure second fuel accumulator reservoir 14b is opened so as not to fall below a predetermined residual pressure Made of

Now, as shown in FIG. 1, the injection control device has an injection start command valve 21 incorporated in the unit injector U.
Further, it is provided with an injection start decompression chamber 22 and an injection start command means 18 incorporated in the metering unit M.

The injection start command valve 21 is, as shown in FIG. 2 and FIG.
It has a valve chamber 28 and a spool 29 which are common to the inlet valve 10 of the fuel injection pump 6. That is, the injection start command valve 21 is provided with the injection start depressurizing passage 52 for communicating the pump chamber 9 and the valve chamber 28 below the outlet 34 of the inlet valve of the peripheral wall of the plunger 8.
And a valve groove 53 that is recessed over the entire circumference in the peripheral surface portion of the spool 29 below the inlet valve hole 33, and the inlet valve 10 that is lower than the top dead center of the spool 29 is opened and closed. When the spool 29 is positioned at a height within a predetermined range including the position of the spool 29, the injection depressurizing passage 52 and the valve groove
The 53 is communicated with and opened.

The injection starting decompression chamber 22 is provided between the inner peripheral surface of the plunger insertion hole 24 and the outer peripheral surface of the plunger 8 by recessing the outer peripheral surface of the peripheral wall portion of the plunger 8 facing the injection starting decompression passage 52. The pressure reducing passage formed in the peripheral wall portion of the plunger 8 facing the injection starting pressure reducing passage 52.
It communicates with the valve chamber 28 via 54. The injection start decompression chamber 22 communicates with the pump chamber 9 through the decompression passage 54, the valve groove 53 and the injection start decompression passage 52 when the injection start decompression passage 52 and the valve groove 53 communicate with each other. Like so. Further, the injection starting decompression chamber 22 is always communicated with the hollow portion 32 of the spool 29 via the minute passage 60 formed in the peripheral wall of the plunger 8 and the communication passage 61 formed in the peripheral wall of the spool 29. ing.

As shown in FIG. 1, the injection start command means 18 includes an inlet valve 10
Timing setting valve 19 and decompression chamber connected in sequence upstream of the
20 is provided, and the decompression chamber 20 is communicated with the upstream side of the inlet valve 10 when the timing setting valve 19 is opened at a predetermined crankshaft angle in conjunction with a crankshaft (not shown). . The timing setting valve 19 includes an advance control valve 19a for advancing or delaying the injection start timing according to the engine speed, and an advance control valve 1a within the advance range.
It is composed of a main timing setting valve 19b connecting the inlet valve 10 and the valve 9a. As shown in FIG. 1, the advance control valve 19a is composed of a pressure-reducing spool valve, and the spool valve element 72 is pushed up by the counterbalancing spring 73 to the retard angle side in the valve box 71. On the other hand, the fuel pressure in the hydraulic pressure working chamber 74 is pushed down and pressed toward the advance side, and is vertically moved to a position where the pushing down pressure and the pushing up elastic force are balanced. .

On the inlet side of the valve box 71, from the top, the retard side valve inlet 75
・ Intermediate timing valve inlet 76 ・ and advance side valve inlet 77 open,
A valve outlet 78 opens on the outlet side of the valve box 71. Spool disc
A spool valve body passage 79 is formed in 72 in a transverse shape. The spool valve body passage 79 has the retard side valve inlet 75 on the inlet side.
The intermediate timing valve inlet 76 and the advance side valve inlet 77 are selectively opened, whereas the outlet side is always communicated with the decompression chamber 20 via the valve outlet 78.

The hydraulic pressure working chamber 74 communicates with the outlet side of the pressure regulator 3 via a pressure communication passage 90. As the engine speed increases from low speed to medium speed to high speed, the pressure regulator 3
The fuel pressure on the outlet side of the valve goes from low pressure to high pressure through medium pressure, and the spool valve element 72 is at the operating pressure of the hydraulic pressure operating chamber 74, and from the upper retard position to the intermediate height position to the lower advance angle. The spool valve passage 79 is moved to the side position and communicates with the retard side valve inlet 75 through the intermediate timing valve inlet 76 to the advance side valve inlet 77.

The main timing setting valve 19b is composed of a rotary valve and has a valve box 8
The rotary valve body 89 is configured to rotate in the clockwise direction in conjunction with the crankshaft of the engine within 8.

A valve inlet 83 is opened at the inlet side of the valve box 88, and at the outlet side thereof, the advance side valve outlet 84, the intermediate timing valve outlet 85, And the retard side valve outlet 86 opens.

When the rotation angle of the crankshaft of the engine reaches the fuel injection start timing, the rotary valve body passage 87 of the rotary valve body 89 continues to communicate with the valve inlet 83 for a while at its inlet side, whereas it does not reach its outlet side. The advance side valve outlet 84, the intermediate timing valve outlet 85, and the retard side valve outlet 86 are sequentially communicated with each other.

The injection start command means 18 configured as described above is for closing the valve closing pressure chamber 12 by opening the rotary valve body 89 when the rotation angle of the engine crankshaft reaches the fuel injection start timing. By releasing the pressure P ₁ to the decompression chamber 20 via the inlet valve 10, the main timing setting valve 19b, and the advance control valve 19a,
The pressure P ₁ for closing the injection valve 15 of the pressure-accumulation fuel injector 7 is weakened, and the valve-opening pressure P 2 due to the fuel accumulation pressure in the fuel accumulation reservoir chamber 14 is opened to open the fuel accumulation pressure. The fuel accumulated in the storage chamber 14 starts to be injected from the injection port 16 into the combustion chamber.

In this way, by opening the rotary valve body 89, the injection valve
When opening 15 to start fuel injection,
First of all, when the engine is rotating at high speed, the fuel pressure at the outlet of the pressure regulator 3 becomes high, so that the pressure in the hydraulic pressure working chamber 74 becomes high and the spool valve body 72 is moved to the advanced position. It is pushed down to open the spool valve disc passage 79 to the advance side valve disc inlet 77.

Therefore, when the rotation angle of the rotary valve body 89 reaches an early timing in the variable region of the fuel injection start timing, that is, the advance timing, and the rotary valve body passage 87 is opened to the advance side valve outlet 84. Then, the valve closing pressure P ₁ of the valve closing pressure chamber 12 escapes to the pressure reducing chamber 20 via the rotary valve body passage 87, the advance side valve outlet 84, the advance side valve inlet 77, and the spool valve body passage 79. The pressure is reduced and the pressure is reduced. As a result, the fuel injection timing is advanced to the advance timing.

Secondly, on the contrary, when the engine is rotating at a low speed, the fuel pressure at the outlet of the pressure regulator 3 becomes low, so that the pressure in the hydraulic pressure operating chamber 74 becomes low and the spool valve element 72
Is pushed up to the retard position by the balance spring 73, and the spool valve body passage 79 communicates with the retard side valve inlet 75.

Therefore, the rotary valve body passage 87 cannot communicate with the spool valve body passage 79 when it first communicates with the advance side valve outlet 84, and cannot communicate with the spool valve body passage 79 when it reaches the intermediate timing valve outlet 85 next. And, the communication is established only when the retard side valve outlet 86 is reached. As a result, the fuel injection timing is delayed to the retarded timing.

And third, when the engine is rotating at medium speed,
By operating in the same manner as in the case of the low speed rotation, the fuel injection timing is adjusted and controlled to the intermediate timing.

Further, the injection start command means 18 includes a timing setting valve.
Exhaust return passage connecting decompression chamber 20 and inlet valve 10 in parallel with 19
55 is provided, and the discharge setting valve 19 that is once opened is shut off in the discharge returning passage 55, and a discharge returning valve 56 that is opened at a predetermined timing after the end of fuel injection is interposed.

A fuel supply valve 57 is interposed between the pressure feed pump 5 of the fuel supply system and the edge filter 27, and between the outlet of the pressure regulator 3 of the fuel supply system and the edge filter 27. An initial pressure adjusting pressure transmission path 58 that connects the outlet of the pressure adjusting device 3 to the upstream side of the edge filter 27 is connected in parallel with the pressure adjusting device 4, the pressure feed pump 5, and the fuel supply valve 57. An on-off valve 59 that is opened when the fuel injection ends and the fuel injection device returns to the initial state is interposed in the initial pressure adjusting pressure transmission path 58.

The fuel supply valve 57, the timing setting valve 19, and the discharge return valve 56 described above.
The on-off valve 59 and the on-off valve 59 may be provided separately, but since these valves are opened and closed by a predetermined crankshaft, they are configured as one combined timing control valve having a common rotary valve body linked to the crankshaft. It is possible to

Next, the operation of the fuel injection device will be described focusing on the operation of the unit injector U and the injection control device.

(A) Initial state In the initial state, the fuel supply valve 57, the timing setting valve 19, the discharge return valve 56, and the opening / closing valve 59 are all closed, and as shown in FIG. 2, the plunger 8 of the fuel injection pump 6 is closed. Is located at the top dead center, and the spool 29 is located at the bottom dead center. Therefore, the inlet valve 10 is opened and the injection start command valve 21 is closed. The check valve 13 is closed by the valve closing spring 13c, and the injection valve 15 is closed by the valve closing spring 43. Further, the check valve 50 and the pressure setting valve 51 of the fuel pressure accumulating chamber 14 are both closed.

Further, in the initial state, the space inside the valve opening pressure chamber 35, the valve closing spring chamber 41 and the cap 47, which communicates with the hollow portion 32 of the inlet valve 10.
48 of the internal pressure P ₀ ', the internal pressure P ₀ of the accumulator 36, the injection start decompression chamber 22
The internal pressure P ₄ is equal to the internal pressure P ₁ of the pump chamber 9 and the valve closing pressure chamber 12 of the pressure-accumulation fuel injector 7 and is equal to a predetermined initial pressure. The internal pressure P ₂ of the first fuel pressure storage chamber 14a on the downstream side of the check valve 13 is equal to the residual pressure at the end of injection (the internal pressure when the injection valve 15 is closed), and the internal pressure P 2 of the second fuel pressure storage chamber 14b. ₃ is the closing pressure of the pressure setting valve 51 (for example, 700 atm).

(B) Fuel supply stroke (fuel supply to the injection pump 6) The supply of fuel to the fuel injection pump 6 is started in FIG.
At a time point (hereinafter, simply referred to as time point a and the same applies to each time point shown in FIG. 4 thereafter), the fuel supply valve 57 is switched from the closed state to the open state, and the pressure pump 5 to the fuel injection pump 6 are switched.
The fuel whose pressure has been regulated and which has been regulated is pumped. This fuel is first pressed into the pressure accumulating chamber 36 via the inlet passage portions 30 and 31 and the hollow portion 32 to move the spool 29 to the top dead center side.

At engine startup, under full load or overload, the maximum injection amount of fuel is pumped from the pump 5 and the spool 29 is moved to top dead center.
Is moved to an intermediate position between the bottom dead center and the top dead center, and the fuel supply valve 57 is closed at time b when the injection of fuel into the fuel injection pump 6 is completed.

At this time point b, the internal pressure P ₁ of the pump chamber 9 and the internal pressure of the pressure accumulating chamber 36
Although P ₀ and pressure P ₀ of the valve-opening pressure chamber 35 that is against the internal pressure P ₀ of the accumulator 36 'is increased from the initial pressure, than the internal pressure P ₂ of the first fuel injection accumulator 14a low pressure Therefore, the check valve 13 cannot be opened.

(C) Fuel injection stroke (fuel injection into the pressure-accumulation fuel injector 7) From the subsequent time point c to time point i, the plunger 8 is pushed down from the top dead center by a cam (not shown). The internal pressure P ₁ of the pump chamber 9 and the internal pressure P ₀ of the pressure accumulating chamber 36 are further increased from the time point c, and the spool 29 is further raised to press the fuel into the pressure accumulating chamber 36 from the pump chamber 9 and eventually the spool 29 at the time point d. Is raised to a predetermined height near the top dead center and the inlet valve 10
Will be closed. After this time d, the internal pressure P _{1 of the} pump chamber 9 is increased until time i when the plunger 8 reaches the bottom dead center.
Is further increased, and the fuel in the pump chamber 9 is pressed into the pressure-accumulation fuel injector 7.

Here, since the volume of the pressure accumulating chamber 36 that is expanded from the time point a to the time point d when the inlet valve 10 is closed is made equal to the maximum injection amount, the pump chamber 9 can be used between the time point c and the time point d. Therefore, the amount of fuel injected into the pressure accumulating chamber 36 corresponds to the difference between the maximum injection amount and the fuel supply amount injected into the pressure accumulating chamber 36 from the time point a to the time point b. Further, since the volume of the pump chamber 9 which is reduced by moving the plunger 8 from the top dead center to the bottom dead center is equal to the maximum injection amount, after the time point d until the time point i when the plunger 8 reaches the bottom dead point. The amount of fuel injected into the accumulator fuel injector 7 from the pump chamber 9 is the maximum injection amount and c
It corresponds to the difference from the amount of fuel press-fitted from the pump chamber 9 into the pressure accumulating chamber 36 between time point e and time point e, that is, the fuel supply amount from the pressure feed pump 5.

In addition, the internal pressure of the injection start decompression chamber 22 from the time point a to the time point d is such that the injection start decompression chamber 22 is in the pump chamber through the minute passage 60, the communication passage 61 hollow portion 32 and the inlet valve 10 before the time point d. Since it is communicated with 9, the internal pressures P ₀ and P ₁ of the pressure accumulating chamber 36 and the pump chamber 9 that change relatively slowly change.

After the time point d, the internal pressure P ₁ of the pump chamber 9 and the valve closing pressure chamber 12 rapidly increases, and exceeds the internal pressure P ₂ of the first fuel pressure accumulating and storing chamber 14a from the time point e, the time point i when the plunger 8 reaches the bottom dead center. The check valve 13 is opened over, and the fuel is press-fitted into the first fuel pressure accumulation chamber 14a. Further, at the time h when the fuel pressure P ₁ (here, P ₂ ) from the pump chamber 9 to the first fuel pressure accumulating storage chamber 14a exceeds the set pressure of the pressure setting valve 51, the check valve 50 is opened and the check valve 50 is opened. Fuel is press-fitted from the first fuel pressure storage chamber 14a into the second fuel pressure storage chamber 14b.

The injection start command valve 21 is opened before the time point d, and
Since the inlet valve 10 is closed at this point, the internal pressure P _{1 of the} pump chamber 9
Injection start command valve 2 from pump chamber 9
1. A very small amount of fuel leaks into the hollow portion 32 of the spool 29 and the pressure accumulating chamber 36 through the injection starting pressure reducing chamber 22, the minute passage 60 and the communication passage 61, and this fuel causes the pressure accumulating chamber 36 and the hollow portion 32 to leak.
The internal pressure P ₀ is slightly increased, and the spool 29 is further pushed up from the position at the time point. The injection start command valve 21 is closed at a time point f shortly before the spool 29 reaches the top dead center. However, after this, the internal pressure P ₄ of the injection start decompression chamber 22 is changed to the internal pressure of the hollow portion 32 and the pressure accumulation chamber 36. The hollow portion 32 of the spool 29 is passed from the injection decompression chamber 22 through the minute passage 60 and the communication passage 61 until the same as P _0.
And the fuel in the accumulator 36 flows in. Due to this inflow, the spool 29 is pushed up to the top dead center.

The injection of fuel from the fuel injection pump 6 into the fuel injector 7 is completed at time i when the plunger 8 reaches the bottom dead center, and the check valves 13 and 50 are closed.

(D) Ignition fuel injection stroke At a predetermined time j after this, the timing setting valve 19 of the injection start command means 18 is opened and the decompression chamber 20 is connected to the upstream side of the inlet valve 10. Thereby, the hollow portion 32 of the inlet valve 10 and the accumulator chamber
The internal pressure of 36 is reduced, the spool 29 starts to descend from the top dead center, and the injection start command valve 21 is opened at time k when the spool 29 descends to a predetermined position slightly below the top dead center. The control delay time from the opening of the timing setting valve 19 to the opening of the injection start command valve 21 is the initial pressure of the decompression chamber 20 (timing setting valve
It becomes constant if the internal pressure before opening valve 19) is constant. By opening the injection start command valve 21, the pump chamber 9 and the valve closing pressure chamber
The internal pressure P _{1 of} 12 is suddenly released into the injection decompression chamber 22,
Internal pressure P _{2 of} the first fuel pressure accumulating chamber 14a (= P ₃ at this point)
Internal pressure P ₁ of the valve closing pressure chamber 12 and valve closing spring
When the valve closing force consisting of the urging force of 43 becomes weak, the injection valve 15
Is opened.

What should be noted here is that the injection start command valve 21 and the injection start pressure reducing chamber 22 are assembled in the plunger 8 of the fuel injection pump 6 so that they are sequentially connected to the valve closing pressure chamber 12 of the pressure accumulating fuel injector 7. The injection start command valve 21 and the injection start depressurization chamber 22 are arranged close to the valve closing pressure chamber 12 of the pressure accumulating fuel injector 7, and the distance from the valve closing pressure chamber 12 to the injection start depressurization chamber 22 is as long as possible. That is to be shortened. When the distance from the valve closing pressure chamber 12 to the injection start decompression chamber 22 is shortened in this way, the resistance of the flow path from the injection start command valve 21 to the injection start decompression chamber 22 becomes small, and the injection start command valve 21 opens. The pressure reduction gradient of the valve closing pressure chamber 12 after the valve can be made steep. As a result, the control sensitivity can be made sensitive, the range of variation in the valve opening start timing of the injection valve 15 can be reduced, and the control accuracy of the injection start timing can be improved.

The depressurization here is a decompression chamber for injection start, which has a relatively small volume.
Since the pressure is released to 22, the amount of fuel with which the internal pressure P ₁ of the valve closing pressure chamber 12 is depressurized is relatively small, and therefore the valve opening amount of the injection valve 15 is also suppressed to a small amount, and the fuel injection rate is small. It can be suppressed. When the internal pressure P _{1 of the} pump chamber 9 and the valve closing pressure chamber 12 and the internal pressure P ₄ of the injection start depressurization chamber 22 become equal, the injection start depressurization chamber 22 and the hollow portion 32 are communicated by the minute passage 60 and the communication passage 61. Therefore, these internal pressures P ₁ (= P ₄ ) are gradually reduced. On the other hand, the first fuel pressure accumulation chamber by fuel injection
The pressure reduction of the internal pressure P ₂ of 14a is more rapid than the pressure reduction of the internal pressure P ₁ of the valve closing pressure chamber 12, and the valve opening amount of the injection valve 15 is changed from the time point m when the difference between the valve opening force and the valve closing force becomes maximum. Decrease and eventually injection valve at time n
15 is once closed and fuel injection is interrupted. When the injection valve 15 is closed at time n, the pressure reduction of the first fuel pressure accumulating chamber 14a is stopped, while the fuel from the second fuel pressure accumulating chamber 14b flows in due to the communication of the pressure setting valve 51. The internal pressure P ₂ of the fuel pressure accumulating storage chamber 14a increases again.

(E) Main fuel injection stroke By the way, the internal pressure P ₀ of the hollow portion 32 of the inlet valve 10 and the pressure accumulating chamber 36 is continuously reduced until time j becomes equal to the internal pressure P ₀ of the pressure accumulating chamber 20. Then, the spool 29 is lowered almost independently of the fuel injection from the time point l to the time point n. When the spool 29 descends to a predetermined height lower than the top dead center, the inlet valve 10 is opened, and the pump chamber 9 and the valve closing pressure chamber 12 are decompressed via the inlet valve 10 and the timing setting valve 19. Connected to chamber 20. As a result, the pump chamber 9
Also, the internal pressure P ₁ of the valve closing pressure chamber 12 is sharply and significantly reduced, the injection valve 15 is suddenly and largely opened, and a large amount of high-pressure fuel is injected.

The injection start command valve starts at time j when the spool 29 starts descending.
The time from k to when 21 is opened and from j to the inlet valve
The time from when the valve 10 is opened to the time point o is from the inlet valve 10 to the decompression chamber.
It is constant because it is determined by the channel resistance up to 20. Further, the time from the time point k to the time point 1 at which the fuel injection is started is constant because it is determined by the flow path resistance from the valve closing pressure chamber 12 to the injection starting decompression chamber 22. Therefore,
The time from the time point l when the ignition injection starts to the time point o when the main injection starts becomes constant irrespective of the engine speed, and by setting this time equal to the ignition delay time, the injection by the ignition injection is performed. Ignition a small amount of fuel that has been ignited to prevent the generation of diesel knocks and reduce engine noise, and when the fuel injected by the ignition injection ignites, a large amount of fuel is injected by the main injection to increase You will be able to get the output.

After the inlet valve 10 is opened, the internal pressure P ₀ of the hollow portion 32 of the inlet valve 10 and the pressure accumulating chamber 36 is further reduced, and the spool 29 is o
It continues to decline after that time. Then, the injection start command valve 21 is closed at a time point p slightly after the time point o. After time point o,
The fuel injection pressure is the same as the internal pressure P ₂ of the first fuel pressure accumulating and storing chamber 14a, and is gradually reduced. Then, the pressure setting valve 51 is closed at the time point q when the internal pressure P _{3 of} the second fuel pressure accumulating chamber 14b is reduced to the setting pressure of the pressure setting valve 51, and the depressurization of the first fuel pressure accumulating chamber 14a after this time point q is reduced. It gets even sharper. The fuel injection rate is from the time point o to the time point q.
Although the high-pressure fuel flowing out from b is injected, it rises, but after the time point q, the internal pressure P _{2 in} the first fuel pressure accumulating chamber 14a decreases sharply and the fuel injection rate decreases. Then, r time after the valve opening force pressure P ₂ is reduced in the first fuel accumulator storage chamber 14a is equal to the closing force by the injection, the internal pressure P ₂ of the first fuel accumulator storage chamber 14a is further continued injection Therefore, the valve closing force becomes stronger than the valve opening force, and the injection valve 15 moves in the valve closing direction. Then, at the time s when the internal pressure P _{2 of} the first fuel pressure accumulating and storing chamber 14a is reduced to a predetermined residual pressure, the injection valve 15 is closed and the fuel injection ends.

The internal pressure P ₁ of the pump chamber 9 is rapidly and significantly reduced after the time point o when the inlet valve 10 is opened, and becomes the same as the internal pressure P ₀ of the hollow portion 32 within a short time. Also, the injection decompression chamber 22
The internal pressure P ₄ of the same is the same as the internal pressure P ₀ of the hollow portion 32 at the time point k, but when the injection start command valve 21 is opened at the time point k, it rises very rapidly and the pump chamber 9 It becomes the same as the internal pressure P ₁ . When the inlet valve 10 is opened at the time point o, the internal pressure P ₁ of the pump chamber 9 and the internal pressure P ₄ of the injection starting decompression chamber 22 suddenly fall, but the spool 29 becomes below a predetermined height and the injection starts. After the time point p at which the command valve 21 is closed, the communication between the injection start depressurization chamber 22 and the pump chamber 9 is cut off, so that the internal pressure P ₄ of the injection start depressurization chamber 22 is set to a small passage from now on.
Pressure is gradually released into the hollow portion 32 via 60 and the communication passage 61,
Eventually, the internal pressure of the injection starting decompression chamber 22 becomes the same as the internal pressures P ₀ and P ₁ of the hollow portion 32 and the pump chamber 9. At this time, in the pressure accumulating chamber 36, the maximum amount of injection plus the amount of fuel leaking from the pump chamber 9 to the pressure accumulating chamber 36 through the injection decompression chamber 22 or the like is added to the pressure reducing chamber 20 to depressurize the fuel. The amount of fuel corresponding to the amount obtained by subtracting the amount of is left, and the spool 29 is positioned higher than the bottom dead center.

(F) Return stroke to initial state Internal pressure of the injection decompression chamber 22, hollow 32 and pump chamber 9
The plunger 8 of the fuel injection pump 6 starts to rise at a predetermined time t after P ₀ , P ₁ and P ₄ become the same, and fuel is sucked from the pressure accumulating chamber 36 into the pump chamber 9 as the plunger 8 rises. .

However, as described above, the amount of fuel stored in the pressure accumulating chamber 36 at time t is the maximum amount of fuel that is the amount of fuel leaking from the pump chamber 9 to the pressure accumulating chamber 36 via the injection starting pressure reducing chamber 22 or the like. The amount corresponds to the amount obtained by subtracting the amount of fuel depressurized in the decompression chamber 20, and is insufficient to raise the plunger 8 to the top dead center. Therefore, the discharge return valve 56 is considered to be required from time u to time v when the plunger 8 should reach the cam base of the cam, that is, from time u to time v.
The valve 8 is opened and the fuel depressurized in the pressure reducing chamber 20 is discharged back to the pressure accumulating chamber 36, whereby the plunger 8 is surely returned to the top dead center. Further, when the plunger 8 is returned to the top dead center at time v in this way, the pressure reducing chamber 20 to the pump chamber 9
During this period, the fuel corresponding to the amount leaked from the pump chamber 9 to the pressure accumulating chamber 36 via the injection starting pressure reducing chamber 22 and the like is excessively confined, so these internal pressures are at time v. Is higher than the initial pressure. So v
By opening the opening / closing valve 59 for adjusting the initial pressure from the predetermined time point w to the time point x after the time point, these internal pressures are reduced to the initial pressure. It should be noted that in the overall operation of the above pressure accumulating fuel injection device, during the list down process of the fuel injection cam (time tv during the return process (F) to the initial state of FIG. 4), the fuel injection cam If there is a gap between the fuel injection cam and the plunger 8, the fuel injection cam will be removed at the next fuel injection cam listing step (time point c-i during the fuel injection step (C) in FIG. 4). The impact with the plunger 8 causes adverse effects such as noise and early wear and deformation.

In order to eliminate this adverse effect, the fuel injection cam and the plunger 8
A gap is not formed between the two, and for this reason, one cycle of the plunger operation will be described below based on the order of each stroke shown in FIGS. 7 (A)-(D).

(A) Initial state See FIG. 7 (A) In this initial state, the spool 29 is located at the bottom dead center D ₂ and the plunger 8 is located at the top dead center U ₁ . The inlet valve 10 is opened, the fuel supply valve 57 is closed, and the check valve 13 is pushed and closed by the internal pressure of the fuel pressure accumulation chamber 14.

The maximum ejection amount V ₀ which the fuel injection pump 6, the maximum volume V ₀ which valve-closing accumulator 36, are set to be equal values.

(B) Fuel Supply Process Refer to FIG. 7 (B) The fuel is supplied by the metering unit M in a metered supply amount V ₁ in accordance with the load of the engine.

When the fuel supply valve 57 opens, the metering supply amount V ₁ of the fuel is pushed into the valve closing pressure accumulating chamber 36 from the metering unit M, and the spool 29 moves from the bottom dead center D ₂ to the top dead center U _2. It is pushed up toward halfway.

(C) Invalid discharge stroke See FIG. 7 (C). After the fuel supply valve 57 is closed, the fuel injection cam 80 enters the lift-up stroke 81 and pushes down the plunger 8. Through the valve 10, the ineffective discharge amount V _{2 is} press-fitted into the valve-closing pressure accumulating chamber 36. At this time, the check valve 13 is closed by the internal pressure of the fuel pressure storage chamber 14.

The fuel in the valve-closing pressure accumulating chamber 36 reaches the maximum volume V ₀ together with the metering supply amount V ₁ that had been contained in the fuel when the ineffective discharge amount V ₂ is completely injected. This allows the spool 29
Rises to the top dead center U ₂ , the internal pressure of the valve closing pressure accumulating chamber 36 rises to the valve closing pressure, and the inlet valve 10 is pushed and closed.

The fuel of the effective discharge amount V ₃ remaining in the pump chamber 9 is the maximum discharge amount.
An amount obtained by subtracting the invalid ejection amount V ₂ from V _0, equal to the maximum volume V ₀ disables the ejection amount V ₂ metering the amount V ₁ of minus from the valve-closing accumulator 36.

(D) Effective discharge stroke Refer to FIG. 7 (D) When the plunger 8 is further pushed down to reach the bottom dead center D ₁ , the effective discharge amount V ₃ (= metering supply amount in the pump chamber 9)
The fuel of V ₁ ) is pressed into the fuel pressure accumulating storage chamber 14 through the check valve 13.

Thereafter, the effective discharge amount V ₃ of fuel is injected from the pressure accumulation type fuel injector 7 into the combustion chamber.

(E) Plunger return stroke See FIG. 7 (A) When the main timing setting valve 19b in the metering unit M is opened for a short time, the internal pressure of the valve-opening accumulator chamber 36 is slightly different from this main timing setting valve 19b. Unplugged into the inlet valve 10
Is pushed open by the elastic force of the valve opening pressure chamber 35.

When the fuel injection cam 80 enters the lift-down stroke 82, the fuel having the maximum volume V ₀ stored in the valve closing pressure accumulating chamber 36 passes through the inlet valve 10 by the elastic pressure of the valve opening pressure chamber 35 and the pump chamber 9 Is pressed into. As a result, the spool 29 is returned from the top dead center U ₂ to the bottom dead center D ₂ , and the plunger 8 is pressed against the fuel injection cam 80 while being returned from the bottom dead center D ₁ to the top dead center U ₁ to make contact. Therefore, there is no gap between the plunger 8 and the fuel injection cam 80.

Therefore, the lift-up stroke 81 of the next fuel injection cam 80
At the time point (c-i in FIG. 7 (C) = FIG. 4), the fuel injection cam 80 does not collide with the plunger 8.

This completes one cycle of the operation of the plunger 8.

<Embodiment 2> FIG. 5 is a vertical cross-sectional view of a main portion of another embodiment of the present invention.

In this embodiment, the injection start command valve 21 is composed of a double spool valve incorporated in the plunger 8. That is,
A child spool 62 is fitted in the lower end portion of the spool 29 so as to be able to move up and down, and the child spool 62 has a through hole 63 whose diameter is reduced at the lower end portion.
And a valve hole 64 formed so as to face each other on the peripheral wall of the large diameter portion of the through hole 63. A valve groove 53 of the injection start command valve 21 is formed on the outer peripheral surface of the peripheral wall of the reduced diameter portion of the through hole 63 over the entire circumference. On the other hand, on the peripheral wall of the lower end of the spool 29, a pair of valve holes 65, 6 communicating with the valve groove 53 when the child spool 62 rises to the top dead center.
6 is formed, and the spool 8 is formed on the plunger 8 when the spool 29 is located at a predetermined range of height slightly lower than the top dead center.
Injection-starting depressurization passages 52, 54 are formed so as to communicate with the 29 valve holes 65, 66, respectively. The other structure is the same as that of the above-described embodiment, and the description thereof is omitted.

In this embodiment, when the timing setting valve 19 of the valve opening start command means 18 is opened to start depressurizing the hollow portion 32, the fuel in the pressure accumulating chamber 36 is sucked out to the depressurizing chamber 20 through the through hole 63. Is
Although the spool 29 descends, since the through hole 63 has a reduced diameter portion, a pressure difference is generated between the pressure accumulating chamber 36 and the hollow portion 32, and the child spool 62 is raised at the same time when the spool 29 descends. Then, when the child spool 62 reaches the top dead center, the injection start depressurizing passages 52, 54 of the plunger 8, the spool 29, 65, 66 and the valve groove 53 of the child spool 62 communicate with each other to open the injection start command valve 21. When the valve is valved, the pump chamber 9 communicates with the injection start depressurizing chamber 22, and the internal pressures of the pump chamber 9 and the valve closing pressure chamber 12 are reduced.

The other operations are the same as those in the above-described embodiment, and thus the description thereof will be omitted.

[Brief description of drawings]

FIG. 1 is an equivalent circuit diagram of a pressure-accumulation fuel injection device for a diesel engine according to the present invention, FIG. 2 is a vertical sectional view of a unit injector used in the fuel injection device in an initial state, and FIG. FIG. 4 is a longitudinal sectional view of the main part of the unit injector when the command valve is opened, FIG. 4 is a timing diagram for explaining the operation of the unit injector and the injection start command means, and FIG. 5 is another embodiment of the present invention. FIG. 6 is a longitudinal sectional view of the essential part of FIG. 6, and FIG. 6 is an equivalent circuit diagram of the prior invention. FIGS. 7A to 7D are diagrams showing the operation sequence of the plunger 8. 6 ... Fuel injection pump, 7 ... Accumulation type fuel injector, 9 ...
… Pump chamber, 10 …… Inlet valve, 11 …… Fuel inlet, 12 …… Closed pressure chamber, 13 …… Check valve, 14 …… Fuel pressure storage chamber, 15 ……
Injection valve, 16 ... Injection hole, 18 ... Injection start command means, 19 ...
… Timing setting valve, 20 …… Decompression chamber, 21 …… Injection start command valve, 22 …… Injection start decompression chamber, 29 …… Valve element, 35 …… Valve opening pressure chamber, 36 …… Valve closing chamber , 43 …… Valve closing spring.

Claims (1)

[Claims] 1. A pressure-accumulation type fuel injector for a diesel engine is provided with a pressure-accumulation type fuel injector (7) and a fuel supply system for supplying fuel thereto, and the fuel supply system is pressure-regulated and metered. A fuel injection pump (6) for injecting the injected fuel into the pressure-accumulation fuel injector (7),
And an inlet valve (10) for opening and closing the inlet side of the fuel injection pump (6).
Fuel inlet (11) communicating with the pump chamber (9) of the valve, the valve closing pressure chamber (12), the check valve (13), the fuel pressure accumulating chamber (14), and the injection valve (15) that are sequentially connected to the fuel inlet (11). And an injection hole (16) and a valve closing spring (43). The injection valve (15) is biased to open by the internal pressure of the fuel pressure accumulating chamber (14) while the valve closing spring (43) is closed. ) And the internal pressure of the valve closing pressure chamber (12), the fuel injection pump (6) is pushed by the plunger (8) into the pump chamber (9). The fuel inlet (1
1), after press-fitting into the fuel pressure storage chamber (14) through the valve closing pressure chamber (12) and the check valve (13), the internal pressure of the valve closing pressure chamber (12) is depressurized at a predetermined timing. Thus, in the injection control device of the accumulator fuel injection device for a diesel engine, the valve closing biasing force of the injection valve (15) is made weaker than the valve opening biasing force to open the injection valve (15). , The valve closing pressure chamber (12) of the pressure accumulating fuel injector (7) is sequentially connected to the injection start command valve (21) and the injection starting decompression chamber (22), which are arranged close to the valve closing pressure chamber (12), The injection start command valve (21) is connected to the fuel injection pump (6) and the valve closing pressure chamber (12) via the inlet valve (10), and the injection start command valve (21) and the inlet valve ( 1
The pressure receiving chamber (36) for urging the valve body (29) of (0) to close and the valve opening pressure chamber (35) for urging the valve body (29) to open are provided, and the injection start command valve ( 21) is provided with an injection start command means (18) for opening the valve at a predetermined injection start time, and the injection start command means (18) supplies fuel from the fuel injection pump (6) to the pressure accumulation type fuel injector (7). A timing setting valve (19) opened at a predetermined time point after press fitting and a decompression chamber (20) communicating with the pressure receiving chamber (36) via the timing setting valve (19) are provided. The timing setting valve (19) is linked to the crankshaft of the engine, and by opening the timing setting valve (19), the pressure receiving chamber (36) communicates with the decompression chamber (20), and the internal pressure of the pressure receiving chamber (36) is increased. The injection start command valve (21) is opened by depressurizing the
The pressure-accumulation fuel injection device for a diesel engine, characterized in that the valve is opened by the internal pressure of 5) and the internal pressure of the valve closing pressure chamber (12) is released into the decompression chamber (22) for injection start. Injection control device.