JPH07332191A - Distribution type fuel injection pump - Google Patents

Abstract

PURPOSE:To provide a distribution type fuel injection pump which facilitates suction of the fuel into a compression chamber.and movement of a plunger, acknowledges the position of a control sleeve with reference to the position of a cam ring, and can control the pressure feed effective stroke with a high accuracy. CONSTITUTION:The inside of a housing is partitioned into a chamber 7, at which a suction port 32 and a cut-off port 33 are open, and a low pressure side chamber 6 where a cam ring 25 is installed, and a control sleeve 26 furnished in such a way as enclosing the suction port 32 and cut-off port 33 is arranged as ranging over the low pressure side chamber 6 and the chamber 7. The control sleeve 26 is located in relation to the cam ring 25, consisting for example of a phase sensor 44, and it is possible to directly acknowledge the phase shift between the cam ring 25 and control sleeve 26.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an inner cam type distribution type fuel injection pump used for supplying fuel to an engine such as a diesel engine, that is, a rotary member synchronized with the engine having a plunger in its radial direction. The present invention relates to a reciprocating type fuel injection pump.

[0002]

2. Description of the Related Art An inner cam type distribution type fuel injection pump is disclosed, for example, in Japanese Patent Laid-Open No. 59-110835.
Pages, pages 4, 4 and 1 and 7 are known. That is, in the fuel chamber 121 (chamber), the concentric inner cam ring 1 is arranged around the fuel distribution rotary member 4 (rotary member), and the rolling element 23 is provided on the cam surface formed inside the inner cam ring 1. 24 (roller), pressure feed plunger 2 through shoes 25, 26
1 and 22 are applied, and the pressure-feeding plungers 21 and 22 are
Are reciprocated in the radial direction of the fuel distribution rotary member 4. The fuel delivery rotary member 4 includes a pressure feed plunger 2
Pump chamber 2 (compression chamber) whose volume changes by 1 and 22
And a suction hole 5 for sucking fuel into the pump chamber 2 during the suction process.
1 to 54, a distribution port 6 for delivering the fuel pressurized in the pump chamber 2 during the pressure feeding process, and overflow ports 71 to 74 for cutting off the fuel delivery are formed.
A ring-shaped member 7 (control sleeve) is oil-tightly fitted so as to cover 1 to 74. The slanted lead groove portion 10 for cutoff is formed on the inner surface of the ring-shaped member 7, and the linear solenoid 81 adjusts the axial position of the ring-shaped member 7 so that the cut-off timing during the pressure feeding step ( The overflow port opens to the oblique lead groove portion and the timing at which the compressed fuel flows out into the fuel chamber 121) can be changed to change the fuel injection amount (first prior art).

[0003]

According to the present inventor, in the fuel injection pump of this type, the fuel intake port and the cut-off port are filled with the fuel pressurized by the feed pump. The pressure around the plunger, such as rollers and shoes, is lower than the pressure inside the chamber, and the pressure acting on both ends of the plunger is made different to facilitate the intake of fuel into the compression chamber. In addition, it has been found that it is desirable to move the plunger outward by this pressure difference.

In order to realize this, as shown in FIG. 8 (a), the periphery of the ports A and B for inhaling and cutting off the fuel is drawn from the space where the rollers C and shoes D are arranged. However, in the case where the control sleeve E for adjusting the cutoff timing is rotationally controlled in the circumferential direction of the rotary member F, when controlling the fuel injection amount, the position of the control sleeve E and , A timer piston I of a timer device H for controlling the position of the cam ring G
And the position sensor are respectively detected by a position sensor, and the output difference between them is calculated to determine the fuel pressure feed effective angle (pressure feed effective stroke) (corresponding to − in FIG. 8B), and the required pressure feed effective stroke is obtained. It is conceivable to correct it.

However, in the case of controlling by each sensor output, sufficient accuracy cannot be obtained due to variations in detection accuracy of individual sensors, calculation speed by the control unit, etc., and variations in fuel injection amount occur. . If the control sleeve is provided in the low-pressure side chamber where the rollers and the like are arranged in order to detect the phase of the control sleeve with respect to the cam ring, it becomes difficult to suck fuel into the compression chamber and move the plunger. .

In view of this, in the present invention, it is possible to facilitate the intake of fuel into the compression chamber and the movement of the plunger, and to accurately recognize the position of the control sleeve in relation to the position of the cam ring to obtain a highly accurate effective feeding stroke. An object of the present invention is to provide a distributed fuel injection pump that can be controlled by.

[0007]

As a result of various researches on an inner cam type fuel injection device, the present inventor has found that a chamber in which a port for injecting fuel and a port for cutting off are opened, and a low-pressure side chamber in which a cam ring is arranged. In such a configuration, it is desirable that the position of the control sleeve and the position of the cam ring are directly associated with each other by some means, and the present invention has been completed from this point of view.

That is, the distributed fuel injection pump of the present invention varies the volume of the rotary member that rotates in synchronization with the engine and the compression chamber that is provided in the radial direction of the rotary member and that is formed in the rotary member. A plunger and a cam ring that is concentrically provided around the rotating member and defines the movement of the plunger are provided in the housing, and a port that communicates with the compression chamber to suck, deliver, and cut off fuel is provided in the rotating member. In the distributed fuel injection pump formed in FIG. 1, a low-pressure side chamber formed in the housing from a fuel inlet to an upstream side of a feed pump, and fuel pressurized by the feed pump are introduced to suck the fuel. , Defined as a chamber that can communicate with the port to be cut off,
A control sleeve, which is provided so as to cover the suction and cutoff ports and controls the communication timing of these ports with the chamber, is rotatably fitted on the rotary member, and the control sleeve is attached to the low pressure side chamber and the low pressure side chamber. And means for providing the position of the control sleeve in association with the position of the cam ring by associating the movement of the control sleeve and the movement of the cam ring with each other. There is (claim 1).

Here, even if the movement of the control sleeve and the movement of the cam ring are associated with each other by detecting the phase shift between the control sleeve and the cam ring (claim 2), the actuator for controlling the drive of the control sleeve may be associated. May be fixed to the cam ring (claim 3).

In order to improve the control accuracy of the effective feeding stroke, it is desirable that the cutoff port and the hole formed in the control sleeve that can communicate with the cutoff port be formed as parallel slits extending in the axial direction of the rotary member. (Claim 4).

[0011]

Therefore, according to the present invention, the interior of the housing is divided into the low pressure side chamber and the chamber, the low pressure side chamber is provided with the cam ring, the shoe, and the roller, and the chamber is provided with the suction port and the cutoff port. Since it is possible to communicate with each other, a pressure difference can be formed inside and outside the rotating member, fuel can be easily sucked in the suction process, and movement of the plunger to the outside can be secured. And
Since the movement of the cam ring and the control sleeve provided over both the chamber and the low pressure side chamber can be directly related, if the effective pumping stroke is managed based on this information, the position of the control sleeve and the cam ring can be controlled. The position does not have to be detected by the sensor separately.

In particular, according to the second aspect of the invention, it is not necessary to separately detect the position of the control sleeve and the position of the cam ring to calculate the phase shift, and the configuration of the third aspect. In this case, the reference position of the control sleeve with respect to the cam ring is always constant, so that the effective feeding stroke can be easily and accurately controlled.

If the cutoff port and the hole of the control sleeve which can communicate with the cutoff port are formed by parallel slits, the timing of communication between the cutoff port and the hole is determined only by the rotation angle. The cutoff timing can always be accurately controlled despite the temporary axial displacement of the rotary member and the temporal displacement due to wear.

[0014]

Embodiments of the present invention will be described below with reference to the drawings.

In FIG. 1, an inner cam type distribution type fuel injection pump is shown. In the distribution type fuel injection pump 1, a drive shaft 3 is inserted into a pump housing 2 and the drive shaft 3 is provided.
One end of the pump protrudes to the outside of the pump housing 2, receives a driving torque from an engine (not shown), and rotates in synchronization with the engine. The other end of the drive shaft 3 extends into the pump housing 2. A feed pump 4 is connected to the drive shaft 3, and the feed pump 4 allows the feed pump 4 to flow into the low pressure side chamber 6 via a fuel inlet 5. The fuel is supplied to the chamber 7 at a slightly higher pressure.

The pump housing 2 has a housing member 2a having a drive shaft inserted therein, a housing member 2b assembled to the housing member 2a and provided with a delivery valve 10, and an opening of the housing member 2b. The chamber 7 is formed by being surrounded by a partition wall body 11 fixed in the pump housing. The partition body 11 is tightly joined to the pump housing 2 via an O-ring, and the space surrounded by the partition body 11 communicates with a governor housing chamber 13 defined by the governor housing 12 to form a governor housing chamber. A shaft 15 of an actuator (electric governor) 14, which will be described later, housed in 13 is covered. Further, the partition wall body 11 has a fitting projection portion 11a integrally formed on a side portion thereof, and the fitting projection portion 1 is provided at the insertion portion 16 of the housing member 2b having the delivery valve 10.
1a is inserted.

The rotary member 17 is inserted through the partition wall body 11 and the insertion portion 11b is formed in the vicinity of the tip end of the rotary member 17 in the fitting projection 11a.
Is rotatably supported in an oil-tight manner by a base end portion of which is connected to the drive shaft 3 via a coupling 18.
Only rotation is allowed with the rotation of.
Further, the spring 20 provided between the housing 19 and the spring receiver 19 formed at the tip of the rotating member 17 urges the rotating member 17 toward the coupling side so as to eliminate the play in the axial direction. I have to.

A plunger 21 is slidably inserted in the radial direction (radial direction) at the base end of the rotary member 17.
In this embodiment, as shown in FIG. 2, four plungers 21 are provided on the same plane at intervals of, for example, 90 degrees, and the tip of each plunger 21 is at the base of the rotary member 17. Compression chamber 2 provided at the center of the end
2 so as to occlude 2, and the proximal end of the plunger 21 is
The inner surface of the ring-shaped cam ring 25 is brought into sliding contact with the shoe 23 and the roller 24. The cam ring 25 is provided concentrically around the rotary member 17, and a cam surface corresponding to the number of cylinders of the engine is formed inside. When the rotary member 17 rotates, the plungers 21 move in the radial direction of the rotary member 17. It reciprocates in the (radial direction) and the compression chamber 2
The volume of 2 is variable.

That is, if the cam ring 25 is formed corresponding to, for example, four cylinders, the cam ring 25
A convex surface is formed every 90 degrees on the inside of the shaft, so that the four plungers 21 move to compress the compression chamber 22 at the same time, and the cam ring 25
At the same time, they are moving away from the center.

A control sleeve 26 is oil-tightly fitted between the tip end portion and the base end portion of the rotary member 17. The control sleeve 26 is attached so as to be allowed to rotate only in the circumferential direction in a state where the rotation member 17 is prevented from moving in the axial direction. It is provided across the low-pressure side chamber 6.

The fuel compressed by the feed pump 4 passes through the passage 2 formed in the upper part of the pump housing.
7 and the pump housing 2 and the governor housing 12 assembled to the pump housing 2 are guided to the chamber 7 through the gap 28 and the governor housing chamber 13 to the overflow valve 29. 7, the rotary member 1 through the passage 11c of the fitting protrusion 11a
7 is guided to the pressure equalizing port 30 formed around the tip end portion of 7 and the rotating member 17.

The rotary member 17 is formed with a vertical hole 31 which is formed in the axial direction thereof and communicates with the compression chamber 22.
1 includes a suction port 32 that opens to the peripheral surface of the rotating member 17.
And a cut-off port 33 provided at a position farther from the compression chamber 22 than the suction port 32 and opening to the peripheral surface of the rotating member 17 in the chamber 7, and further at a portion inserted into the partition body 11. A distribution port 35, which is open to the peripheral surface of the rotating member 17 and can communicate with a distribution passage 34 communicating with the delivery valve 10, is connected.

The control sleeve 26 is provided so as to cover the suction port 32 and the cutoff port 33.
An intake hole 36 that can communicate with the intake port 32 and a cutoff hole 37 that can communicate with the cutoff port 33 are formed. In particular, the cutoff port 33 and the cutoff hole 37
Are formed as parallel slits extending in the axial direction of the rotating member 17, so that the communication timing between the cutoff port 33 and the cutoff hole 37 does not deviate due to rattling in the axial direction. . The actuator 14 is connected to the control sleeve 26.

The actuator 14 is a shaft 1 attached to a rotor 40 which is rotated by a signal from the outside.
A ball 41 provided at the tip of the shaft 15 is engaged with an engagement groove 42 formed in the control sleeve 26 shown in FIGS. 3A and 3B.
The ball 41 is provided eccentrically with respect to the shaft 15, and the engagement groove 42 formed in the sleeve 26 is formed over a predetermined angular range in the circumferential direction. Therefore, when the rotor 40 rotates. The locking position between the ball 41 and the engagement groove 42 is displaced, and the control sleeve 26 is rotated in the circumferential direction of the rotating member 17.

A projecting piece 43 extending in the radial direction is provided at a portion of the control sleeve 26 projecting to the low pressure side chamber 6, and a tip end of the projecting piece 43 is provided with a phase sensor 44 provided on a side part of the cam ring 25. They are facing each other. Here, the phase sensor 44 is composed of a potentiometer or an inductance type sensor that outputs a signal corresponding to a relative phase shift between the control sleeve 26 and the cam ring 25, and is provided on the protruding side of the control sleeve 26. Alternatively, the phase sensor 44 constitutes means for associating the movement of the control sleeve 26 and the movement of the cam ring 25 so that the position of the control sleeve 26 can be recognized in relation to the position of the cam ring 25.

A timer mechanism 50 is connected to the cam ring 25. The timer mechanism 50 used here has a timer piston 51 slidably housed in a cylinder provided below the cam ring 25. The timer piston 51 and the cam ring 25 are connected via a lever 52, The cam ring 25 is rotated by moving the timer piston 51 to change the advance angle.

A high pressure chamber into which the high pressure fuel in the chamber is introduced is formed at one end of the timer piston 51, and a low pressure chamber communicating with the suction path of the feed pump 4 is formed at the other end. Further, a timer spring is elastically mounted in the low pressure chamber, and the timer piston 51 is constantly urged toward the high pressure chamber by the timer spring. Therefore, the timer piston 51 stops at a position where the spring pressure of the timer spring and the hydraulic pressure in the high pressure chamber are balanced, and when the high pressure chamber pressure increases, the timer piston 51 moves to the low pressure chamber side against the timer spring, The cam ring 25 is rotated in a direction that advances the injection timing, and the injection timing is advanced. Further, when the high pressure chamber pressure becomes low, the timer piston 51
Moves to the high pressure chamber side, the cam ring 25 is rotated in a direction to retard the injection timing, and the injection timing is delayed.

The pressure in the high pressure chamber of the timer is adjusted by the timing control valve (TCV) 55 so that the required timer advance angle can be obtained. In the timing control valve 55, an inlet portion communicating with the chamber 7 and the high pressure chamber is formed on a side portion, and an outlet portion communicating with the low pressure chamber is formed at a tip portion, and the inlet portion and the outlet portion are internally formed. A needle 56 that opens and closes between and is stored. The needle 56 is constantly urged by a spring in a direction of blocking the communication between the inlet and the outlet, and when the solenoid 57 is energized and pulled toward the spring, the inlet and the outlet communicate with each other. The high pressure chamber and the low pressure chamber are communicated with each other.

When no current is flowing through the solenoid 57, the high pressure chamber and the low pressure chamber are completely cut off, but when the current is flowing, the high pressure chamber and the low pressure chamber are connected and the pressure in the high pressure chamber decreases. To do. As the pressure in the high-pressure chamber decreases, the timer piston 51 moves to a position that balances with the spring force of the timer spring, which causes the cam ring 25 to rotate and change the injection timing. The timing control valve 55 may be controlled by duty ratio control.

In the above structure, when the rotary member 17 rotates, the plunger 21 is reciprocated in the radial direction of the rotary member 17 by the cam ring 25. In the suction stroke, the suction port 32 and the suction hole are provided. 36, and the fuel in the chamber 7 is sucked into the compression chamber 22.

After that, when entering the pumping stroke, the suction port 3
The communication between 2 and the suction hole 36 is cut off, the distribution port 35 and one of the distribution passages 34 are aligned, and the compressed fuel is supplied to the delivery valve 10 through the distribution passage 34. The fuel delivered from the delivery valve 10 is delivered to an injection nozzle via an injection pipe (not shown), and is injected into the cylinder of the engine from this injection nozzle.

Then, when the cut-off port 33 and the cut-off hole 37 are aligned and the cut-off port 33 opens in the chamber 7 in the course of the pressure-feeding stroke, the compressed fuel flows out into the chamber 7 and reaches the injection nozzle. Is stopped and the injection ends. Therefore, after the communication between the suction port 32 and the suction hole 36 is cut off, the rotation angle from when the plunger 21 starts moving toward the center of the cam ring 25 until the cutoff port 33 and the cutoff hole 37 communicate with each other. Is the effective feed stroke (effective feed angle).

Here, since the timing at which the cutoff port 33 is aligned with the cutoff hole 37 can be varied depending on the position of the control sleeve 26, the injection is ended by adjusting the position of the control sleeve 26, that is, the injection amount or the effective pumping stroke is adjusted. Therefore, as the control sleeve 26 is rotated in the rotation direction of the rotating member 17, the communication timing between the cutoff port 33 and the cutoff hole 37 is delayed, so that as shown in FIG. As shown by the broken line, the effective pumping stroke is increased, and the injection amount can be increased. On the contrary, the injection amount can be reduced as the rotating member 17 is rotated in the direction opposite to the rotating direction.

FIG. 4 shows an operation section covered by the actuator 14 for driving and controlling the control sleeve 26. The section up to the start of pressure feeding (pre-injection section) fluctuated by the timer control shown by and the plunger shown by 21 starts to lift and cutoff port 33
Of the cut-off hole 37 until it communicates with the cut-off hole 37. This is represented by-and represents the effective stroke of fuel pressure feeding, and the phase sensor 44
By associating the angle detected in step 1 with the pressure feeding effective stroke angle, the pressure feeding effective stroke can be directly recognized from the output of the phase sensor 44.

That is, as shown in FIG. 4A, if the control sleeve 26 is rotated to increase the effective feeding stroke, the control sleeve 26 is rotated by
Since the phase between the control sleeve 26 and the cam ring 25 also deviates, the detection angle of the phase sensor 44 always corresponds to the effective feed angle.

Further, when the injection is started by adjusting the position of the timer piston 51, that is, the prestroke amount is adjusted and, for example, the cam ring 25 is retarded, as shown by the solid line to the broken line in FIG. 4B, the timer control is performed. The period until fluctuating pumping starts becomes longer. In this case, since the position of the control sleeve is not mechanically interlocked, the effective feeding stroke is shortened, and the phase of the control sleeve 26 and the cam ring 25 is deviated by the amount of rotation of the cam ring 25. The angle also becomes smaller as the effective feeding stroke becomes shorter. In this case, although the injection amount becomes small, if the rotation angle of the control sleeve 26 is corrected so that the original pressure feeding effective stroke is obtained,
It is possible to avoid fluctuations in the injection amount.

Conventionally, the control sleeve 2
The position of 6 and the position of the cam ring 25 are detected by some method, and the correction amount of the effective feeding stroke is calculated from the respective detection signals. However, according to the present invention,
Since the pressure-feeding effective stroke can be detected directly from the phase sensor 44, accurate pressure-feeding effective stroke control can be performed, and control accuracy can be improved. Further, since the correction processing can be performed only by the output from the phase sensor 44, the calculation processing time can be shortened as compared with the conventional one in which the calculation processing is performed based on the output of each sensor, and the actual injection amount becomes the target injection amount. It is possible to quickly follow, and also from this point, the control accuracy can be improved.

As a point to be additionally noted, since the cutoff port 33 and the cutoff hole 37 are formed in parallel with the axial direction of the rotary member 17, the rotary member 17 has a rattling in the axial direction. Even with this, the start and end of the pumping do not fluctuate and the injection characteristics do not shift, and the injection accuracy can be improved without increasing the assembly accuracy of the rotary member 17 in the axial direction.

Further, inside the pump housing 2, a partition wall body 1 is provided.
Since the low pressure side chamber 6 filled with the low pressure low temperature fuel by 1 and the chamber 7 filled with the fuel compressed by the feed pump 4 and kept at a somewhat high pressure, the fuel to the compression chamber 22 and the The movement of the plunger 21 to the outside can be easily and reliably performed by the differential pressure generated inside and outside the rotating member 17, and further, the cam ring 25, the roller 24, and the shoe 23 are arranged in the low pressure side chamber 6. Therefore, the contact portion between the cam ring 25 and the roller 24, which tends to have frictional heat as the rotating member 17 rotates, the roller 24
The cooling of the contact portion between the shoe and the shoe 23 is promoted, and
Lubrication around the rollers is promoted to ensure smooth movement.

The means for making the position of the control sleeve recognizable in relation to the position of the cam ring by associating the movement of the control sleeve with the movement of the cam ring is the control sleeve 26 and the cam ring 2 described above.
5 is constituted by a phase sensor 44 for detecting a phase shift from the cam ring 2, the actuator 14 for driving and controlling the control sleeve 26 is provided with the cam ring 2 as shown in FIG.
Alternatively, the reference position of the control sleeve with respect to the cam ring may be kept constant. In this case, the control sleeve 26 and the shaft 15 of the actuator 14 engage with each other outside the chamber 7. Again, the engagement groove 42 for engaging the shaft 15 is shown in FIG.
As shown in (b), the control sleeve 26
Is obliquely formed on the peripheral surface of the rotary member 17 at a predetermined angle with the axial direction of the rotary member 17.

In such a structure, the timing when the cutoff port 33 is aligned with the cutoff hole 37 is
Since it can be changed by rotating the control sleeve 26 as in the case of the above example, the injection amount is increased as the control sleeve 26 is rotated in the rotation direction of the rotating member 17 (FIG. 7A), and the rotating member is rotated. The amount of injection can be reduced as it is rotated in the direction opposite to the rotating direction of 17. Here, since the actuator 14 is fixed to the cam ring 25, the operation section covered by the actuator 14 corresponds to the effective feeding stroke, and comes after the pre-injection section by the timer control shown by. In this case, the effective feeding stroke can be directly recognized and controlled by the control amount itself of the actuator 14.

Further, since the reference position of the control sleeve 26 with respect to the cam ring 25 is always kept constant, as shown in FIG. 7B, when the cam ring 25 is rotated in a direction that retards the injection timing. , Cam ring 25
The control sleeve 26 is also rotated in the same direction by the same angle in accordance with the rotation of the suction port 32, and the timing at which the suction port 32 communicates with the suction hole 36 and the timing at which the cutoff port 33 communicates with the cutoff hole 37 are both delayed. Therefore, the effective pumping stroke does not change. Therefore, in this case, it is not necessary to correct the pressure-feeding effective stroke, that is, the injection amount by performing the advance angle control, the control time can be further shortened, and the error due to the variation of the sensor can be eliminated, and the control accuracy can be improved. Can be further enhanced.

In this case as well, the cutoff port 3
By using 3 and the cut-off hole 37 as parallel slits extending in the axial direction of the rotating member 17, more precise control can be realized.

[0044]

As described above, according to the first to third aspects of the invention, the pressure difference is provided between the inside and the outside of the rotary member, and the control sleeve is provided in both the chamber and the low pressure side chamber. Since it is provided and the position of the control sleeve is directly recognized in relation to the position of the cam ring, it is possible to easily and reliably perform the intake of fuel and the outward movement of the plunger in the intake process, and the control sleeve Even if the position and the position of the cam ring are not individually detected, the effective feeding stroke can be controlled easily and accurately.

If the cut-off port and the cut-off hole are parallel slits, the cut-off timing can be accurately controlled even if the rotary member is displaced in the axial direction. be able to.

[Brief description of drawings]

FIG. 1 is a sectional view showing a distribution type fuel injection pump according to the present invention.

FIG. 2 is a view of the cam ring shown in FIG. 1 and members inside thereof as viewed in the axial direction of a rotating member.

3 (a) is a view showing a control sleeve used in the distribution type fuel injection pump shown in FIG. 1, and FIG. 3 (b) is a development view thereof.

4 (a) is a view for explaining a case where the timer position is fixed and the control sleeve is displaced in the distribution type fuel injection pump shown in FIG. 1, and FIG. 4 (b) is a view for explaining the control sleeve. It is a figure explaining the case where a position is fixed and a timer advance angle is changed.

5 is a schematic configuration diagram of a main part showing another configuration example of the distribution type fuel injection pump of FIG.

6A is a view showing a control sleeve used in the distribution type fuel injection pump shown in FIG. 5, and FIG. 6B is a development view thereof.

7 (a) is a diagram for explaining a case in which the timer position is fixed and the control sleeve is displaced in the distribution type fuel injection pump shown in FIG. 5, and FIG. 7 (b) is a diagram showing the control sleeve. It is a figure explaining the case where a position is fixed and a timer advance angle is changed.

FIG. 8 (a) is a schematic configuration diagram showing a main part of a distribution type fuel injection pump prototyped at the beginning of development by the present inventor,
FIG. 6B is a diagram showing the relationship between the position control of the control sleeve and the advance control of the timer.

[Explanation of symbols]

 2 Pump Housing 4 Feed Pump 5 Fuel Inlet 6 Low Pressure Side Chamber 7 Chamber 14 Actuator 17 Rotating Member 21 Plunger 22 Compression Chamber 23 Shoe 24 Roller 25 Cam Ring 26 Control Sleeve 32 Suction Port 33 Cutoff Port 35 Distribution Port 36 Suction Hole 37 Cutoff Hole 44 phase sensor

Claims (4)

[Claims] 1. A rotary member that rotates in synchronization with an engine, a plunger that is provided in a radial direction of the rotary member, and that varies the volume of a compression chamber formed in the rotary member, and a concentric ring around the rotary member. And a cam ring that regulates the movement of the plunger in a housing, and a port that communicates with the compression chamber to suck, deliver, and cut off fuel is formed in the rotary member. A chamber capable of communicating with a low-pressure side chamber formed in the housing from a fuel inlet to an upstream side of a feed pump, and a port into which fuel pressurized by the feed pump is guided to suck and cut off the fuel. And the rotation member is provided on the rotary member so as to cover the suction and cutoff ports, and the communication timing of these ports with the chamber is defined. A control sleeve for controlling the control sleeve is rotatably fitted over the control sleeve. The control sleeve is provided in both regions of the low-pressure side chamber and the chamber. Further, the control sleeve is associated with the movement of the control sleeve and the movement of the cam ring. A fuel injection pump of the distributed type, characterized in that it is provided with means for making it possible to recognize the position of the above position in relation to the position of the cam ring. 2. The distributed fuel injection pump according to claim 1, wherein the movement of the control sleeve and the movement of the cam ring are associated with each other by detecting a phase shift between the control sleeve and the cam ring. 3. The distributed fuel injection pump according to claim 1, wherein the movement of the control sleeve and the movement of the cam ring are associated with each other by fixing a drive control actuator of the control sleeve to the cam ring. . 4. The control sleeve has a hole that can communicate with the cutoff port, and the cutoff port and the hole are formed as parallel slits extending in the axial direction of the rotating member. The distributed fuel injection pump according to claim 1.