JPS58222925A - Distributor type fuel injection device - Google Patents

Abstract

PURPOSE:To control an injection quantity in accordance with an operational condition, by providing an injection start spill ring and an injection end spill ring to a distributor type injection pump of inner cam type and controlling overflow timing. CONSTITUTION:An electronic controller 19 calculates an accurate injection quantity corresponding to an operational condition to feed a driving signal to a hydraulic control unit 12 and a rotor solenoid 16. A distributing member 2 is moved in the shaft direction by opening and closing a solenoid valve 12a of the unit 12, and the relation of a relative position between a spill port 9a of a spill ring 9 and a spill port 21 is controlled then injection start timing is controlled. While a spill ring 10 is independently controlled by the rotary solenoid 16, and the relation of a relative position between a spill port 10a and a spill port 22 is controlled, then injection end timing is controlled.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a distributed fuel injection device used in an engine, and more particularly to an inner cam type distributed fuel injection device that has a rotary pump member with a pump plunger provided radially inside an inner cam. Zuru.

In a conventional inner cam type fuel injection device, which has a rotary pump member with a pump plunger radially inside the inner cam and a distribution member connected to the rotary pump member, the distribution member performs only rotational movement to distribute fuel to each distribution passage. Because of this configuration, overflow adjustment control that controls the overflow amount by controlling the position of the spill ring cannot be performed, and the fuel injection amount is not controlled by this overflow method.

The present invention focuses on the above points, and controls the vortex timing by providing an overflow metering control device to an inner cam type distribution type fuel injection pump having a rotary pump member with a pump plunger provided radially inside the inner cam. It is an object of the present invention to provide a distribution type fuel injection port 4 device that can control a fuel injection amount suitable for the operating condition of an engine. To this end, the present invention connects a distribution member to a rotary pump member having a pump plunger at variable connection intervals, and provides a spill ring for secondary injection start control and a spill ring for injection end control on the outer periphery of a spill boat of the distribution member. A hydraulic control unit is fitted onto the outside and applies hydraulic pressure to the connection gap between the pump member and the distribution member to control the axial position of the distribution part I, and a rotary solenoid is provided to control the rotational angular position of one spill ring. It is characterized by an electronic control device that controls the timing of overflow from the spill boats of the two spill rings by operating a hydraulic control unit and a rotary solenoid based on detected data of engine rotational speed and load amount. shall be.

Embodiments of the present invention will be described below based on the drawings.

FIG. 1 shows a schematic cross-sectional iIδ configuration diagram of an inner cam type distribution type fuel injection device, and is a 111-rotation pump member,
It is connected to a drive shaft (not shown) and is driven to rotate at 172 rotations of the engine rotation speed. An inner cam member (not shown) is provided as a fixed part on the outer periphery of the rotary pump member 1, and inside the inner cam member there are pump plungers ia and 1b arranged radially, which rotate around a drive shaft. A reciprocating motion of the pump plunger in the direction of arrows A and A in the figure is based on a change in the contact position between the pump plungers 1a and 1b and the inner cam member. As a result, fuel is sucked and compressed into the pressure chamber 3. An axial passage 3a communicates with the pressure chamber 3 so that fuel pumped into the pump chamber by a feed pump (not shown) is sucked in through the suction port 4. Further, this passage 3a sends fuel by the compression force applied to the pressure chamber 3 by the compression movement of the pump plungers 1a and 1b to the introduction port 7a of the distribution member 2, which will be described later, via the pressure passage 5 and the check valve 6. The distribution member 2 is rotatably and slidably supported by a support member 24 and connected to the rotary pump member 1 . The connecting portion is connected to a diagonal groove 23 bored on the outer periphery of the distribution member 2 by a piece-shaped connecting arm 15 on the rotary pump member 1 side.
A connecting gap 11 is created between the distribution member 2 and the rotary pump member 1. Reference numeral 12 denotes a hydraulic control unit that controls the hydraulic pressure in the connection gap 11, and a solenoid valve 12a is provided in the hydraulic pressure supply path 25, and the solenoid valve 12a is opened and closed at a timing determined by a control signal from an electronic control device 19, which will be described later. determining the oil pressure level in the gap 11;
The pressing force applied to the distribution member 2 in the right direction in FIG. 1 is adjusted. When a pressing force is applied to the distribution member 2, the distribution member 2 slides in the right direction while maintaining connection with the connecting arm 15 at the diagonal 23, and at the same time, when viewed from the right side in the figure to the left side, the distribution member 2 moves in the direction of downward movement. and is held in a position that balances the resistance of the spring 14 in the chamber 13.

A distribution boat 1-7b1 communicating with the fuel introduction boat 7a and spill boats 21 and 22 are provided in the distribution member 2, and the distribution boat 1-7b is formed on the support member 24 and has a length of one column.
i! A spill ring 9 is disposed so as to communicate with the passage 26, and a spill ring 9 is fitted around the spill boat 21 so as to allow the distribution member 2 to slide and cover it. 10 is similarly slidably fitted on the outside. The spill ring 9 is used for controlling the start of injection, and spill ports 1-98 are bored on the inner surface of the spill ring 9. On the other hand, the spill ring 10 is used for controlling the end of injection, and a spill boat 10a is formed on the inner surface of the spill ring 9. is drilled. The spill ring 10 is disposed so as to cover the tip of the distribution member 2, and the distribution member 2 is placed in a chamber 13 formed by the spill ring 10 and the distribution member 2.
A coil spring 14 is provided which is always biased in the direction. Further, a rotary solenoid 16 is connected to the spill ring 10, and its rotation angle position is controlled by the rotary solenoid 16. Reference numeral 8 designates a delivery valve installed in the distribution passage 26, the output side of which is connected to a fuel injection nozzle (not shown). Reference numeral 17 indicates a position sensor for detecting the rotational angle of 1 m of the spill ring 10, and reference numeral 18 indicates a position sensor for detecting the axial position of the distribution member 2, each of which outputs a detection signal indicating the position to the electronic control unit 19. .

The electronic control device 19 inputs signals indicating the engine rotation speed and load from a rotation sensor and an engine load sensor (for example, a throttle opening sensor) (not shown), and receives various information from the position sensors 17 and 18. Based on these data, the hydraulic control unit 12 and rotary solenoid 16 are operated to control the timing of fuel overflow so that the appropriate amount of fuel corresponding to the operating state of the engine is injected at the appropriate timing. It consists of a microprocessor, a memory for storing constants for various calculations and map data, and the like. In addition, the spill ring 10 (J) is provided on the inner surface of the spill ring 10 (J) in FIG.
By tilting the distribution member 2 so that it has the same inclination as @23, the spillover 1 can be prevented even by the movement of the distribution member 2.
The relative positional relationship between Mi 22 and spill boat 10a remains unchanged, and spill rings 9 and 10 can be controlled independently. In addition, as shown in Figure 3, the spill ring 10
When the spill port 101) is parallel to the axis and not tilted, the deviation between the spill port 22 and the spill port 101) due to the movement of the distribution member 2 can be corrected by the calculation processing of the electronic control unit 19.

Next, the operation of the 17J fuel injection device #1 will be explained.

As the rotary pump member 1 rotates at half the rotational speed of the engine, the pump plungers 1a and 1b reciprocate according to the profile of an inner cam (not shown), and as a result, the fuel pumped from the feed pump (not shown) is The prefushi 11 is sucked into the yamba 3 and compressed. This compressed fuel passes through the pressure feeding passage 5, passes through the check valve 6, and then passes through the introduction boat 7a of the rotating distribution member 2.
When it matches the pressure feeding port on the support member 24 side, the introduction bow]・7a
and into the distribution member 2. Then, the distribution boat 7b of the distribution member 2 is fitted into one of the distribution passages 26 provided in the same number as the cylinders of the engine, and the high-pressure fuel is passed from the distribution boat 7b through the distribution passage 26 and the delivery valve 8. The fuel is then force-fed to an injection nozzle (not shown), and at this time, the overflow timing is controlled by the action of the distribution member 2 and the spill ring 9, 10, and the fuel injection Itl and timing are controlled. Therefore, the electronic control unit 19 sends a drive signal to the hydraulic control unit 12 and the rotary solenoid 16.
Spill ring 9 due to change in rotational angular position of distribution member 2
Relative inner position tF of spill port 9a and spill port 21
7. By changing the relationship, the compression start timing is controlled, and by changing the rotation angle of the spill ring 10 (spill bow due to change in position) -22 and the relative positional relationship between the spill bow l-10a, E compression is completed. Controls timing. That is, the electronic control device 19 controls one rotation sensor from a rotation sensor (not shown).
- Inputs a signal N indicating the engine rotation speed, inputs a signal α indicating the amount of engine load from an engine load sensor (for example, an accelerator sensor), and determines an appropriate injection amount and injection timing from these data. When controlling the compression start timing based on this calculated data, a control drive signal is sent from the electronic control unit 19 to the hydraulic control unit 12, and different hydraulic pressures are distributed by opening and closing the solenoid valve 12a. The distribution member 2 is moved in the axial direction by applying a voltage to the tip of the member 2 to change the width of the connecting gap. Then, when the distribution member 2 simultaneously moves to the right in FIG. 1, the distribution member 2 rotates clockwise when viewed from the right side, and when it moves to the left, it rotates counterclockwise to change its angular position. Therefore, Spieling 9's Spielbo i~9
The relative positional relationship between a and the spillover 1-21 is controlled in the advance or lag direction, and the compression start timing is thereby controlled. On the other hand, at this time, Spilling 1 to 1 of Spilling 10
Although the positional relationship between 0a and the spill port 22 of the distribution member 2 also changes, the rotary solenoid 16 is actuated by the control drive signal from the electronic control device 19, and the rotational angular position of the spill ring 10 is independently controlled. The relative positional relationship between 108 and 22 is to create a corresponding compression end timing in order to put the calculated injection interval to practical use:
controlled by sea urchins. While such control is being carried out, the position sensor 17 detects the rotation angle position of the rebuild ring 10, the position sensor +3-18 detects the axial position of the distribution member 2, and these data are (Then, the angle f of the spill ring 10 is sent to the electronic control unit 19.
☆The position data is used for control as is, and the position data of the distribution member 2 is stored as a map in the memory of the electronic control unit 19.The axial position and circumferential movement of the distribution part port 2 are The angle of movement of the distribution section 142 in the circumferential direction is changed and used based on the data indicating the relationship between the angles.

FIG. 2 shows the pump plunger rla of the rotary pump member 1,
, 1b is a timing chart showing the timing B1 of the overflow timing by the spill ring 9 and the timing C of the overflow timing by the spill ring 10 with respect to the pressure waveform created by , 1b. According to this figure, at time A when the pump enters the compression stroke, overflow by the spill ring 9 ends and compression begins, and overflow by the spill ring 10 begins at the timing opening just before the compression top dead center, causing compression. ends.

Therefore, the period A and the opening are the compression period, that is, the injection period, during which high-pressure fuel is sent from the distribution passage 26 to the injection nozzle via the delivery valve 8.

FIG. 4 shows another embodiment of the invention, in which:
The connecting portion between the rotary pump member 31 and the distribution member 32 has a structure in which the distribution member 32 simply moves only in the axial direction by changing the connection gap. Furthermore, the distribution member 32
As shown in FIG. 5, the spill ring 33 for controlling the compression start timing, which is precisely fitted on the outside, is provided with a diagonal lead-shaped groove 35, and when the distribution member 32 moves in the axial direction, the spill ring 33 is connected to the spill boat 34. Relative positional relationship tj1 of groove 35
, can be changed in the same way as the embodiment shown in FIG. 1, and the compression start timing can be controlled in the same way as in the previous embodiment.

In the embodiments shown in FIGS. 1 and 4, the compression start timing is controlled by the spill ring 9 or 33, and the compression end timing is controlled by the spill ring 10. However, by reversing these relationships, the spill ring 9 Alternatively, the compression end timing can be controlled by 33, and the compression start timing can be controlled by spill ring 10.

As described above, according to the inner cam type distribution type fuel injection device of the present invention, the rotary pump member and the distribution member are separated, and the two spills fitted on the distribution member are separated by moving the distribution member in the axial direction. Since the configuration is configured so that the compression (injection) start timing and compression (injection) end timing can be controlled using the ring, the overflow amount can be controlled and the amount of fuel 113 can be controlled appropriately according to the operating condition of the engine. I can do what I want to do.

[Brief explanation of the drawing]

The figures show an embodiment of the present invention, and Fig. 1 is a schematic cross-sectional configuration diagram of a distributed fuel injection device, Fig. 2 is a timing chart showing the timing of overflow, Fig. 3a, Fig. A perspective view of the spill ring 10, FIG. 4 is a schematic sectional view of an injection device of another embodiment, and FIG. 5 is a perspective view of a spill ring 33 of the same device. 1... Rotary pump member 1a, lb... Pump plunge 11 2... Distribution member 9.10... Spill ring 9a, 10a... Spill boat 11... Connection gap 12... Hydraulic control Part 16...Rotary solenoid 19...Electronic control device agent Patent attorney Tsutomu Adachi

Claims (1)

[Claims] A distribution type fuel comprising a rotary pump member equipped with a pump plunger that is slidable and radially arranged on the inner peripheral surface of an inner cam, and a distribution member that is connected to the rotary pump section 4A with a variable connection gap. In the injection device, a spill ring for starting injection and a spill ring for ending injection are slidably fitted on the outer periphery of the spill port of the distribution member, and hydraulic pressure is applied to the connecting gap. A hydraulic control unit is provided to control at least the axial position of the distribution member by applying a hydraulic pressure, and a rotary solenoid is connected to one of the spill rings to control the rotational angular position of the spill ring. The distribution system is characterized in that it is equipped with an electronic control device that operates the hydraulic control section and the rotary solenoid based on the load detection data 114 to control the timing of the swirling flow from the spillovers 1 to 1 of the two spill rings. Type fuel injector.