JPH07247931A - Distributor type fuel injection pump - Google Patents

Abstract

PURPOSE:To provide an injection rate characteristic of long duration at the time of a low load and to provide an injection rate characteristic of rapid spill at the time of a high load. CONSTITUTION:A cam 25 for cutting off to cut off fuel is provided separately from a cam 14 for oil delivery to deliver fuel in an inner cam type fuel injection pump, and cutting off speed of fuel is independently set by this cam 25 for cutting off. A characteristic to increase cam speed continuously in a force feeding process is given to this cam 25 for cutting off, cutting off speed is, decreased at the time of a low load where cutting off is fast, and the cutting off speed at the time of a high load where cutting off is slow is increased.

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 injection pump which is used for fuel supply to a diesel engine or the like and adjusts injection timing and injection amount, that is, a rotary member which is synchronized with the engine. The present invention relates to a fuel injection pump in which a plunger reciprocates in a radial direction.

[0002]

2. Description of the Related Art As a distribution type injection pump of this type, for example, a second type is mainly disclosed in JP-A-59-110835.
The ones shown in pages, page 4, FIGS. 1 and 7 are known. This is a fuel distribution rotary member 4 synchronized with the engine.
A concentric inner cam ring 1 is arranged around the inner circumference of the inner cam ring 1, and the cam surfaces formed inside the inner cam ring 1 reciprocate the pressure-feeding plungers 21 and 22 in the radial direction of the fuel distribution rotary member 4. The fuel distribution rotary member 4 has a pump chamber 2 whose volume is changed by the pressure-feeding plungers 21 and 22, suction holes 51 to 54 for sucking fuel into the pump chamber 2 during the suction process, and pressure in the pump chamber 2 during the pressure-feeding process. The distribution port 6 for delivering the fuel and the overflow ports 71 to 74 for cutting off the fuel delivery are formed, and the ring-shaped member 7 is oil-tightly fitted to cover the overflow ports 71 to 74. The slanted lead groove portion 10 for cutoff is formed on the inner surface of the ring-shaped member 7. By adjusting the axial position of the ring-shaped member 7 by the linear solenoid 81, the cutoff time (overflow) during the pressure feeding process (overflow) is obtained. The fuel injection amount can be varied by changing the timing at which the flow port opens in the oblique lead groove portion).

Further, in JP-A-60-201067, as shown in the first page, right column, fifth line to the second page, upper right column, fifth line, and FIG. In the injection pump, a technology is disclosed in which the leak passage 17 for releasing the fuel in the pressurizing chamber 6 is opened and closed by a solenoid valve 19, and the solenoid valve 19 is opened at the time of cutoff of the fuel to let the fuel escape from the leak passage 17. ing.

[0004]

However, in the former inner cam type injection pump, the overflow port and 71 to 7 are used.
Since the speed (cutoff speed) at which the fuel 4 is communicated with the oblique lead groove portion 10 is cut off (cutoff speed) is not changed by the shape of the cam surface of the inner cam ring 1, but is determined by the rotation of the engine. The degree of freedom in setting the injection rate characteristics according to various loads on the engine is small.

Further, in the latter injection pump in which the fuel injection amount is controlled by opening and closing the solenoid valve, the response speed is substantially constant, and it is difficult to change the response speed according to the load. Therefore, the higher the rotational speed range, the longer the response period converted into the crank angle, which makes it difficult to obtain a good cutoff characteristic especially in the high load range. Generally, there is a demand to form a long duration injection rate characteristic at a low load to reduce NO _x and noise and conversely, at a high load, a rapid spill (increasing cutoff speed) injection rate characteristic. There is a demand to reduce the occurrence of smoke by forming it and giving priority to noise and the like.

Therefore, an object of the present invention is to provide a distribution type fuel injection pump which can solve the above-mentioned inconvenience and can obtain an injection characteristic having an optimum cutoff speed according to a load.

Further, a distribution type fuel injection pump capable of obtaining an injection rate characteristic of long duration at a low load to reduce noise and obtaining an injection rate characteristic of a rapid spill at a high load to reduce smoke. The challenge is to provide.

[0008]

As a result of various studies on means for responding to the above inconveniences and demands, the inventor of the present invention has found that in an inner cam type fuel injection device, the spill speed of fuel at cutoff is used for oil feeding. Although it is not possible to achieve the desired characteristics with a cam (cam ring), focus on the fact that a cutoff speed can be set independently of the oil feeding characteristics by providing a cutoff cam that is separate from the oil feeding cam. Then, the present invention has been completed.

That is, the distributed fuel injection pump according to the present invention has a rotating member that rotates in synchronism with the engine, a plunger provided in the radial direction of the rotating member, and a concentric arrangement around the rotating member. A ring-shaped oil feeding cam that regulates the movement of the plunger is provided, and a compression chamber that faces the plunger is formed on the rotary shaft, and a port that communicates with the compression chamber to suck, deliver, and cut off fuel. A cut-off sleeve is slidably fitted onto the rotary member, and a cut-off cam that regulates the axial movement of the cut-off sleeve is provided on the rotary member, and the cut-off sleeve is provided with the cut-off sleeve. Is formed with a cut-off hole that can communicate with the above-mentioned port, and a control sleeve for adjusting the opening timing of the cut-off hole is slidably fitted on the cut-off sleeve. (Claim 1).

Here, as the cut-off cam, a cam disk or the like in which the base end portion of the cut-off sleeve abuts in the axial direction of the rotating member can be considered, but the cam speed continuously increases in the pressure feeding process. It is desirable to have a cam speed characteristic (claim 2). As a cut-off cam having such a cam speed characteristic, there is a cam having a concave arc shape in the pumping section so that the cam speed change is small in the initial stage of the effective pumping cam angle and becomes large in the latter stage. Conceivable.

Further, a roller may be provided at the base end portion of the cutoff sleeve that abuts against the cutoff cam to reduce the friction between the cutoff cam and the cutoff sleeve.

Further, the characteristic of the fuel injection rate (cutoff speed) may be further adjusted by the shape of the cutoff hole formed in the cutoff sleeve. For example, the cutoff speed can be increased as the width of the cutoff hole in the circumferential direction of the cutoff sleeve is increased, and conversely, the cutoff speed can be decreased as the width of the cutoff hole is reduced in the circumferential direction. The initial width of the cutoff hole may be reduced in the circumferential direction, and then the circumferential width may be increased continuously or stepwise to obtain a desired fuel injection rate.

[0013]

Therefore, according to the first aspect of the invention, when the rotary member rotates, the cam ring causes the plunger to reciprocate in the radial direction of the rotary member to change the volume of the compression chamber, and at the same time, the cut-off sleeve cuts. The cam for reciprocation reciprocates in the axial direction of the rotating member, but when the cutoff port communicates with the cutoff hole and the cutoff hole is released from the closed state by the control sleeve in the pressure feeding process, the compressed fuel spills. Then, the injection is ended.

That is, the injection pump of the present application has a fuel cutoff cam (cutoff cam) in addition to the fuel pressure feed cam (pressure feed cam), and the timing at which the fuel is spilled by the cutoff cam. The cut-off speed (amount of fuel spilling per unit time) at (injection end) can be independently determined. Moreover, the cutoff cam has
Unlike the pressure-feed cam, the fuel pressure does not act via the plunger, so the cam shape of the cut-off cam can be freely formed without being restricted by the fuel pressure, and the desired cut-off characteristics can be formed. it can.

Further, if the cam speed of the cut-off cam is continuously increased in the pressure feeding step as in the second aspect, the cut-off speed is low under a low load (when the opening time of the cut-off hole is advanced). Therefore, the injection rate characteristic of long duration is formed. On the contrary, at a high load (when the opening timing of the cutoff hole is delayed), the cutoff speed becomes faster and the injection rate characteristic of the rapid spill is formed.

[0016]

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 a chamber 4 in the pump housing 2, and a feed pump 5 is connected to the drive shaft 3 to feed fuel from a fuel tank (not shown) in the drawing. The chamber 4 is provided with a passage 7a formed above the feed pump and a gap 7b formed between the pump housing 2 and the governor housing 42 attached thereto.
To be supplied to.

The rotating member 6 has its tip 6a rotatably fitted in a cylindrical body 8 fixed to the pump housing 2 in an oil-tight manner, and the base end of the rotating member 6 has a coupling 9 interposed therebetween. Is connected to the drive shaft 3 so that only rotation is allowed as the drive shaft 3 rotates.

A plunger 10 is slidably inserted into the base end portion 6b of the rotary member 6 in the radial direction (radial direction). In this embodiment, as also shown in FIG.
For example, four plungers 10 are provided on the same plane at intervals of 90 degrees.
The front end of the plunger 10 faces the compression chamber 11 provided at the center of the base end of the rotary member 6, and the base end of the plunger 10 has a ring-shaped oil feeding cam (via a shoe 12 and a roller 13). The inner surface of the cam ring 14 is slidably contacted. The oil feeding cam 14 is provided concentrically around the rotary member 6, and the cam surface 14a corresponding to the number of cylinders of the engine is formed inside, and when the rotary member 6 rotates,
Each plunger 10 reciprocates in the radial direction (radial direction) of the rotating member 6 to change the volume of the compression chamber 11.

That is, if the oil feeding cam 14 is formed corresponding to, for example, four cylinders, the oil feeding cam 14
Since the convex surfaces are formed inside every 90 degrees, the four plungers 10 move so as to compress the compression chambers 11 at the same time, and the oil feeding cams 14
At the same time, they are moving away from the center.

As shown in FIG. 4, the cam speed characteristic of the oil feeding cam 14 has such a characteristic that the cam speed continuously increases up to a predetermined cam angle, especially when the cam lift is small. At (the initial stage of the effective pressure feed cam angle), the change in cam speed is greater than that at the time when the cam lift is large (the latter stage of the effective pressure feed cam angle).

A cut-off sleeve 15 is slidably fitted between the tip portion 6a and the base end portion 6b of the rotary member 6, and a control sleeve 16 is slidably fitted on the cut-off sleeve 15. It is fitted over. A suction hole 17 and a cutoff hole 18 are formed in the cutoff sleeve 15, and the control sleeve 16 has a cutoff hole 18
Is provided so that the relative position between the cutoff hole 18 and the control sleeve 16 changes in accordance with the movement of the cutoff sleeve in the axial direction.

A vertical hole 20 formed in the axial direction of the rotary member 6 and communicating with the compression chamber 11, a suction port 21 for communicating the vertical hole 20 with a suction hole 17 of the cut-off sleeve 15, and a vertical hole. 20 and distribution passage 2 formed in the cylindrical body 8
There are formed a distribution port 23 for communicating with 2 and a cutoff port 24 for communicating with the vertical hole 20 and the cutoff hole 18 of the cutoff sleeve 15.

A cam (cut-off cam 25) for fuel cut-off which rotates together with the rotary member 6 is fixedly mounted, and the base end of the cut-off sleeve 15 slides on the cut-off cam 25. It is movably abutted. The cut-off sleeve 15 is pressed against the cut-off cam 25 by a sleeve return spring 27 that is elastically mounted between the spring receiver 26 provided at the base end portion 15a of the cut-off sleeve 15 and the pump housing 2. Cam 1
The tip end of the guide member 28 that moves with 4 is locked in a groove formed in the side portion of the cutoff sleeve 15, so that the cutoff sleeve 15 can rotate in synchronization with the oil feeding cam 14. The cut-off cam 25 has a cam surface 2 formed at a contact portion with the cut-off sleeve 15.
5a also has four convex surfaces formed at equal intervals corresponding to the number of cylinders of the engine. When the cutoff cam 25 rotates as the rotary member 6 rotates, the cutoff sleeve 15 causes the rotary member 6 to rotate. It is designed to reciprocate in the axial direction.

The oil feeding cam 14 and the cutoff cam 2
5 is attached so that the plunger 10 and the cut-off sleeve 15 move in synchronization with each other in substantially the same phase,
The cam speed of the cut-off cam 25 in the pressure feeding process is shown in FIG.
As shown in, the cam angle increases continuously as the cam angle increases in the pumping process. When the cam angle is small, the increase rate of the cam speed is small and when the cam angle is large, the increase rate of the cam speed is large. It is a characteristic.

When the rotary member 6 rotates, the cutoff cam 25 is rotated, and the cutoff sleeve 15 is rotated.
Will be reciprocally moved in the axial direction by the cut-off cam 25.
In the suction process of moving away from the center of 4, the suction port 21 and the suction hole 17 are aligned and fuel is sucked into the compression chamber 11. After that, when the plunger 6 enters the pressure feeding step of moving toward the center of the oil feeding cam 14, the communication between the suction port 21 and the suction hole 17 is cut off, and the distribution port 23 and one of the distribution passages 22 are aligned. The compressed fuel is supplied to the delivery valve 30 via the distribution passage 22. The fuel sent from the delivery valve 30 is sent to an injection nozzle via an injection pipe (not shown), and is injected from the injection nozzle into the cylinder of the engine.

When the cut-off port 24 and the cut-off hole 18 are aligned in the middle of the pressure feeding process and the cut-off hole 18 is disengaged from the side edge of the control sleeve 16 and opened into the chamber 4, the compressed fuel is discharged. Chamber 4
, The delivery to the injection nozzle is stopped, and the injection ends. Here, since the timing at which the cut-off hole 18 is disengaged from the side edge of the control sleeve 16 can be varied depending on the position of the control sleeve 16, the injection can be ended by adjusting the position of the control sleeve 16, that is, the injection amount can be adjusted. The injection amount can be reduced as it moves to the left side (the base end side of the rotating member 6) in the figure, and can be increased as it moves to the right side (the tip end side of the rotating member 6).

Here, the control sleeve 16 includes
A ball 34 formed at the tip of a shaft 33 attached to the rotor 32 of the actuator 31 is engaged, and the ball 34 is provided eccentrically with respect to the shaft 33 and is controlled by a signal from the outside. The control sleeve 16 is moved by rotating the rotor 32, and the position of the rotating member 6 in the axial direction can be adjusted.

Incidentally, as to the timer device 35,
The timer device 35 used here has a timer piston 36 slidably housed in a cylinder provided below the oil feeding cam 14 described above.
6 is connected to the oil feeding cam 14 via the lever 37, and the oil feeding cam 14 is rotated by the timer piston 36 to adjust the injection timing.

A high pressure chamber into which the high pressure fuel in the chamber is introduced is formed at one end of the timer piston 36, and a low pressure chamber communicating with the suction path of the feed pump 5 is formed at the other end. Further, a timer spring is elastically mounted in the low pressure chamber, and the timer piston 36 is constantly urged toward the high pressure chamber by the timer spring. Therefore, the timer piston 36 stops at a position where the spring pressure of the timer spring and the hydraulic pressure in the high pressure chamber are in balance, and when the high pressure chamber pressure increases, the timer piston 36 moves to the low pressure chamber side against the timer spring, The oil feeding cam 14 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 36
Moves to the high pressure chamber side, and the oil feeding cam 14 is rotated in a direction that retards 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) 38 so that the required timer advance angle can be obtained. In the timing control valve 38, an inlet portion communicating with the chamber 4 and the high pressure chamber is formed at a side portion, and an outlet portion communicating with the low pressure chamber is formed at a tip portion, and the inside has an inlet portion and an outlet portion. A needle 40 that opens and closes between and is stored. The needle 40 is constantly urged by a spring in a direction of blocking communication between the inlet portion and the outlet portion. When the solenoid 41 is energized and pulled toward the spring, the inlet portion and the outlet portion 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 41, the high pressure chamber and the low pressure chamber are completely cut off, but when current is flowing, the high pressure chamber and the low pressure chamber are connected and the pressure in the high pressure chamber drops. To do. As the pressure in the high-pressure chamber decreases, the timer piston 36 moves to a position in which the spring force of the timer spring is balanced with the spring force of the timer spring. The timing control valve may be controlled by duty ratio control.

In the above construction, at the time of high load (conditional region shown by A in FIG. 3) requiring a large amount of fuel injection, the control sleeve 16 is moved to the tip end side of the rotary member 6, so that the injection is completed. Becomes slower, and the effective feed cam angle of the cut-off cam 25 becomes larger. Therefore, as shown in FIG. 4, the cam speed of the cutoff cam is high at the time of cutoff, and the cutoff speed, that is, the speed at which the cutoff hole 18 opens in the chamber 4 is increased, and the inside of the rotary member is cut off. The compressed fuel is quickly returned to the chamber 4. That is, as shown by the injection rate characteristic of FIG. 5A, the injection rate increases at high load,
The end of injection becomes faster as shown by the solid line than the conventional characteristic shown by the broken line, and the generation of smoke at high load can be reduced.

Further, when the fuel injection amount is low and the load is low (for example, in the condition region shown by B in FIG. 3), the control sleeve 16 is moved to the base end side of the rotary member 6, so that the end of injection is early. Become, cutoff cam 2
The effective feeding cam angle of No. 5 becomes smaller. Therefore, as shown in FIG. 4, the cam speed of the cutoff cam is small at the time of cutoff, the cutoff speed becomes slow, and the compressed fuel in the rotary member is slowly returned to the chamber 4. That is, as shown by the injection rate characteristic of FIG. 5B, the injection rate becomes small at the time of low load, but the end of injection becomes slower as shown by the solid line than the conventional characteristic shown by the broken line. It is possible to reduce the noise at low load (see Table 1).

[0035]

[Table 1]

The cut-off cam 25 used in this embodiment is similar in shape to the cam disk used in the VE pump, but is pressurized in the compression chamber like the VE pump. The fuel does not act, and only a small biasing force biased by the sleeve return spring 27 acts. Therefore, in the cam disk used in the VE pump, although there is a limit to the formation of the cam shape from the viewpoint of durability in spite of the demand to obtain a high injection rate, according to the present invention, Since the cam for receiving the fuel pressure (the oil feeding cam 14) and the cam for reciprocating the cutoff sleeve 15 (the cutoff cam 25) are separated, the cutoff cam 25 has a friction with the cutoff sleeve 15. However, the degree of freedom in machining the cam surface is significantly increased, and the cam shape can be made to obtain optimum characteristics without being limited by the oil feeding cam 14.

In the above-described embodiment, the cut-off cam 25 is directly contacted with the base end of the cut-off sleeve 15, but a roller is attached to the base end of the cut-off sleeve 15. Cut-off cam 2
You may make it contact | abut with 5. According to such a configuration, the friction of the contact portion can be further reduced, and there is an advantage that a smooth movement can be guaranteed.

Further, the cam speed characteristic is such that the cam speed is low at the initial stage of the effective pressure feeding cam angle (when the cam lift is small) and becomes high at the latter stage of the effective pressure feeding cam angle (when the cam lift is large). If so, the shape of the cut-off cam 25 may be changed if necessary. For example, the cam shape is such that the characteristics shown in FIG. 4 can be obtained, that is, a shape in which the pumping section is a concave arc so that the cam speed change is small when the cam lift is small and the cam speed change is large when the cam lift is large. You may

Further, by adjusting the shape of the cutoff hole 18 of the cutoff sleeve 15, the characteristics of the fuel injection rate and the cutoff characteristics can be further varied.

This will be described for convenience with reference to a development view of the cut-off hole 18 as seen from the outside of the cut-off sleeve 15 in the radial direction. A rectangular shape (width L in the circumferential direction) shown in FIG.
Assuming that the injection rate characteristic in the state in which the cutoff hole 18 of 1) is formed is as shown in FIG. 7 (shown by the broken line), the circumferential length of the cutoff hole 18 is shown in FIG. 6B. If the length L2 is longer than the length L1, the cut-off hole 1 that is opened from the side edge of the control sleeve to the chamber 4
Since the area per unit stroke of 8 becomes large, the amount of fuel flowing out into the chamber per unit time becomes large, and the injection rate gradient at the cutoff becomes steep as shown in (solid line) of FIG. .

The shape of the cut-off hole is shown in FIG. 6 (c).
As shown in (b), if a cutout 18a having a narrow width is further provided toward the tip of the cut-off sleeve 15 in the shape of (b), if the cutout 18a deviates from the side edge of the control sleeve 16, the fuel injection rate is increased. Is suppressed, and then the rectangular portion of width L2 following the notch is disengaged from the side edge of the control sleeve, the fuel is rapidly spilled and cut off. That is, as shown by (dashed line) in FIG. 7, the maximum injection rate is suppressed, and similarly, the gradient at the cutoff becomes steep.

There are various other possible shapes of the cut-off hole. As shown in FIG. 6 (d), if the cut-off sleeve 15 is formed in a triangular shape with its width gradually narrowing toward the tip, it flows out into the chamber. Since the amount of fuel per unit stroke gradually increases, the increase in the fuel injection rate is suppressed, and the gradient of the fuel injection rate becomes steeper in the latter half of the cutoff, and the characteristics similar to those in FIG. 7 are obtained.

Further, as shown in FIG. 6E, the shape of the cut-off sleeve is changed in the thickness direction (radial direction),
The sliding contact surface with the rotating member 6 has the shape shown in FIG. 6B, and the sliding contact surface with the control sleeve has a narrower width toward the tip of the cut-off sleeve 15, as shown in FIG. 6C. The shape may be provided with the notch 18b. Also in this case, when the notch 18b is disengaged from the side edge of the control sleeve 16, an increase in the fuel injection rate is suppressed, and when the rectangular portion having the width L2 following the notch is disengaged from the side edge of the control sleeve, the fuel injection rate is rapidly increased. Fuel is spilled and cut off. Therefore, also in this case, as shown in FIG. 7, the characteristics that the maximum injection rate is suppressed and the gradient at the cutoff is steep are obtained.

Therefore, the injection rate characteristic can be changed according to the load by changing the cutoff speed with the cutoff cam provided separately from the oil feeding cam, and by selecting the shape of the cutoff hole. Also, the setting of the injection rate characteristic can be changed, and by combining these, the injection rate characteristic can be designed with a greater degree of freedom.

[0045]

As described above, according to the first aspect of the present invention, the cutoff speed is determined by the cutoff cam provided separately from the fuel oil feeding cam. The cut-off speed can be independently determined without being limited by the oil feeding cam, and the fuel pressure does not act on the cut-off cam via the plunger. It is possible to obtain the injection characteristic with the optimum cutoff speed.

According to the second aspect of the present invention, the cut-off cam has a cam speed characteristic of continuously increasing the cam speed in the pressure feeding step, so that the injection of long duration is performed at a low load. The rate characteristic can be obtained to reduce the noise, and the rapid spill injection rate characteristic can be obtained at the time of high load to reduce the smoke.

[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 cross-sectional view of the oil feeding cam shown in FIG. 1 and members inside thereof as viewed in the axial direction of a rotating member.

FIG. 3 is a characteristic diagram showing a relationship between a fuel injection amount and a pump rotation speed.

FIG. 4 is a characteristic diagram showing a cam speed of an oil feeding cam and a cam speed of a cutoff cam with respect to a cam angle.

FIG. 5 is a diagram showing a fuel injection rate characteristic with respect to a cam angle, (a) shows a characteristic at a high load, and (b) shows a characteristic at a low load.

FIG. 6 is a view showing various shapes of cutoff holes formed in the cutoff sleeve.

FIG. 7 is a diagram for explaining changes in fuel injection rate characteristics with respect to various cutoff holes shown in FIG.

[Explanation of symbols]

 6 Rotating member 10 Plunger 11 Compression chamber 14 Oil feeding cam 15 Cut-off sleeve 16 Control sleeve 17 Suction hole 18 Cut-off hole 20 Vertical hole 21 Suction port 22 Distribution passage 23 Distribution port 24 Cut-off port 25 Cut-off cam

Claims (2)

[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 a ring-shaped feed that is provided concentrically around the rotary member and that regulates the movement of the plunger. An oil cam is provided, a compression chamber facing the plunger is formed on the rotary shaft, and a port that communicates with the compression chamber to suck, deliver, and cut off fuel is formed, and a cutoff sleeve is slid on the rotary member. Movably fitted,
A cutoff cam that regulates the movement of the cutoff sleeve in the axial direction is provided on the rotating member, and a cutoff hole that is capable of communicating with the cutoff port is formed in the cutoff sleeve. A distribution type fuel injection pump, wherein a control sleeve for adjusting the opening timing of the cutoff sleeve is slidably fitted on the cutoff sleeve. 2. The distribution type fuel injection pump according to claim 1, wherein the cut-off cam has a cam speed characteristic in which the cam speed continuously increases in the pressure feeding step.