JP7198363B2 - Electromagnetic intake valve and high pressure fuel supply pump - Google Patents

Description

The present invention relates to an electromagnetic suction valve and a high pressure fuel supply pump.

A high-pressure fuel supply pump is disclosed, for example, in Patent Document 1. A high-pressure fuel supply pump described in Patent Document 1 includes an electromagnetic intake valve. When the electromagnetic suction valve is in a non-energized state in which the electromagnetic coil is not energized, the valve element is urged by the urging force of the spring to open the valve. On the other hand, when the electromagnetic coil is energized, a magnetic attraction force is generated to move the valve body against the biasing force of the spring, thereby closing the electromagnetic intake valve. In this manner, the electromagnetic intake valve performs opening and closing motions depending on whether or not the electromagnetic coil is energized, thereby controlling the supply amount of high-pressure fuel.

JP 2013-148025 A

However, in the electromagnetic intake valve of the high-pressure fuel supply pump disclosed in Patent Document 1, a spring that biases the valve body is arranged in the pressurizing chamber. As a result, the dead volume in the pressurization chamber increases, and the volumetric efficiency of the high-pressure fuel supply pump deteriorates.

SUMMARY OF THE INVENTION An object of the present invention is to provide an electromagnetic intake valve and a high-pressure fuel supply pump that can reduce the dead volume in the pressurizing chamber in consideration of the above problems.

In order to solve the above problems and achieve the object of the present invention, a high-pressure fuel supply pump of the present invention includes a valve member, a seat member, a biasing member, and a stopper . The valve member has a rod portion and a valve portion provided at one end of the rod portion. The seat member has a guide portion that guides the outer periphery of the rod portion, and a seat portion on which the valve portion is seated. The biasing member biases the rod portion in a direction in which the valve portion is seated on the seat portion. When the valve member moves in the valve opening direction, which is the opposite direction to the valve closing direction, the stopper comes into contact with the valve portion to restrict movement of the valve member in the valve opening direction. The length from the center of the guide portion, which is the center in the direction in which the rod extends in the guide portion, to the other end of the rod portion is shorter than the length from the center of the guide portion to the tip of the valve portion. Furthermore, the stopper has an engagement hole with which the tip of the valve portion engages.

According to the high-pressure fuel supply pump configured as described above, the dead volume in the pressurization chamber can be reduced.
Problems, configurations, and effects other than those described above will be clarified by the following description of the embodiments.

1 is an overall configuration diagram of a fuel supply system using a high-pressure fuel supply pump according to one embodiment of the present invention; FIG. 1 is a longitudinal sectional view (Part 1) of a high-pressure fuel supply pump according to an embodiment of the present invention; FIG. FIG. 2 is a longitudinal sectional view (No. 2) of the high-pressure fuel supply pump according to one embodiment of the present invention; 1 is a horizontal cross-sectional view of a high-pressure fuel supply pump according to an embodiment of the present invention, viewed from above; FIG. FIG. 4 is a cross-sectional view of an exploded electromagnetic intake valve in the high-pressure fuel supply pump according to the embodiment of the present invention; FIG. 4 is an enlarged cross-sectional view of the electromagnetic intake valve in the high-pressure fuel supply pump according to the embodiment of the present invention, showing a state in which the electromagnetic intake valve is open; FIG. 4 is an enlarged cross-sectional view of the electromagnetic intake valve in the high-pressure fuel supply pump according to the embodiment of the present invention, showing a state in which the electromagnetic intake valve is closed;

1. Embodiment Hereinafter, a high pressure fuel supply pump according to one embodiment of the present invention will be described. In addition, the same code|symbol is attached|subjected to the member which is common in each figure.

[Fuel supply system]
Next, a fuel supply system using a high-pressure fuel supply pump according to this embodiment will be described with reference to FIG.
FIG. 1 is an overall configuration diagram of a fuel supply system using a high-pressure fuel supply pump according to this embodiment.

As shown in FIG. 1 , the fuel supply system includes a high-pressure fuel supply pump 100 , an ECU (Engine Control Unit) 101 , a fuel tank 103 , a common rail 106 and a plurality of injectors 107 . Components of the high-pressure fuel supply pump 100 are integrally incorporated into the body 1 .

Fuel in the fuel tank 103 is pumped up by a feed pump 102 driven based on a signal from the ECU 101 . The pumped fuel is pressurized to an appropriate pressure by a pressure regulator (not shown) and sent to the low-pressure fuel suction port 51 of the high-pressure fuel supply pump 100 through the low-pressure pipe 104 .

The high-pressure fuel supply pump 100 pressurizes the fuel supplied from the fuel tank 103 and pumps it to the common rail 106 . A plurality of injectors 107 and a fuel pressure sensor 105 are attached to the common rail 106 . A plurality of injectors 107 are mounted according to the number of cylinders (combustion chambers), and inject fuel according to the drive current output from the ECU 101 . The fuel supply system of this embodiment is a so-called direct injection engine system in which the injector 107 directly injects fuel into the cylinder of the engine.

The fuel pressure sensor 105 outputs the detected pressure data to the ECU 101 . The ECU 101 determines an appropriate injection fuel amount (target injection fuel length) and an appropriate fuel pressure (target fuel pressure), etc.

The ECU 101 also controls the driving of the high-pressure fuel supply pump 100 and the plurality of injectors 107 based on the calculation results of the fuel pressure (target fuel pressure) and the like. That is, the ECU 101 has a pump control section that controls the high-pressure fuel supply pump 100 and an injector control section that controls the injector 107 .

The high-pressure fuel supply pump 100 has a pressure pulsation reduction mechanism 9 , an electromagnetic suction valve 3 that is a variable displacement mechanism, a relief valve mechanism 4 (see FIG. 2 ), and a discharge valve 8 . The fuel flowing from the low-pressure fuel intake port 51 reaches the intake port 335a of the electromagnetic intake valve 3 via the pressure pulsation reducing mechanism 9 and the intake passage 10b.

The fuel that has flowed into the electromagnetic intake valve 3 passes through the valve portion 339 , flows through the intake passage 1 a formed in the body 1 , and then flows into the pressurization chamber 11 . A plunger 2 is slidably held in the pressure chamber 11 . The plunger 2 reciprocates when power is transmitted by a cam 91 (see FIG. 2) of the engine.

In the pressure chamber 11, fuel is drawn from the electromagnetic intake valve 3 during the downward stroke of the plunger 2, and is pressurized during the upward stroke. When the fuel pressure in the pressurizing chamber 11 exceeds a set value, the discharge valve 8 is opened, and high-pressure fuel is pressure-fed to the common rail 106 through the discharge passage 12a. The discharge of fuel by the high-pressure fuel supply pump 100 is operated by opening and closing the electromagnetic intake valve 3 . The opening and closing of the electromagnetic intake valve 3 is controlled by the ECU 101 .

[High pressure fuel supply pump]
Next, the configuration of the high-pressure fuel supply pump 100 will be described with reference to FIGS. 2 to 4. FIG.
FIG. 2 shows a longitudinal sectional view (Part 1) of the high-pressure fuel supply pump 100 seen in a cross section perpendicular to the horizontal direction, and FIG. It is a figure (part 2). FIG. 4 is a horizontal cross-sectional view of the high-pressure fuel supply pump 100 as seen in a cross-section perpendicular to the vertical direction.

As shown in FIGS. 2 to 4, the body 1 of the high-pressure fuel supply pump 100 is provided with the suction passage 1a and the mounting flange 1b. The mounting flange 1b is in close contact with a fuel pump mounting portion 90 of an engine (internal combustion engine) and fixed with a plurality of bolts (screws) not shown. That is, the high-pressure fuel supply pump 100 is fixed to the fuel pump mounting portion 90 by the mounting flange 1b.

As shown in FIG. 2, an O-ring 93, which is a specific example of a seat member, is interposed between the fuel pump mounting portion 90 and the body 1. As shown in FIG. This O-ring 93 prevents engine oil from leaking outside the engine (internal combustion engine) through between the fuel pump mounting portion 90 and the body 1 .

A cylinder 6 for guiding the reciprocating motion of the plunger 2 is attached to the body 1 of the high-pressure fuel supply pump 100 . The cylinder 6 is formed in a tubular shape and is press-fitted into the body 1 at its outer peripheral side. The body 1 and the cylinder 6 form a pressure chamber 11 together with the electromagnetic intake valve 3, plunger 2 and discharge valve 8 (see FIG. 4).

The body 1 is provided with a fixing portion 1c that engages with the central portion of the cylinder 6 in the axial direction.
The fixing portion 1c of the body 1 presses the cylinder 6 upward (upward in FIG. 2) so that the fuel pressurized in the pressure chamber 11 does not leak from between the upper end surface of the cylinder 6 and the body 1. I'm trying

A tappet 92 is provided at the lower end of the plunger 2 to convert the rotary motion of a cam 91 attached to the camshaft of the engine into vertical motion and transmit the vertical motion to the plunger 2 . The plunger 2 is urged toward the cam 91 by the spring 16 via the retainer 15 and pressed against the tappet 92 . The tappet 92 reciprocates as the cam 91 rotates. The plunger 2 reciprocates together with the tappet 92 to change the volume of the pressurization chamber 11 .

A seal holder 17 is arranged between the cylinder 6 and the retainer 15 . The seal holder 17 is formed in a cylindrical shape into which the plunger 2 is inserted, and has an auxiliary chamber 17a at the upper end portion on the cylinder 6 side. In addition, the seal holder 17 holds a plunger seal 18 at the lower end on the retainer 15 side.

The plunger seal 18 is in slidable contact with the outer circumference of the plunger 2, and when the plunger 2 reciprocates, it seals the fuel in the auxiliary chamber 17a and prevents the fuel in the auxiliary chamber 17a from flowing into the engine. there is The plunger seal 18 also prevents lubricating oil (including engine oil) that lubricates the sliding parts in the engine from flowing into the body 1 .

In FIG. 2, the plunger 2 reciprocates vertically. If the plunger 2 descend|falls, the volume of the pressurization chamber 11 will expand, and if the plunger 2 raises, the volume of the pressurization chamber 11 will reduce.
That is, the plunger 2 is arranged so as to reciprocate in the direction of expanding and contracting the volume of the pressurizing chamber 11 .

The plunger 2 has a large diameter portion 2a and a small diameter portion 2b. When the plunger 2 reciprocates, the large diameter portion 2a and the small diameter portion 2b are positioned in the auxiliary chamber 17a. Therefore, the volume of the auxiliary chamber 17a increases and decreases as the plunger 2 reciprocates.

The auxiliary chamber 17a communicates with the low-pressure fuel chamber 10 through a fuel passage 10c (see FIG. 4). When the plunger 2 moves downward, fuel flows from the auxiliary chamber 17a to the low-pressure fuel chamber 10. When the plunger 2 moves upward, fuel flows from the low-pressure fuel chamber 10 to the auxiliary chamber 17a. As a result, the flow rate of fuel into and out of the high-pressure fuel supply pump 100 during the intake stroke or return stroke of the high-pressure fuel supply pump 100 can be reduced, and the pressure pulsation generated inside the high-pressure fuel supply pump 100 can be reduced.

Further, the body 1 is provided with a relief valve mechanism 4 communicating with the pressurizing chamber 11 . The relief valve mechanism 4 operates when a problem occurs in the common rail 106 or the members behind it, and the pressure in the common rail 106 exceeds a predetermined pressure and becomes high pressure. 11 is a valve configured to return to 11.

The relief valve mechanism 4 has a relief spring 41 , a relief valve holder 42 , a relief valve 43 and a seat member 44 . The relief spring 41 has one end in contact with the body 1 and the other end in contact with the relief valve holder 42 . The relief valve holder 42 is engaged with the relief valve 43 , and the biasing force of the relief spring 41 acts on the relief valve 43 via the relief valve holder 42 .

The relief valve 43 is pressed by the biasing force of the relief spring 41 and closes the fuel passage of the seat member 44 . A fuel passage of the seat member 44 communicates with the discharge passage 12a. Movement of fuel between the pressurizing chamber 11 (upstream side) and the sheet member 44 (downstream side) is blocked by the relief valve 43 contacting (adhering to) the sheet member 44 .

When the pressure in the common rail 106 and its members increases, the fuel on the side of the seat member 44 presses the relief valve 43 to move the relief valve 43 against the urging force of the relief spring 41 . As a result, the relief valve 43 is opened, and the fuel in the discharge passage 12 a returns to the pressurization chamber 11 through the fuel passage of the seat member 44 . Therefore, the pressure for opening the relief valve 43 is determined by the biasing force of the relief spring 41 .

Although the relief valve mechanism 4 of the present embodiment communicates with the pressurizing chamber 11, it is not limited to this, and communicates with, for example, a low-pressure passage (low-pressure fuel suction port 51, suction passage 10b, etc.). You may make it

As shown in FIG. 3, the body 1 of the high-pressure fuel supply pump 100 is provided with a low-pressure fuel chamber 10 . A suction joint 5 is attached to a side portion of the low-pressure fuel chamber 10 . The intake joint 5 is connected to a low-pressure pipe 104 through which fuel supplied from a fuel tank 103 passes. Fuel in the fuel tank 103 is supplied from the intake joint 5 to the inside of the high-pressure fuel supply pump 100 .

The suction joint 5 has a low-pressure fuel suction port 51 connected to the low-pressure pipe 104 and a suction passage 52 communicating with the low-pressure fuel suction port 51 . Fuel passing through the intake passage 52 reaches the intake port 335a (see FIG. 2) of the electromagnetic intake valve 3 via the pressure pulsation reduction mechanism 9 and the intake passage 10b (see FIG. 2) provided in the low-pressure fuel chamber 10. . A suction filter 53 is arranged in the suction flow path 52 . The suction filter 53 removes foreign matter present in the fuel and prevents the foreign matter from entering the high-pressure fuel supply pump 100 .

The low-pressure fuel chamber 10 is provided with a low-pressure fuel flow path 10a and an intake passage 10b. The intake passage 10b communicates with the intake port 335a (see FIG. 2) of the electromagnetic intake valve 3, and the fuel passing through the low-pressure fuel passage 10a enters the intake port 335a of the electromagnetic intake valve 3 through the intake passage 10b. reach.

A pressure pulsation reduction mechanism 9 is provided in the low-pressure fuel flow path 10a. When the fuel that has flowed into the pressurized chamber 11 passes through the open electromagnetic intake valve 3 and is returned to the intake passage 10b (see FIG. 2), pressure pulsation occurs in the low-pressure fuel chamber 10. FIG. The pressure pulsation reducing mechanism 9 reduces pressure pulsation generated in the high-pressure fuel supply pump 100 from spreading to the low-pressure pipe 104 .

The pressure pulsation reducing mechanism 9 is formed of a metal diaphragm damper in which two corrugated disk-shaped metal plates are pasted together at their outer peripheries and an inert gas such as argon is injected inside. The metal diaphragm damper of the pressure pulsation reducing mechanism 9 absorbs or reduces pressure pulsation by expanding and contracting.

The discharge valve 8 is connected to the outlet side of the pressurization chamber 11 . As shown in FIG. 4, the discharge valve 8 includes a discharge valve seat 81 communicating with the pressurizing chamber 11, a valve body 82 contacting and separating from the discharge valve seat 81, and biasing the valve body 82 toward the discharge valve seat 81 side. and a discharge valve stopper 84 that determines the stroke (movement distance) of the valve body 82 .

Further, the discharge valve 8 has a plug 85 for blocking leakage of fuel to the outside. The discharge valve stopper 84 is press-fitted into the plug 85 . The plug 85 is welded to the body 1 at a weld 86 . The discharge valve 8 communicates with a discharge valve chamber 87 that is opened and closed by a valve body 82 . The discharge valve chamber 87 is formed in the body 1 and communicates with the fuel discharge port 12b through a horizontal hole formed in the body 1 and extending in the horizontal direction.

A discharge joint 12 is inserted into a lateral hole formed in the body 1 . The discharge joint 12 has the above-described discharge passage 12a communicating with the lateral hole, and a fuel discharge port 12b that is one end of the discharge passage 12a. A fuel discharge port 12 b of the discharge joint 12 communicates with the common rail 106 . In addition, the discharge joint 12 is fixed to the body 1 by welding with a welding portion 12c.

When there is no fuel pressure difference (fuel differential pressure) between the pressure chamber 11 and the discharge valve chamber 87, the valve body 82 is pressed against the discharge valve seat 81 by the biasing force of the discharge valve spring 83, and the discharge valve 8 is closed. is closed. When the fuel pressure in the pressure chamber 11 becomes higher than the fuel pressure in the discharge valve chamber 87, the valve body 82 moves against the biasing force of the discharge valve spring 83, and the discharge valve 8 is opened. Become.

When the discharge valve 8 is closed, the (high-pressure) fuel in the pressure chamber 11 passes through the discharge valve 8 and reaches the discharge valve chamber 87 . The fuel reaching the discharge valve chamber 87 is discharged through the fuel discharge port 12b of the discharge joint 12 to the common rail 106 (see FIG. 1). With the configuration described above, the discharge valve 8 functions as a check valve that limits the flow direction of the fuel.

[Electromagnetic suction valve]
Next, the configuration of the electromagnetic suction valve 3 will be described with reference to FIGS. 2 and 5. FIG.
FIG. 5 is a cross-sectional view of an exploded electromagnetic intake valve in the high-pressure fuel supply pump 100. As shown in FIG.

As shown in FIG. 2, the electromagnetic intake valve 3 is composed of a coil unit 31, an anchor unit 32, a valve body unit 33, and a stopper .

(coil unit)
The coil unit 31 has a base member 311 fitted to the anchor unit 32 , an electromagnetic coil 312 fixed to the base member 311 , and terminal members 313 connected to the electromagnetic coil 312 .

The base member 311 is molded from a resin material or the like, and a bobbin 315 is joined thereto. The bobbin 315 and the base member 311 form a fitting hole 316 into which a housing 321 (described later) of the anchor unit 32 is fitted. The electromagnetic coil 312 is wound around a bobbin 315 and arranged to go around the anchor unit 32 fitted in the fitting hole 316 .

A portion of the terminal member 313 is embedded in the base member 311 and electrically connected to the electromagnetic coil 312 . On the other hand, the other part of the terminal member 313 is exposed to the outside, enabling connection between the terminal member 313 and the outside (power source). That is, current flows through the electromagnetic coil 312 via the terminal member 313 .

(anchor unit)
As shown in FIG. 5, the anchor unit 32 has a housing 321 , an anchor guide 322 , a magnetic core 323 , an anchor 324 , an anchor sleeve 325 and an anchor sleeve biasing spring 326 . Anchor sleeve biasing spring 326 represents one embodiment of a moveable member biasing member according to the present invention.

The housing 321 has a bottomed cylindrical housing body 321a and a joint projection 321b provided on the outer periphery of the housing body 321a on the opening side. The joint protrusion 321b is continuous in the circumferential direction of the housing body 321a and fits into a fitting hole provided in the body 1 (see FIG. 2). In addition, the coil unit 31 abuts on the end surface of the joint protrusion 321b facing the bottom side of the housing body 321a.

The anchor guide 322 is arranged inside the housing body 321a. The anchor guide 322 is formed in a cylindrical shape, and includes a large diameter portion 322a fixed to the bottom portion of the housing body 321a, and a small diameter portion 322b continuous with the large diameter portion 322a and having a smaller diameter than the large diameter portion 322a. have.

The magnetic core 323 is arranged inside the housing main body 321a. It is formed in a cylindrical shape, and the outer peripheral portion is in contact with the inner peripheral portion of the housing main body 321a. A large-diameter portion 322a of an anchor guide 322 is fitted to one axial end of the magnetic core 323 (the end on the bottom side of the housing body 321a). The inner peripheral portion of the magnetic core 323 excluding one end faces the outer peripheral portion of the small diameter portion 322b of the anchor guide 322 with a predetermined distance therebetween. The other axial end of the magnetic core 323 faces the anchor 324 .

The anchor 324 and the anchor sleeve 325 are the integrally assembled movable portion 320 and are movably disposed within the housing body 321a. The anchor 324 is formed in the shape of a cylinder, and its outer peripheral portion is slidably engaged with the inner peripheral portion of the housing main body 321a. One axial end of the anchor 324 faces the other end of the magnetic core 323 .

The anchor sleeve 325 has a fixed tubular portion 328 that is press-fitted and fixed to the inner peripheral portion of the anchor 324, and a contact portion 329 that is continuous with the fixed tubular portion. The inner peripheral portion of the fixed cylindrical portion 328 is slidably engaged with the outer peripheral portion of the small diameter portion 322b of the anchor guide 322. As shown in FIG. One axial end of the fixed tubular portion 328 is arranged inside the anchor 324 . The abutting portion 329 is continuous with the other axial end of the fixed tubular portion 328 and is formed in a disk shape with an outer diameter larger than the outer diameter of the fixed tubular portion 328 . A through hole 329 a communicating with the cylindrical hole of the fixed cylindrical portion 328 is formed in the contact portion 329 .

The anchor sleeve biasing spring 326 is fitted between the outer peripheral portion of the small diameter portion 322 b of the anchor guide 322 and the inner peripheral portion of the magnetic core 323 . One end of the anchor sleeve biasing spring 326 contacts the large diameter portion 322 a of the anchor guide 322 , and the other end of the anchor sleeve biasing spring 326 contacts the fixed tubular portion 328 of the anchor sleeve 325 .

An anchor sleeve biasing spring 326 biases the movable portion 320 away from the magnetic core 323 . Therefore, a clearance is generated between the anchor 324 and the magnetic core 323 when no magnetic attraction force acts between the anchor 324 and the magnetic core 323 . On the other hand, when a magnetic attraction force acts between the anchor 324 and the magnetic core 323 , the movable part 320 moves against the biasing force of the anchor sleeve biasing spring 326 and the anchor 324 contacts the magnetic core 323 .

When the movable portion 320 moves away from the magnetic core 323 , it presses the valve member 332 of the valve unit 33 , which will be described later, so that the valve portion 339 of the valve member 332 is separated from the suction valve seat 331 , which will be described later. is in the open state. Hereinafter, the direction in which the movable portion 320 moves away from the magnetic core 323 is the valve opening direction. That is, the anchor sleeve biasing spring 326 biases the movable portion 320 in the valve opening direction.

(valve unit)
The valve body unit 33 has an intake valve seat 331 , a valve member 332 , a spring holder 333 and an intake valve biasing spring 334 . The intake valve seat 331 shows one specific example of the seat member according to the present invention. Also, the spring holder 333 shows a specific example of the biasing member holder according to the invention, and the intake valve biasing spring 334 shows a specific example of the valve biasing member according to the invention.

The intake valve seat 331 is formed in a cylindrical shape and has a large diameter seat portion 335 and a small diameter seat portion 336 that is continuous with the large diameter seat portion 335 . The large-diameter seat portion 335 is press-fitted and fixed to the body 1 , and the small-diameter seat portion 336 is press-fit and fixed to the inner peripheral side of the housing 321 (housing main body 321 a ) of the anchor unit 32 .

The large-diameter seat portion 335 is formed with a suction port 335a reaching from the outer peripheral portion to the inner peripheral portion. The intake port 335a communicates with the intake passage 10b (see FIG. 2) in the low-pressure fuel chamber 10 described above. The end surface of the large-diameter seat portion 335 opposite to the small-diameter seat portion 336 is a seating surface 335b on which a valve portion 339 of the valve member 332, which will be described later, is seated. The seating surface 335b is formed on a plane orthogonal to the axial direction of the large-diameter seat portion 335. As shown in FIG.

Further, an inner peripheral guide portion 337 is provided on the inner peripheral portion of the large-diameter seat portion 335 . The inner peripheral guide portion 337 is formed in a plate shape having a plane perpendicular to the axial direction of the large-diameter seat portion 335, and has a through hole through which a rod 338 portion (described later) of the valve member 332 passes. The inner peripheral guide portion 337 slidably holds the rod portion 338 of the valve member 332 .

The valve member 332 has a cylindrical rod portion 338 and a valve portion 339 connected to one axial end of the rod portion 338 . The rod portion 338 is arranged inside the intake valve seat 331 , and the valve portion 339 faces the seating surface 335 b of the intake valve seat 331 . An intermediate portion of the rod portion 338 is slidably held by the inner peripheral guide portion 337 of the intake valve seat 331 . Further, the contact portion 329 of the anchor sleeve 325 in the suction valve seat 331 engages with the other axial end portion of the rod portion 338 .

The valve portion 339 is formed in a disc shape having a diameter larger than the diameter of the inner peripheral portion of the large-diameter seat portion 335, and includes a valve portion seat surface 339a facing the seating surface 335b of the intake valve seat 331 and a valve portion seat surface 339a. It has a seat surface 339a and a contact surface 339b on the opposite side.

The valve portion seat surface 339a is formed on a plane orthogonal to the valve opening direction (valve closing direction), and contacts the seating surface 335b of the intake valve seat 331 when the electromagnetic intake valve 3 is in the closed state. That is, the valve portion 339 is seated on the seating surface 335b of the intake valve seat 331 by the valve portion seat surface 339a coming into contact with the seating surface 335b of the intake valve seat 331 .

A contact surface 339b of the valve portion 339 is formed in a tapered shape that protrudes toward the central portion. The contact surface 339b contacts a bottom portion 341 of the stopper 34, which will be described later, when the electromagnetic suction valve 3 is open. Further, the contact surface 339b is provided with an engaging projection 339c that engages with an engaging hole 341a of the stopper 34, which will be described later.

The spring holder 333 is cylindrical and has a flange with which one end of the intake valve biasing spring 334 abuts. The spring holder 333 is press-fitted and fixed to the end of the rod portion 338 opposite to the valve portion 339 side. That is, the spring holder 333 is assembled integrally with the valve member 332 and constitutes the movable portion 330 .

The length from the guide portion center, which is the center of the direction in which the rod portion 338 extends in the inner peripheral guide portion 337 (the direction parallel to the valve closing direction and the valve opening direction) to the other end portion of the rod portion 338, is It is shorter than the length to the end of the valve portion 339 opposite to the rod portion 338 side (the tip of an engaging projection 339c described later). By shortening the length from the center of the guide portion to the other end of the rod portion 338, the length of which can be set regardless of the size of the intake valve seat 331, the size (reduction) of the movable portion 330 can be reduced. can be planned. As a result, it becomes possible to improve the responsiveness of the movable part 330 .

The intake valve biasing spring 334 is arranged upstream (opposite to the pressurizing chamber 11 ) of the inner peripheral guide portion 337 , and is positioned inside the small diameter seat portion 336 of the intake valve seat 331 . It is fitted between the peripheral portion and the outer peripheral portion of the spring holder 333 . One end of the intake valve biasing spring 334 contacts the flange of the spring holder 333 , and the other end of the suction valve biasing spring 334 contacts the inner peripheral guide portion 337 of the suction valve seat 331 .

The suction valve biasing spring 334 biases the valve member 332 in the direction in which the valve portion 339 approaches the seating surface 335 b of the suction valve seat 331 . Hereinafter, the direction in which the valve portion 339 approaches the seating surface 335b of the intake valve seat 331 is defined as the valve closing direction. That is, the suction valve biasing spring 334 biases the valve member 332 (movable portion 330) in the valve closing direction.

The biasing force of the intake valve biasing spring 334 is set to be smaller than the biasing force of the anchor sleeve biasing spring 326 . Therefore, when no magnetic attraction force acts between the anchor 324 and the magnetic core 323 in the anchor unit 32, the anchor sleeve biasing spring 326 biases the movable portion 320 and the movable portion 330 in the valve opening direction. ing.
As a result, the valve portion seat surface 339a of the valve portion 339 is separated from the seating surface 335b of the suction valve seat 331, and the electromagnetic suction valve 3 is in the open state.

(Stopper)
The stopper 34 is fixed to the body 1 (see FIG. 2). The stopper 34 is formed in a bottomed cylindrical shape that is open on the valve member 332 side, and has a bottom portion 341 . The inner diameter of the stopper 34 is set larger than the outer diameter of the valve portion 339 . The bottom portion 341 of the stopper 34 restricts movement of the movable portion 330 (valve member 332 ) in the valve opening direction by contact with the valve portion 339 .

A bottom portion 341 of the stopper 34 is formed with an engagement hole 341a and a plurality of fuel passage holes 341b. The engagement hole 341a is provided in the central portion of the bottom portion 341, and the plurality of fuel passage holes 341b are arranged around the engagement hole 341a at appropriate intervals. When the electromagnetic intake valve 3 is open, the engagement hole 341a of the stopper 34 is engaged with the engagement protrusion 339c of the valve portion 339, and the bottom portion 341 of the stopper 34 is engaged with the contact surface 339b of the valve portion 339. abut. Therefore, the valve member 332 has a valve opening stroke (a stroke from the valve closed state to the valve open state) defined by the stopper 34 .

[Operation of high-pressure fuel pump]
Next, the operation of the high-pressure fuel pump according to this embodiment will be described with reference to FIGS. 2, 6 and 7. FIG.
FIG. 6 is a cross-sectional view showing a state in which the electromagnetic intake valve 3 in the high-pressure fuel supply pump 100 is closed. FIG. 7 is a cross-sectional view showing a state in which the electromagnetic intake valve 3 in the high-pressure fuel supply pump 100 is closed.

In FIG. 2, when the plunger 2 descends and the electromagnetic intake valve 3 is open, fuel flows into the pressurization chamber 11 from the intake passage 1a. Hereinafter, the stroke in which the plunger 2 descends will be referred to as a suction stroke. On the other hand, when the plunger 2 rises and the electromagnetic intake valve 3 is closed, the pressure of the fuel in the pressurization chamber 11 is increased, and it passes through the discharge valve 8 and is pressure-fed to the common rail 106 (see FIG. 1). be. Hereinafter, the process in which the plunger 2 ascends will be referred to as an ascending stroke.

As described above, if the electromagnetic intake valve 3 is closed during the ascending stroke, the fuel sucked into the pressurization chamber 11 during the intake stroke is pressurized and discharged to the common rail 106 side. On the other hand, if the electromagnetic intake valve 3 is open during the ascending stroke, the fuel in the pressurization chamber 11 is pushed back toward the intake passage 1a and is not discharged toward the common rail 106 side. Thus, the discharge of fuel by the high-pressure fuel supply pump 100 is controlled by opening and closing the electromagnetic intake valve 3 . The opening and closing of the electromagnetic intake valve 3 is controlled by the ECU 101 .

In the intake stroke, the volume of the pressurization chamber 11 increases and the fuel pressure in the pressurization chamber 11 decreases. As a result, the fluid differential pressure between the intake port 335a and the pressurizing chamber 11 (hereinafter referred to as "fluid differential pressure across the valve portion 339") is reduced. When the biasing force of the anchor sleeve biasing spring 326 becomes greater than the differential pressure of the fluid across the valve portion 339, the movable portions 320 and 330 move in the valve opening direction, and the valve portion 339 is opened as shown in FIG. It leaves the seating surface 335b of the suction valve seat 331, and the electromagnetic suction valve 3 is opened.

When the electromagnetic intake valve 3 is opened, the fuel in the intake port 335a passes between the valve portion 339 and the intake valve seat 331, and flows into the pressurization chamber 11 through the plurality of fuel passage holes 341b of the stopper 34. do. When the electromagnetic suction valve 3 is open, the valve portion 339 is in contact with the stopper 34, so the position of the valve portion 339 in the valve opening direction is restricted. The gap between the valve portion 339 and the suction valve seat 331 in the open state of the electromagnetic suction valve 3 is the movable range of the valve portion 339, which is the valve opening stroke.

After completing the intake stroke, the process proceeds to the ascending stroke. At this time, the electromagnetic coil 312 remains in a non-energized state, and no magnetic attraction force acts between the anchor 324 and the magnetic core 323 . The valve member 332 (movable portion 330) is provided with an urging force in the valve opening direction corresponding to the difference in urging force between the anchor sleeve urging spring 326 and the intake valve urging spring 334, and the fuel from the pressurization chamber 11. A pressure force acts in the valve closing direction due to the fluid force generated when the fuel flows back into the low-pressure fuel passage 10a.

In this state, the difference in biasing force between the anchor sleeve biasing spring 326 and the suction valve biasing spring 334 is set larger than the fluid force so that the electromagnetic intake valve 3 maintains the open state. The volume of the pressurization chamber 11 decreases as the plunger 2 rises. Therefore, the fuel sucked into the pressurization chamber 11 passes again between the valve portion 339 and the intake valve seat 331 and is returned to the intake port 335a, and the pressure inside the pressurization chamber 11 rises. There is no such thing. This stroke is called a return stroke.

In the return process, when a control signal from the ECU 101 (see FIG. 1) is applied to the electromagnetic intake valve 3, current flows through the electromagnetic coil 312 via the terminal member 313. As shown in FIG. When a current flows through the electromagnetic coil 312 , a magnetic attractive force acts between the magnetic core 323 and the anchor 324 , and the anchor 324 (movable part 320 ) is attracted to the magnetic core 323 . As a result, the anchor 324 (movable portion 320 ) moves in the valve closing direction (away from the valve member 332 ) against the biasing force of the anchor sleeve biasing spring 326 .

A clearance between the anchor 324 and the magnetic core 323 is set to be larger than the valve opening stroke between the valve portion 339 and the intake valve seat 331 . For example, if the clearance between the anchor 324 and the magnetic core 323 is smaller than the valve opening stroke, the anchor 324 contacts the magnetic core 323 before the valve portion 339 contacts the intake valve seat 331 . As a result, the valve portion 339 and the intake valve seat 331 do not come into contact with each other, and the electromagnetic intake valve 3 cannot be closed.

On the other hand, if the clearance between the anchor 324 and the magnetic core 323 is too large, even if the electromagnetic coil 312 is energized, a sufficient magnetic attraction force cannot be obtained, and the electromagnetic suction valve 3 cannot be closed. Further, even if the electromagnetic intake valve 3 can be closed, the responsiveness of the electromagnetic intake valve 3 is degraded, resulting in high-pressure discharge during high-speed operation of the internal combustion engine (during high-speed rotation of the cam). Inability to control the amount of fuel. Therefore, the clearance between the anchor 324 and the magnetic core 323 is appropriately set according to the number of turns of the electromagnetic coil 312, the magnitude of the current flowing through the electromagnetic coil 312, and the like.

When the anchor 324 (movable portion 320) moves in the valve closing direction, the valve member 332 (movable portion 330) is released from the biasing force in the valve opening direction, and the biasing force of the intake valve biasing spring 334 and the fuel are sucked. It moves in the valve closing direction due to fluid force caused by flowing into the passage 10b. Then, as shown in FIG. 7, when the valve portion seat surface 339a of the valve portion 339 contacts the seating surface 335b of the intake valve seat 331 (the valve portion 339 is seated on the seating surface 335b), the electromagnetic intake valve 3 is The valve is closed.

After the electromagnetic intake valve 3 is closed, the pressure of the fuel in the pressure chamber 11 increases as the plunger 2 rises, and when it reaches a predetermined pressure or higher, it passes through the discharge valve 8 and passes through the common rail 106 (see FIG. 1). is discharged to This stroke is called a discharge stroke. That is, the upward stroke from the lower start point to the upper start point of the plunger 2 consists of a return stroke and a discharge stroke. By controlling the timing of energization of the electromagnetic coil 312 of the electromagnetic intake valve 3, the amount of high-pressure fuel to be discharged can be controlled.

If the timing of energizing the electromagnetic coil 312 is advanced, the proportion of the return stroke during the upward stroke becomes small, and the proportion of the discharge stroke becomes large. As a result, less fuel is returned to the intake passage 10b, and more fuel is discharged at high pressure. On the other hand, if the timing of energizing the electromagnetic coil 312 is delayed, the proportion of the return stroke in the upward stroke increases and the proportion of the ejection stroke decreases. As a result, more fuel is returned to the intake passage 10b, and less fuel is discharged at high pressure. By controlling the timing of energization of the electromagnetic coil 312 in this manner, the amount of fuel discharged at high pressure can be controlled to the amount required by the engine (internal combustion engine).

2. Summary As described above, the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment includes the valve member 332 (valve member), the intake valve seat 331 (seat member), and the intake valve biasing valve. and a spring 334 (valve biasing member). The valve member 332 has a rod portion 338 (rod portion) and a valve portion 339 (valve portion) connected to one end of the rod portion 338 . The intake valve seat 331 has an inner peripheral guide portion 337 (guide portion) that guides the outer periphery of the rod portion 338, and a seating surface 335b (seat surface) on which the valve portion 339 is seated. The suction valve biasing spring 334 biases the rod portion 338 in the valve closing direction, which is the direction in which the valve portion 339 approaches the seating surface 335b. In addition, the suction valve biasing spring 334 is arranged on the valve closing direction side of the inner circumferential guide portion 337 . The length from the center of the guide portion, which is the center of the inner peripheral guide portion 337 in the direction parallel to the valve closing direction, to the other end portion of the rod portion 338 is ) is shorter than the length of

As a result, in a state in which the valve portion 339 is seated on the seating surface 335b of the intake valve seat 331, the valve portion 339 is arranged in the pressurizing chamber 11, and the intake valve biasing spring 334 is positioned upstream of the valve portion 339 (intake port). 335a side). Therefore, it is not necessary to provide a space for arranging the intake valve biasing spring 334 in the pressurizing chamber 11, and the dead volume in the pressurizing chamber 11 can be reduced. As a result, the volume of the pressurization chamber 11 can be reduced, and the volumetric efficiency of the high-pressure fuel supply pump 100 can be improved. Further, by arranging the intake valve biasing spring 334 on the upstream side (intake port 335a side) of the valve portion 339, the intake valve biasing spring 334 is not covered with high fuel pressure fuel, and the intake valve biasing spring 334 is not covered with high fuel pressure fuel. It becomes possible to improve the durability of the force spring 334 .

The length from the guide portion center of the inner peripheral guide portion 337 to the other end portion of the rod portion 338 can be set regardless of the size of the intake valve seat 331 . Therefore, by shortening the length from the center of the guide portion to the other end portion of the rod portion 338, the size (reduction) of the movable portion 330 can be reduced. As a result, the responsiveness of the valve member 332 (movable portion 330) can be improved.

Further, the electromagnetic suction valve 3 (electromagnetic suction valve) according to one embodiment described above is attached to the other end of the rod portion 338 (rod portion) and holds the suction valve biasing spring 334 (valve biasing member). A spring holder 333 (biasing member holder) is provided. This allows the suction valve biasing spring 334 to be easily engaged with the rod portion 338 . Further, in the above-described embodiment, the length of the rod portion 338 is set so that the other end portion of the rod portion 338 reaches the press-fitting portion of the spring holder 333 . Thereby, the rod portion 338 can be shortened as much as possible, and the responsiveness of the valve member 332 (movable portion 330) can be improved.

Further, the electromagnetic suction valve 3 (electromagnetic suction valve) according to the embodiment described above includes a valve member 332 (valve member), a suction valve seat 331 (seat member), a suction valve biasing spring 334 (valve biasing member), and the spring holder 333 (biasing member holder) are assembled as one valve body unit (valve body unit 33). As a result, the valve member 332 urged by the intake valve urging spring 334 can be easily assembled to the body 1 of the high-pressure fuel supply pump 100 . workability can be improved.

Further, the electromagnetic suction valve 3 (electromagnetic suction valve) according to the above-described embodiment is configured separately from the valve body unit 33 (valve body unit), and the valve member 332 (valve member) is arranged in a direction different from the valve closing direction. It has a stopper 34 (stopper) that restricts the movement of the valve member 332 in the valve-opening direction by coming into contact with the valve portion 339 (valve portion) when the valve member 332 moves in the valve-opening direction, which is the opposite direction. Thereby, the valve opening stroke can be defined. In addition, the fluid force applied to the valve portion 339 in the return stroke described above can be reduced, and the force required to keep the electromagnetic intake valve 3 open can be reduced. Further, since the stopper 34 is configured separately from the valve body unit 33, the stopper 34 can be assembled to the body 1 alone.

For example, if the stopper 34 is integrated with the valve body unit 33 , the stopper 34 needs to be press-fitted onto the outer periphery of the suction valve seat 331 . However, since the outer periphery of the intake valve seat 331 is press-fitted into the body 1, the location where the stopper 34 is press-fitted into the intake valve seat 331 and the location where the intake valve seat 331 is press-fitted into the body 1 are the same location. entered.

First, when the stopper 34 is press-fitted into the intake valve seat 331, the outer peripheral portion of the stopper 34 is deformed. Since the amount of deformation of the stopper 34 varies, variations in the press-fitting load when the intake valve seat 331 is press-fitted into the body 1 become large. As a result, the press-fitting load when press-fitting the intake valve seat 331 into the body 1 tends to be excessive, and the intake valve seat 331 may not be assembled with the body 1 in some cases.

In contrast, the electromagnetic suction valve 3 according to the above-described embodiment can avoid double press-fitting. As a result, it is possible to reduce variations in the press-fitting load when the intake valve seat 331 is press-fitted into the body 1, and to prevent the press-fitting load from becoming excessive.

Further, in the electromagnetic suction valve 3 (electromagnetic suction valve) according to the above-described embodiment, the other end of the rod portion 338 is configured separately from the rod portion 338, and the movable portion 320 that drives the rod portion 338 (movable part). In this way, since the rod portion 338 and the movable portion 320 are configured separately, the size of the rod portion 338 can be reduced, and the responsiveness of the valve member 332 (movable portion 330) can be improved. .

Further, in the electromagnetic suction valve 3 (electromagnetic suction valve) according to the above-described embodiment, the rod portion The other end of 338 is pressed in the valve opening direction, which is the opposite direction to the valve closing direction. Thus, in a state where no force is applied to move the movable portion 320 in the valve closing direction, a force can be applied to the rod portion 338 (valve member 332) against the biasing force of the suction valve biasing spring 334. The open state of the electromagnetic suction valve 3 can be easily maintained.

Further, the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment is arranged on the side of the valve closing direction relative to the movable portion 320 (movable portion), and the movable portion 320 is arranged in the direction opposite to the valve closing direction. The movable portion 320 is attracted in the valve closing direction by an electromagnetic attraction force generated by energizing the anchor sleeve biasing spring 326 (moving portion biasing member) and the electromagnetic coil 312 (coil) that biases the valve in a certain valve opening direction. and a magnetic core 323 (magnetic core). When the electromagnetic coil 312 is de-energized, the movable portion 320 is biased in the valve opening direction by the anchor sleeve biasing spring 326, and the intake valve biasing spring 334 (valve biasing member) is biased. The valve member 332 is moved in the valve opening direction against the force. As a result, only the movable portion 320 collides with the magnetic core 323 due to the magnetic attraction force, and the mass of the valve member 332 is not added to the collision. Therefore, the mass that collides with the magnetic core 323 can be reduced, and the sound generated by the collision can be reduced. In addition, the electromagnetic intake valve 3 can be opened when the electromagnetic coil 312 is de-energized.

Further, in the electromagnetic suction valve 3 (electromagnetic suction valve) according to the above-described embodiment, in a state where the movable portion 320 (movable portion) is attached to the valve body unit 33 (valve body unit), the movable portion 320 is The other end of the rod portion 338 (rod portion) is biased in the valve opening direction, and the valve portion 339 of the valve member 332 is brought into contact with the stopper 34 , thereby setting the valve opening stroke of the valve portion 339 . As a result, the valve opening stroke can be easily set only by assembling the electromagnetic intake valve 3 with the respective parts such as the valve body unit 33, the stopper 34 and the movable portion 320. FIG.

Further, in the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment, the valve portion 339 (valve portion) is formed on a plane perpendicular to the valve closing direction, and contacts the seating surface 335b (seating surface). It has a valve seat surface 339a (valve seat surface), and a seating surface 335b (seat surface) of the intake valve seat 331 (seat member) is formed in a plane orthogonal to the valve closing direction. As a result, the sealing performance when the valve seat surface 339a contacts the seating surface 335b can be ensured, and the workability of the valve seat surface 339a and the seating surface 335b can be improved. For example, if the valve portion seat surface 339a and the seating surface 335b are tapered surfaces, it is necessary to increase the precision of the taper angles of both in order to ensure sealing performance. sexuality worsens.

Further, in the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment, the movable portion 320 (movable portion) is positioned closer to the inner peripheral guide portion 337 (guide portion) than the intake valve seat 331 (seat member). It contacts with the other end of the rod portion 338 on the valve closing direction side. As a result, the other end of the rod portion 338 does not protrude outside the suction valve seat 331, so that the rod portion 338 can be made smaller, and the responsiveness of the valve member 332 (movable portion 330) can be improved. can.

The embodiments of the electromagnetic intake valve and the high-pressure fuel supply pump of the present invention have been described above, including their effects. However, the electromagnetic intake valve and high-pressure fuel supply pump of the present invention are not limited to the above-described embodiments, and various modifications can be made without departing from the gist of the invention described in the claims. be. Further, the above-described embodiments have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the described configurations.

For example, in the embodiment described above, the valve opening stroke of the valve portion 339 is set by the valve portion 339 of the valve member 332 coming into contact with the stopper 34 . However, as the electromagnetic intake valve according to the present invention, the spring holder 333 may be brought into contact with the inner peripheral guide portion 337, and a predetermined valve opening stroke may be set at this time.

However, in the case of the configuration in which the spring holder 333 is brought into contact with the inner peripheral guide portion 337, the impact caused by the opening and closing of the electromagnetic suction valve exceeds the press-fit load of the spring holder 333 while the electromagnetic suction valve repeats opening and closing. As a result, the press-fitting position of the spring holder 333 shifts. As a result, the valve opening stroke may change.

If the valve opening stroke is greater than a predetermined amount, the time required for the valve member 332 to start moving in the valve closing direction after the electromagnetic coil 312 is energized and contact the intake valve seat 331 to completely close the valve is the opening time. longer than for a given amount of valve stroke. Therefore, when the internal combustion engine is running at high speed (when the cam rotates at high speed), the responsiveness is insufficient, the electromagnetic intake valve 3 cannot be closed at the target timing, and the amount of fuel discharged at high pressure cannot be controlled. . Therefore, the valve opening stroke is set to a value that allows the amount of high-pressure fuel to be controlled even when the cam rotates at high speed.

Further, when the valve opening stroke is smaller than a predetermined amount, the fluid force generated in the valve portion 339 in the return process of the high-pressure fuel supply pump 100 (the closing force generated by the fuel flowing back from the pressurization chamber 11 to the low-pressure fuel flow path 10a) is reduced. force in the direction of the valve) increases. In this case, the electromagnetic intake valve 3 closes at an unexpected timing during the return process, making it impossible to control the amount of fuel discharged at high pressure. Therefore, the valve opening stroke is set to a value that does not cause the electromagnetic intake valve 3 to close even when the cam rotates at high speed.

DESCRIPTION OF SYMBOLS 1... Body 2... Plunger 3... Electromagnetic suction valve 4... Relief valve mechanism 5... Suction joint 6... Cylinder 8... Discharge valve 9... Pressure pulsation reducing mechanism 10... Low pressure fuel chamber 10a... Low pressure Fuel flow path 10b Suction passage 11 Pressure chamber 12 Discharge joint 31 Coil unit 32 Anchor unit 33 Valve unit 34 Stopper 100 High-pressure fuel supply pump 101 ECU , 102... Feed pump 103... Fuel tank 104... Low pressure pipe 105... Fuel pressure sensor 106... Common rail 107... Injector 311... Base member 312... Electromagnetic coil 313... Terminal member 315... Bobbin 316 Fitting hole 320 Movable part 321 Housing 322 Anchor guide 323 Magnetic core 324 Anchor 325 Anchor sleeve 330 Movable part 331 Suction valve seat 332 Valve member 333 Spring holder 335a Suction port 335b Seating surface 337 Inner guide part 338 Rod part 339 Valve part 339a Valve seat surface 339b Contact surface 339c Engagement projection 341... Bottom 341a... Engagement hole 341b... Fuel passage hole

Claims (10)

a valve member having a rod portion and a valve portion connected to one end of the rod portion;
a seat member having a guide portion that guides the outer periphery of the rod portion and a seating surface on which the valve portion is seated;
a valve biasing member that biases the rod portion in a valve closing direction in which the valve portion approaches the seating surface;
a stopper that restricts movement of the valve member in the valve-opening direction by coming into contact with the valve portion when the valve member moves in the valve-opening direction that is opposite to the valve-closing direction; prepared,
The valve biasing member is arranged on the valve closing direction side of the guide portion,
The length from the guide portion center, which is the center of the guide portion in the direction parallel to the valve closing direction, to the other end portion of the rod portion is shorter than the length from the guide portion center to the tip of the valve portion. ,
The stopper has an engagement hole with which the tip of the valve portion engages.
Electromagnetic intake valve. 2. The electromagnetic intake valve according to claim 1, further comprising a biasing member holder attached to the other end of said rod portion and holding said valve biasing member. 3. The electromagnetic intake valve according to claim 2, wherein the valve member, the seat member, the valve biasing member, and the biasing member holder are assembled as one valve body unit. 2. The electromagnetic intake valve according to claim 1, wherein the other end of the rod portion is configured separately from the rod portion and contacts a movable portion that drives the rod portion. The movable portion presses the other end portion of the rod portion in a valve opening direction opposite to the valve closing direction in a state where no force is applied to move the movable portion in the valve closing direction. The electromagnetic intake valve according to claim 4 . a movable portion biasing member disposed on the valve closing direction side of the movable portion and biasing the movable portion in the valve opening direction, which is a direction opposite to the valve closing direction;
a magnetic core that attracts the movable portion in the valve closing direction by an electromagnetic attraction force generated by energizing the coil;
When the coil is de-energized, the movable portion is biased in the valve opening direction by the movable portion biasing member, and moves the valve member in the valve opening direction against the biasing force of the valve biasing member. 5. The electromagnetic suction valve according to claim 4 . a biasing member holder attached to the other end of the rod portion and holding the valve biasing member;
The valve member, the seat member, the valve biasing member, and the biasing member holder are assembled as one valve body unit,
In a state in which the movable portion is attached to the valve body unit, the movable portion biases the other end portion of the rod portion in the valve opening direction, and the valve portion of the valve member acts against the stopper. The electromagnetic intake valve according to claim 6 , wherein the valve opening stroke of the valve portion is set by contact. The valve portion is formed on a plane orthogonal to the valve closing direction and has a valve portion seat surface that contacts the seating surface,
The electromagnetic intake valve according to claim 1, wherein the seating surface of the seat member is formed on a plane perpendicular to the valve closing direction. The electromagnetic intake valve according to claim 4 , wherein the movable portion contacts the other end portion of the rod portion on the valve closing direction side of the guide portion in the seat member. a body with a pressurized chamber;
a plunger that is reciprocally supported by the body and that reciprocates to increase or decrease the volume of the pressurizing chamber;
and an electromagnetic suction valve that discharges fuel to the pressurized chamber,
The electromagnetic suction valve is
a valve member having a rod portion and a valve portion connected to one end of the rod portion;
a seat member having a guide portion that guides the outer periphery of the rod portion and a seating surface on which the valve portion is seated;
a valve biasing member that biases the rod portion in a valve closing direction in which the valve portion approaches the seating surface;
a stopper that restricts movement of the valve member in the valve-opening direction by coming into contact with the valve portion when the valve member moves in the valve-opening direction that is opposite to the valve-closing direction; have
The valve biasing member is arranged on the valve closing direction side of the guide portion,
The length from the guide portion center, which is the center of the guide portion in the direction parallel to the valve closing direction, to the other end portion of the rod portion is shorter than the length from the guide portion center to the tip of the valve portion. ,
The stopper has an engagement hole with which the tip of the valve portion engages.
High pressure fuel supply pump.

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