DE112020003215T5 - Electromagnetic inlet valve and high pressure fuel supply pump - Google Patents

Abstract

An electromagnetic intake valve capable of reducing a dead volume in a pressure chamber is provided. An electromagnetic intake valve of the present invention includes a valve member, a seat member, and a valve biasing member. The valve element has a rod portion and a valve portion provided at an end portion 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 valve biasing member biases the rod portion in a direction in which the valve portion approaches the seating surface. Moreover, the valve biasing member is disposed on the valve closing direction side with respect to the guide portion. A length from a center of the guide portion, which is a center in a direction parallel to the valve closing direction, to the other end portion of the rod portion is shorter than a length from the center of the guide portion to a tip of the valve portion.

Description

technical field

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

State of the art

A high-pressure fuel supply pump is described in PTL 1, for example. The high-pressure fuel supply pump described in PTL 1 includes an electromagnetic inlet valve. When the intake electromagnetic valve is in a non-energized state in which an electromagnetic coil is not energized, a valve body is biased by a biasing force of a spring and thus the intake electromagnetic valve is opened. Meanwhile, when the electromagnetic coil is excited, a magnetic attraction force is generated and thus the valve body moves against the biasing force of the spring and the intake electromagnetic valve is closed. As described above, the intake electromagnetic valve performs opening/closing motion depending on whether the electromagnetic coil is energized and controls a supply amount of high-pressure fuel.

citation list

patent document(s)

PTL 1: JP 2013-148025 A

Summary of the Invention

Technical problem

However, in the electromagnetic inlet valve of the high-pressure fuel supply pump described in PTL 1, the spring that biases the valve body is disposed in a pressure chamber. Therefore, a dead volume in the pressure chamber increases, and the delivery rate of the high-pressure fuel supply pump deteriorates.

In view of the above problems, an object of the present invention is to provide an electromagnetic intake valve and a high-pressure fuel supply pump capable of reducing a dead volume in a pressure chamber.

solution to the problem

In order to solve the above problems and the object of the present invention, a high-pressure fuel supply pump of the present invention includes a valve member, a seat member, and a biasing member. The valve element includes a rod portion and a valve portion provided at an end portion of the rod portion. The seat member includes 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. A length from a center of the guide portion, which is a center in a direction in which a rod extends, to the other end portion of the rod portion is shorter than a length from the center of the guide portion to a tip of the valve portion.

Advantageous Effects of the Invention

According to the high-pressure fuel supply pump having the above configuration, a dead volume in the pressure chamber can be reduced. Objects, configurations and effects other than those described above will be clarified by the following descriptions of embodiments.

character list

• [ 1 ] 1 14 is an overall configuration diagram of a fuel supply system using a high-pressure fuel supply pump according to an embodiment of the present invention.
• [ 2 ] 2 12 is a longitudinal sectional view (part 1) of the high-pressure fuel supply pump according to the embodiment of the present invention.
• [ 3 ] 3 12 is a longitudinal sectional view (part 2) of the high-pressure fuel supply pump according to the embodiment of the present invention.
• [ 4 ] 4 14 is a horizontal cross-sectional view of the high-pressure fuel supply pump according to the embodiment of the present invention as viewed from above.
• [ 5 ] 5 14 is an exploded cross-sectional view of the electromagnetic inlet valve in the high-pressure fuel supply pump according to the embodiment of the present invention.
• [ 6 ] 6 14 is an enlarged cross-sectional view of an electromagnetic inlet valve in the high-pressure fuel supply pump according to the embodiment of the present invention, and shows a state in FIG which the electromagnetic inlet valve is open.
• [ 7 ] 7 14 is an enlarged cross-sectional view of an electromagnetic inlet valve in the high-pressure fuel supply pump according to the embodiment of the present invention, and shows a state where the electromagnetic inlet valve is closed.

Description of Embodiments

1st embodiment

A high-pressure fuel supply pump according to an embodiment of the present invention will be described below. Common elements in each drawing are represented by the same reference numbers.

[fuel supply system]

Next, a fuel supply system using the high-pressure fuel supply pump according to the present embodiment will be described with reference to FIG 1 described.

1 14 is an overall configuration diagram of the fuel supply system using the high-pressure fuel supply pump according to the present embodiment.

like it in 1 As shown, the fuel supply system includes a high pressure fuel supply pump 100, an engine control unit (ECU) 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 integrated into a body 1.

A fuel in the fuel tank 103 is pumped up by a charge 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 through a low pressure pipe 104 to a low pressure fuel inlet port 51 of the high pressure fuel supply pump 100 .

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

The fuel pressure sensor 105 outputs the detected pressure data to the ECU 101 . The ECU 101 calculates an appropriate injection fuel amount (target injection fuel length), an appropriate fuel pressure (target fuel pressure), and the like based on engine state quantities (e.g., a crank angle, a throttle opening, an engine speed, a fuel pressure, and the like) obtained from various sensors.

In addition, the ECU 101 controls driving of the high-pressure fuel supply pump 100 and the plurality of injectors 107 based on a calculation result of the fuel pressure (target fuel pressure) or the like. That is, the ECU 101 includes a pump control unit that controls the high-pressure fuel supply pump 100 and an injector control unit that controls the injector 107 .

The high-pressure fuel supply pump 100 includes a pressure pulsation reducing mechanism 9, an electromagnetic intake valve 3 which is a variable capacity mechanism, a relief valve mechanism 4 (see 2 ) and an exhaust valve 8. The fuel flowing in from the low-pressure fuel inlet port 51 reaches an inlet port 335a of the electromagnetic inlet valve 3 via the pressure pulsation reducing mechanism 9 and an inlet passage 10b.

The fuel flowing into the electromagnetic intake valve 3 passes through the valve portion 339, flows through the intake passage 1a formed in the body 1, and then flows into a pressure chamber 11. A piston 2 is held in the pressure chamber 11 in a slidable manner. The piston 2 reciprocates when force is applied from a cam 91 (see 2 ) is transmitted to the prime mover.

In the pressure chamber 11, fuel is sucked in from the electromagnetic intake valve 3 on a downward stroke of the piston 2, and the fuel is pressurized on an upward stroke. When the fuel pressure in the pressure chamber 11 exceeds a predetermined value, the exhaust valve 8 is opened and the high-pressure fuel is supplied under pressure to the common rail 106 via an exhaust passage 12a. the Fuel delivery by the high-pressure fuel supply pump 100 is operated by opening and closing the intake electromagnetic valve 3 . The opening or closing of the intake electromagnetic valve 3 is controlled by the ECU 101 .

[High Pressure Fuel Supply Pump]

Next, a configuration of the high-pressure fuel supply pump 100 will be described with reference to FIG 2 until 4 described.

2 12 is a longitudinal cross-sectional view (part 1) of the high-pressure fuel supply pump 100 as viewed in a cross section perpendicular to a horizontal direction and FIG 3 14 is a longitudinal cross-sectional view (part 2) of the high-pressure fuel supply pump 100 as viewed in a cross section perpendicular to the horizontal direction. 4 12 is a horizontal cross-sectional view of the high-pressure fuel supply pump 100 viewed in a cross section perpendicular to the vertical direction.

like it in 2 until 4 As shown, the body 1 of the high-pressure fuel supply pump 100 includes the above-described intake port 1a and a 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 is fixed by a plurality of bolts (bolts) (not shown). That is, the high-pressure fuel supply pump 100 is fixed to the fuel pump attachment portion 90 through the attachment flange 1b.

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

A cylinder 6 which guides the reciprocation of the piston 2 is fixed to the body 1 of the high-pressure fuel supply pump 100. As shown in FIG. A cylinder 6 is formed into a tubular shape and press-fitted into the body 1 at an outer peripheral side thereof. The body 1 and the cylinder 6 form the pressure chamber 11 together with the electromagnetic inlet valve 3, the piston 2 and the outlet valve 8 (see 4 ).

The body 1 is provided with a fixing portion 1c engaged with a central portion of the cylinder 6 in an axial direction. The fixing portion 1c of the body 1 pushes the cylinder 6 upward (in 2 upward) so that the fuel pressurized in the pressure chamber 11 does not leak between an upper end surface of the cylinder 6 and the body 1.

A lower end of the piston 2 is provided with a plunger 92 which converts the rotary motion of a cam 91 fixed to a camshaft of the engine into vertical motion and transmits the vertical motion to the piston 2 . The plunger 2 is biased toward the cam 91 by a spring 16 via a retainer 15 and pinched against the plunger 92 . The plunger 92 reciprocates in accordance with the rotation of the cam 91 . The piston 2 reciprocates together with the plunger 92 to change a volume of the pressure chamber 11 .

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

The piston seal 18 is slidably in contact with an outer periphery of the piston 2 and seals the fuel in the auxiliary chamber 17a when the piston 2 reciprocates so that the fuel in the auxiliary chamber 17a does not flow into the engine. The piston seal 18 prevents lubricating oil (including engine oil) that lubricates a sliding portion in the engine from flowing into the body 1 .

In 2 the piston 2 reciprocates in an up-down direction. When the piston 2 is lowered, the volume of the pressure chamber 11 increases, and when the piston 2 is raised, the volume of the pressure chamber 11 decreases. That is, the piston 2 is arranged to reciprocate in a direction of increasing and decreasing the volume of the pressure chamber 11 .

The piston 2 has a large-diameter portion 2a and a small-diameter portion 2b. When the piston 2 reciprocates, the large-diameter portion 2a and the small-diameter portion 2b are in the auxiliary chamber 17a. Therefore, the volume of the auxiliary chamber 17a increases or decreases by the reciprocation of the piston 2.

The auxiliary chamber 17a communicates with the low-pressure fuel chamber 10 through a fuel passage 10c (see Fig 4 ). When the piston 2 is lowered, the fuel flows from the auxiliary chamber 17a into the low-pressure fuel chamber 10, and when the piston 2 is raised, the fuel flows from the low-pressure fuel chamber 10 into the auxiliary chamber 17a. As a result, a flow rate of fuel into and out of the pump in an intake stroke or a return stroke of the high-pressure fuel supply pump 100 can be reduced, and the pressure pulsation 100 generated in the high-pressure fuel supply pump 100 can be reduced.

The body 1 is provided with a relief valve mechanism 4 communicating with the pressure chamber 11 . The relief valve mechanism 4 is a valve configured to act and return the fuel in the discharge passage 12a to the pressure chamber 11 when a problem occurs in the common rail 106 or an element beyond the common rail 106 and the common rail unites reaches high pressure that exceeds a predetermined pressure.

The relief valve mechanism 4 includes a relief spring 41 , a relief valve holder 42 , a relief valve 43 and a seat member 44 . 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 through the relief valve holder 42.

The relief valve 43 is pressed by the biasing force of the relief spring 41 to close fuel passage of the seat member 44 . The fuel passage of the seat member 44 communicates with the outlet passage 12a. The movement of fuel between the pressure chamber 11 (upstream side) and the seat member 44 (downstream side) is blocked by the contact (close contact) of the relief valve 43 with the seat member 44 .

When the pressure in the common rail 106 or an element in front of the common rail increases, the fuel on the seat element 44 side presses the relief valve 43 to move the relief valve 43 against the biasing force of the relief spring 41 . As a result, the relief valve 43 is opened and the fuel in the outlet passage 12a returns to the pressure 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 .

The relief valve mechanism 4 of the present embodiment communicates with the pressure chamber 11, but is not limited thereto. For example, the relief valve mechanism 4 may communicate with a low-pressure passage (the low-pressure fuel inlet port 51, inlet passage 10b, or the like).

like it in 3 As shown, the body 1 of the high-pressure fuel supply pump 100 is provided with the low-pressure fuel chamber 10 . An inlet joint 5 is attached to a side surface portion of the low-pressure fuel chamber 10 . The inlet joint 5 is connected to the low-pressure pipe 104 through which the fuel supplied from the fuel tank 103 flows. The fuel in the fuel tank 103 is supplied from the inlet joint 5 to the inside of the high-pressure fuel supply pump 100 .

The intake connection 5 includes the low-pressure fuel intake port 51 connected to the low-pressure pipe 104 and an intake flow path 52 communicating with the low-pressure fuel intake port 51 . The fuel that has passed through the intake flow path 52 reaches an intake port 335a (see FIG 2 ) of the electromagnetic intake valve 3 via the pressure pulsation reducing mechanism 9 and the intake passage 10b (see 2 ) provided in the low-pressure fuel chamber 10 . An inlet filter 53 is arranged in the inlet flow path 52 . The inlet 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 port 10b. The inlet channel 10b communicates with the inlet port 335a (see 2 ) of the intake electromagnetic valve 3 communicates, and the fuel having passed through the low-pressure fuel flow path 10a reaches the intake port 335a of the intake electromagnetic valve 3 via the intake passage 10b.

The pressure pulsation reducing mechanism 9 is provided in the low-pressure fuel flow path 10a. When the fuel that has flowed into the pressure chamber 11 returns to the intake port 10b through the electromagnetic intake valve 3 in the valve opening state (see FIG 2 ) is returned, pressure pulsation occurs in the low-pressure fuel chamber 10. The pressure pulsation reduction mechanism 9 redu graces the propagation of the pressure pulsation generated in the high-pressure fuel supply pump 100 into the low-pressure pipe 104.

The pressure pulsation reducing mechanism 9 is composed of a metal diaphragm damper in which two corrugated disk-shaped metal plates are bonded to each other at their outer periphery and an inert gas such as argon is injected into the metal diaphragm damper. The metal diaphragm damper of the pressure pulsation reducing mechanism 9 expands and contracts to absorb or reduce pressure pulsation.

The outlet valve 8 is connected to the outlet side of the pressure chamber 11 . like it in 4 As shown, the exhaust valve 8 includes an exhaust valve seat 81 communicating with the pressure chamber 11, a valve body 82 coming into contact with and separating from the exhaust valve seat 81, an exhaust valve spring 83 biasing the valve body 82 toward the side of the exhaust valve seat 81 is biased, and an exhaust valve stopper 84 that determines a lift (moving distance) of the valve body 82 .

The outlet valve 8 includes a plug 85 which blocks the escape of fuel to the outside. The outlet valve stop 84 is pressed into the plug 85 . The plug 85 is connected to the pump body 1 by welding at a welded portion 86 . The discharge valve 8 communicates with a discharge valve chamber 87 which is opened and closed by the valve portion 82 . The outlet valve chamber 87 formed in the body 1 communicates with the fuel outlet port 12b via a side hole formed in the body 1 and extending in the horizontal direction.

In the lateral hole formed in the body 1, an outlet connection 12 is inserted. The outlet joint 12 includes the outlet passage 12a communicating with the side hole and the fuel outlet port 12b which is one end of the outlet passage 12a. The fuel outlet port 12b of the outlet joint 12 communicates with the common rail 106 . The outlet joint 12 is fixed to the body 1 by welding through a welded portion 12c.

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

When the outlet valve 8 is closed, the (high-pressure) fuel in the pressure chamber 11 passes through the outlet valve 8 and reaches the outlet valve chamber 87. Then the fuel that has reached the outlet valve chamber 87 is discharged through the fuel outlet port 12b of the outlet joint 12 to the common Bar 106 (see 1 ) submitted. With the above configuration, the exhaust valve 8 functions as a check valve that restricts a flow direction of fuel.

[Electromagnetic inlet valve]

Next, a configuration of the intake electromagnetic valve 3 will be described with reference to FIG 2 and 5 described.

5 12 is an exploded cross-sectional view of the electromagnetic inlet valve of the high-pressure fuel supply pump 100.

like it in 2 As shown, the electromagnetic intake valve 3 has a coil unit 31, an armature unit 32, a valve body unit 33 and a stopper 34.

(coil unit)

The coil unit 31 includes a base member 311 attached to the armature unit 32 , an electromagnetic coil 312 fixed to the base member 311 , and a terminal member 313 connected to the electromagnetic coil 312 .

The base member 311 is formed of a resin material or the like, and a coil bobbin 315 is assembled thereto. The bobbin 315 and the base member 311 form a fitting hole 316 into which a housing 321 (described later) of the armature unit 32 is fitted. The electromagnetic coil 312 is wound around the bobbin 315 and is arranged to make a round around the armature 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 . Meanwhile, the other portion of the connector 313 is exposed to the outside to allow connection between the connector 313 and the outside (power supply). That is, a current flows through the connection element 313 through the electromagnetic coil 312.

(anchor unit)

like it in 5 As shown, the armature unit 32 includes a housing 321, an armature guide 322, a magnetic core 323, an armature 324, an armature sleeve 325, and an armature sleeve biasing spring 326. The armature sleeve biasing spring 326 is a specific example of a movable portion biasing member according to FIG present invention.

The case 321 has a case main body 321a formed in a bottomed cylindrical shape, and a connecting projection 321b provided on an outer peripheral portion on an opening side of the case main body 321a. The connection projection 321b is continuous in the circumferential direction of the case main body 321a and fitted into a fitting hole provided in the body 1 (see FIG 2 ). In addition, the coil unit 31 abuts on an end face of the connecting projection 321b that faces a bottom portion side of the case main body 321a.

The armature guide 322 is arranged in the case main body 321a. The armature guide 322 is formed in a columnar shape and includes a large-diameter portion 322a fixed to the bottom portion of the housing main body 321a and a small-diameter portion 322b that is continuous with the large-diameter portion 322a and has a smaller diameter than that Large diameter section 322a.

The magnetic core 323 is arranged in the case main body 321a. The magnetic core 323 is formed in a cylindrical shape, and an outer peripheral portion thereof is in contact with an inner peripheral portion of the case main body 321a. Also, the large-diameter portion 322a of the armature guide 322 is attached to an end portion (an end portion on the bottom portion side of the case main body 321a) of the magnetic core 323 in the axial direction. An inner peripheral portion excluding an end portion of the magnetic core 323 faces an outer peripheral portion of the small-diameter portion 322b of the armature guide 322 at a predetermined distance. The other end of the magnetic core 323 in the axial direction faces the armature 324 .

The armature 324 and the armature sleeve 325 are integrally assembled movable portions 320 and are movably disposed in the case main body 321a. The armature 324 is formed in a cylinder, and an outer peripheral portion thereof is slidably engaged with an inner peripheral portion of the case main body 321a. One end of the armature 324 in the axial direction faces the other end of the magnetic core 323 .

The anchor sleeve 325 includes a fixed tubular portion 328 press-fitted and fixed to the inner peripheral portion of the armature 324, and an abutting portion 329 continuous with the fixed tubular portion. An inner peripheral portion of the fixed tubular portion 328 abuts with an outer peripheral portion of the small-diameter portion 322b of the armature guide 322 slidably engaged. One end of the fixed tubular portion 328 in the axial direction is located inside the armature 324 . The abutment portion 329 is continuous with the other end of the fixed tubular portion 328 in the axial direction and is formed in a disk shape having an outer diameter larger than the outer diameter of the fixed tubular portion 328 . The tubular hole of the fixed tubular portion 328 is formed in the abutting portion 329 .

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

The armature sleeve biasing spring 326 biases the movable portion 320 in a direction away from the magnetic core 323 . Therefore, when no magnetic attractive force acts between the armature 324 and the magnetic core 323, a clearance is generated between the armature 324 and the magnetic core 323. When a magnetic attraction force acts between the armature 324 and the magnetic core 323 , the movable portion 320 moves against the biasing force of the armature sleeve biasing spring 326 and the armature 324 comes into contact with the magnetic core 323 .

When the movable portion 320 moves in a direction away from the magnetic core 323, the later-described valve element 332 of the valve body unit 33 is pressed and the valve portion 339 of the valve element 332 is separated from the intake valve seat 331, which will be described later, and the electromagnetic intake valve 3 is opened. Hereinafter, a direction in which the movable portion 320 moves away from the magnetic core 323 is defined as a valve opening direction. That is, the armature sleeve biasing spring 326 biases the movable portion 320 in the valve opening direction.

(valve body unit)

The valve body assembly 33 includes an intake valve seat 331, a valve member 332, a spring retainer 333, and an intake valve biasing spring 334. The intake valve seat 331 is a specific example of a seat member according to the present invention. Spring retainer 333 is a specific example of a biasing member retainer according to the present invention, and intake valve biasing spring 334 is a specific example of a valve biasing member according to the present invention.

The intake valve seat 331 is formed in a cylindrical shape and includes a large-diameter seat portion 335 and a small-diameter seat portion 336 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-fitted and fixed to the inner peripheral side of the housing 321 (housing main body 321a) of the armature unit 32 .

The large-diameter seat portion 335 is formed with the inlet port 335a reaching the inner peripheral portion from the outer peripheral portion. The inlet port 335a communicates with the inlet port 10b (see Fig 2 ) in the low-pressure fuel chamber 10 described above. An end surface of the large-diameter seat portion 335 on the opposite side 336 to the small-diameter seat portion is a seat surface 332b on which a later-described valve portion 339 of the valve element 335 is seated. The seating surface 335b is formed in a plane perpendicular to an axial direction of the large-diameter seating portion 335 .

Also, an inner peripheral guide portion 337 is provided at an 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 portion 338 of the valve element 332 to be described later passes. The inner peripheral guide portion 337 holds the rod portion 338 of the valve element 332 in a slidable manner.

The valve element 332 includes a rod portion 338 formed in a columnar shape and a valve portion 339 connected to an end portion of the rod portion 338 in the axial direction. The rod portion 338 is disposed in the intake valve seat 331 and the valve portion 339 faces the seating surface 335b of the intake valve seat 331 . An intermediate portion of the rod portion 338 is held by the inner peripheral guide portion 337 of the intake valve seat 331 in a slidable manner. Also, the abutting portion 329 of the armature sleeve 325 is engaged with the other end portion of the rod portion 338 in the axial direction in the intake valve seat 331 .

The valve portion 339 is formed in a disc shape with a diameter larger than the diameter of the inner peripheral portion of the large-diameter seat portion 335, and has a valve portion seat surface 339a facing the seat surface 335b of the intake valve seat 331 and an abutting surface 339b facing a surface opposite to the valve portion seating surface 339a.

The valve portion seat surface 339a is formed in a plane perpendicular to the valve opening direction (valve closing direction), and abuts against the seat surface 335b of the intake valve seat 331 in the closed state of the electromagnetic intake valve 3 . That is, when the valve portion seat surface 339a abuts the seat surface 335b of the intake valve seat 331, the valve portion 339 sits on the seat surface 335b of the intake valve seat 331.

The abutting surface 339b of the valve portion 339 is formed in a tapered shape protruding toward the central portion. The abutment surface 339 b abuts on a later-described bottom portion 341 of the stopper 34 in the valve opening state of the intake electromagnetic valve 3 . In addition, the abutment surface 339b is provided with an engaging projection 339c for engaging with an engaging hole 341a of the stopper 34 to be described later.

The spring retainer 333 is formed in a cylindrical shape and has a flange on which one end of the intake valve biasing spring 334 abuts. The spring retainer 333 is press-fitted and fixed to an end portion of the rod portion 338 on the side opposite to the valve portion 339 . That is, the spring retainer 333 is mounted integrally with the valve element 332 and forms the movable portion 330.

A length from a center of the guide portion, which is a center of the inner peripheral guide portion 337, in a direction (direction parallel to the valve closing direction and the valve opening direction) in which the rod portion 338 extends to the other end portion of the rod portion 338 is shorter than the length from the center of the guide portion to the end portion of the valve portion 339 opposite to the rod portion 338 side (tip of an engaging projection 339c which will be described later). As a result, the length from the center of the guide portion, where the length can be adjusted without being affected by a size of the intake valve seat 331, to the other end portion of the rod portion 338 is shortened, and thus the movable portion 330 can be downsized (reduced). will. As a result, the responsiveness of the movable portion 330 can be improved.

In the intake valve preload spring 334, the intake valve preload spring 334 is arranged on an upstream side (opposite to the pressure chamber 11) of the inner peripheral guide portion 337 and is fitted between an inner peripheral portion of the small-diameter seat portion 336 in the intake valve seat 331 and an outer peripheral portion of the spring retainer 333. One end of the intake valve preload spring 334 abuts the flange of the spring retainer 333 and the other end of the intake valve preload spring 334 abuts the inner peripheral guide portion 337 of the intake valve seat 331 .

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

The preloading force of the intake valve preloading spring 334 is set smaller than the preloading force of the armature sleeve preloading spring 326. Therefore, when no magnetic attractive force acts between the armature 324 and the magnetic core 323 in the armature unit 32, the movable portion 320 and the movable portion 330 are by the Armature sleeve bias spring 326 biased in the valve opening direction.

As a result, the valve portion seat surface 339a of the valve portion 339 is separated from the seat surface 335b of the intake valve seat 331, and the intake electromagnetic valve 3 is opened.

(Attack)

The stop 34 is fixed to the body 1 (see 2 ). The stopper 34 is formed in a bottomed cylindrical shape with the valve element 332 side opened, and has a bottom portion 341 . An inner diameter of the stopper 34 is set larger than an outer diameter of the valve portion 339 . The bottom portion 341 of the stopper 34 limits the movement of the movable portion 330 (valve element 332) in the valve opening direction when the valve portion 339 comes into contact with the bottom portion.

An engaging hole 341 a and a plurality of fuel passage holes 341 b are formed in the bottom portion 341 of the stopper 34 . The engaging hole 341a is provided in the central portion of the bottom portion 341, and the plurality of fuel passage holes 341b are arranged at intervals applicable to the circumference of the engaging hole 341a. In the valve opening state of the intake electromagnetic valve 3 , the engaging projection 339c of the valve portion 339 is engaged with the engaging hole 341a of the stopper 34 , and the abutting surface 339b of the valve portion 339 abuts the bottom portion 341 of the stopper 34 . Therefore, a valve-opening stroke (a stroke from a valve-closed state to a valve-opened state) of the valve element 332 is defined by the stopper 34 .

[High Pressure Fuel Pump Operation]

Next, the operation of the high-pressure fuel pump according to the present embodiment will be explained with reference to FIG 2 , 6 and 7 described.

6 14 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 7 12 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 2 the fuel flows from the intake passage 1a into the pressure chamber 11 when the piston 2 is lowered and the electromagnetic intake valve 3 is opened. In the following, the downward stroke of the piston 2 is referred to as the intake stroke. On the other hand, when the piston 2 is raised and the electromagnetic inlet valve 3 is closed, the fuel in the pressure chamber 11 is pressurized, passes through the outlet valve 8 and is supplied under pressure to the common rail 106 (see Fig 1 ). The following is a process of raising the piston 2 is referred to as the upstroke.

As described above, when the intake electromagnetic valve 3 is closed during the upstroke, the fuel sucked into the pressure chamber 11 during the intake stroke is pressurized and discharged to the common rail 106 side. On the other hand, when the intake electromagnetic valve 3 is opened during the upstroke, the fuel in the pressurizing chamber 11 is pushed back toward the intake port 1a side and is not discharged to the common rail 106 . In this way, fuel delivery by the high-pressure fuel supply pump 100 is actuated by opening and closing the intake electromagnetic valve 3 . The opening or closing of the intake electromagnetic valve 3 is controlled by the ECU 101 .

In the intake stroke, the volume of the pressure chamber 11 increases and the fuel pressure in the pressure chamber 11 decreases. As a result, a fluid differential pressure (hereinafter referred to as “fluid differential pressure before and after the valve portion 339”) between the inlet port 335a and the pressure chamber 11 decreases. Then, when the biasing force of the armature-sleeve biasing spring 326 becomes greater than the differential fluid pressure before and after the valve portion 339, the movable portions 320 and 330 move in the valve opening direction and, as shown in FIG 6 1, the valve portion 339 is separated from the seating surface 335b of the intake valve seat 331, and the electromagnetic intake valve 3 is opened.

When the electromagnetic intake valve 3 is opened, the fuel in the intake port 335a flows between the valve portion 339 and the intake valve seat 331, passes through the plurality of fuel passage holes 341b of the stopper 34, and flows into the pressure chamber 11. In the valve-opening state of the electromagnetic intake valve 3, the valve portion 339 comes in contact with the stopper 34, and thus the position of the valve portion 339 in the valve opening direction is regulated. A gap existing between the valve portion 339 and the intake valve seat 331 in the valve-opening state of the electromagnetic intake valve 3 is a moving range of the valve portion 339, which is a valve-opening stroke.

After the intake stroke is complete, the process moves to the upstroke. At this time, the electromagnetic coil 312 remains in a non-energized state, and no magnetic attraction force acts between the armature 324 and the magnetic core 323 . Then, a biasing force acts in the valve opening direction corresponding to a difference in biasing forces between the armature sleeve biasing spring 326 and the intake valve biasing spring 334 and an urging force in the valve closing direction by a fluid force generated when the fuel flows from the pressure chamber 11 to the low-pressure fuel flow path 10a flows back, onto the valve element 332 (the movable portion 330).

In this state, in order to keep the intake electromagnetic valve 3 in the valve-opening state, the difference in preload force between the armature sleeve preload spring 326 and the intake valve preload spring 334 is set larger than the fluid force. The volume of the pressure chamber 11 decreases when the piston 2 is raised. Therefore, the fuel sucked into the pressure chamber 11 again passes between the valve portion 339 and the intake valve seat 331 and is returned to the intake port 335a, and thus the pressure in the pressure chamber 11 does not rise. This stroke is called the return stroke.

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

A clearance between the armature 324 and the magnetic core 323 is set larger than the valve opening lift between the valve portion 339 and the intake valve seat 331 . For example, when the clearance between the armature 324 and the magnetic core 323 is smaller than the valve opening stroke, the armature 324 abuts against the magnetic core 323 before the valve portion 339 comes into contact with the intake valve seat 331 . As a result, the valve portion 339 and the intake valve seat 331 do not come into contact, and the electromagnetic intake valve 3 cannot be brought into the valve-closed state.

If the clearance between the armature 324 and the magnetic core 323 is too large, sufficient magnetic attraction force cannot be obtained even when the electromagnetic coil 312 is excited, and thus the intake electromagnetic valve 3 cannot be brought into the valve-closed state. Even if that electromagnetic intake valve 3 can be brought into the valve-closed state, the responsiveness of the electromagnetic intake valve 3 deteriorates. Accordingly, the high-pressure fuel amount discharged cannot be controlled during the high-speed operation of the internal combustion engine (during the high-speed rotation of the cam). Therefore, the clearance between the armature 324 and the magnetic core 323 is appropriately adjusted depending on the number of turns of the electromagnetic coil 312, the amount of current flowing through the electromagnetic coil 312, and the like.

When the armature 324 (movable portion 320) moves in the valve-closing direction, the valve element 332 (the movable portion 330) is released from the biasing force in the valve-opening direction and moves by the biasing force of the intake valve biasing spring 334 and the fluid force flowing through the valve in the Inlet channel 10b flowing fuel is caused in the valve closing direction. like it in 7 1, when the valve portion seating surface 339a of the valve portion 339 comes into contact with the seating surface 335b of the intake valve seat 331 (the valve portion 339 is seated on the seating surface 335b), the intake electromagnetic valve 3 is closed.

After the inlet electromagnetic valve 3 is closed, the fuel in the pressure chamber 11 is pressurized as the piston 2 rises, and then when the pressure becomes greater than or equal to a predetermined pressure, the fuel flows through the outlet valve 8 and is sent to the common rail 106 (see 1 ) submitted. This stroke is called the exhaust stroke. That is, the upward stroke from a lower start point to an upper start point of the piston 2 includes the return stroke and the exhaust stroke. Then, by controlling a timing of energizing the electromagnetic coil 312 of the intake electromagnetic valve 3, the amount of high-pressure fuel discharged can be controlled.

In the upstroke, when the timing of energizing the electromagnetic coil 312 is earlier, a proportion of the return stroke is small and a proportion of the exhaust stroke is large. That is, the fuel returned to the intake port 10b decreases and the high pressure discharged fuel increases. When the timing of energizing the electromagnetic coil 312 is delayed, however, the proportion of the return stroke increases and the proportion of the exhaust stroke decreases in the up stroke. That is, the fuel returned to the intake passage 10b increases and the high-pressure discharged fuel decreases. According to the configuration described above, by controlling the timing of energizing the electromagnetic coil 312, the amount of high-pressure fuel discharged can be controlled to an amount required by the internal combustion engine.

2. Summary

As described above, the electromagnetic intake valve 3 (electromagnetic intake valve) according to the embodiment described above includes the valve element 332 (valve element), the intake valve seat 331 (seat element), and the intake valve biasing spring 334 (valve biasing element). The valve element 332 includes the rod portion 338 (rod portion) and the valve portion 339 (valve portion) connected to an end portion of the rod portion 338 . The intake valve seat 331 includes the inner peripheral guide portion 337 (guide portion) that guides the outer periphery of the rod portion 338 and the seat surface 339b (seat surface) on which the valve portion 335 is seated. The intake valve biasing spring 334 biases the rod portion 338 in the valve closing direction in which the valve portion 339 approaches the seat surface 335b. The intake valve biasing spring 334 is located closer to the valve closing direction side than the inner peripheral 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 shorter than the length from the center of the guide portion to the tip of the valve portion 339 (the tip of the engaging projection 339c).

As a result, in a state where the valve portion 339 is seated on the seating surface 335b of the intake valve seat 331, the valve portion 339 is disposed in the pressure chamber 11 and the intake valve biasing spring 334 is disposed on the upstream side (inlet port 335a side) of the valve portion 339. Therefore, it is not necessary to provide a space for arranging the intake valve preload spring 334 in the pressure chamber 11, and a dead volume in the pressure chamber 11 can be reduced. As a result, a volume of the pressure chamber 11 can be reduced, and the delivery efficiency of the high-pressure fuel supply pump 100 can be improved. Since the intake valve preload spring 334 is disposed on the upstream side (on the intake port 335a side) of the valve portion 339, the intake valve preload spring 334 is not covered with high fuel pressure fuel and the durability of the intake valve preload spring 334 can be improved.

The length from the center of the guide portion of the inner peripheral guide portion 337 to the other end portion of the rod portion 338 can be adjusted without being affected by 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 movable portion 330 can be downsized (reduced). As a result, the responsiveness of the valve element 332 (movable portion 330) can be improved.

The electromagnetic intake valve 3 (electromagnetic intake valve) according to the embodiment described above includes the spring holder 333 (preload member holder) attached to the other end portion of the rod portion 338 (rod portion) and the intake valve biasing spring (valve biasing member) 334 holds. As a result, the intake valve biasing spring 334 can be easily engaged with the rod portion 338 . In the embodiment described above, the length of the rod portion 338 is adjusted so that the other end portion of the rod portion 338 reaches the press-fit portion of the spring retainer 333 . As a result, the rod portion 338 can be shortened as much as possible, and the responsiveness of the valve element 332 (movable portion 330) can be improved.

In the electromagnetic intake valve 3 (electromagnetic intake valve) according to the embodiment described above, the valve element 332 (valve element), the intake valve seat 331 (seat element), the intake valve biasing spring 334 (valve biasing element), and the spring holder 333 (biasing element holder) are assembled as a valve body unit ( Valve body unit 33) assembled. As a result, the valve element 332 biased by the intake valve biasing spring 334 can be easily assembled to the body 1 of the high pressure fuel supply pump 100, and the assemblability of the electromagnetic intake valve 3 and the high pressure fuel supply pump 100 can be improved.

In addition, according to the above-described embodiment, the electromagnetic intake valve 3 (electromagnetic intake valve) is formed separately from the valve body unit 33 (valve body unit), and includes the stopper 34 (stopper) that restricts the movement of the valve element 332 in the valve opening direction by the contact of the valve portion 339 (valve portion ) is restricted when the valve element 332 (valve element) moves in the valve opening direction, which is the opposite direction to the valve closing direction. Thus, 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 maintain the valve opening of the intake electromagnetic valve 3 can be reduced. In addition, since the stopper 34 is formed separately from the valve body unit 33, the stopper 34 can be mounted on the body 1 alone.

For example, when the stopper 34 is formed integrally with the valve body unit 33 , it is necessary to press-fit and fix the stopper 34 to the outer periphery of the intake valve seat 331 . However, since the outer periphery of the intake valve seat 331 is press-fitted into the body 1, a portion where the stopper 34 is press-fitted into the intake valve seat 331 and a portion where the intake valve seat 331 is press-fitted into the body 1 are the same and double press-fitting he follows.

Then, when the stopper 34 is press-fitted into the intake valve seat 331, the outer peripheral portion of the stopper 34 is first deformed. Since the amount of deformation of the stopper 34 varies, the variation in press-fitting load increases when the intake valve seat 331 is press-fitted into the body 1. As a result, when the intake valve seat 331 is press-fitted into the body 1, the press-in load tends to be excessive, and the intake valve seat 331 cannot be assembled to the body 1.

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

In the electromagnetic intake valve 3 (electromagnetic intake valve) according to the embodiment described above, the other end portion of the rod portion 338 is formed separately from the rod portion 338 and is in contact with the movable portion 320 (movable portion) that drives the rod portion 338 . As described above, since the rod portion 338 and the movable portion 320 are formed separately, the rod portion 338 can be downsized, and the responsiveness of the valve element 332 (movable portion 330) can be improved:

In the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above In the embodiment described above, the movable portion 320 (movable portion) pushes the other end portion of the rod portion 338 in the valve opening direction, which is a direction opposite to the valve closing direction, in a state where no force is applied to move the movable portion 320 in the valve closing direction. As a result, in a state where no force is applied to move the movable portion 320 in the valve closing direction, a force against the biasing force of the intake valve biasing spring 334 can be applied to the rod portion 338 (valve element 332) and the valve opening state of the electromagnetic intake valve 3 can be easily maintained.

The electromagnetic intake valve 3 (electromagnetic intake valve) according to the embodiment described above includes the armature-sleeve biasing spring 326 (the movable portion biasing member) disposed on the valve closing direction side with respect to the movable portion 320 (movable portion) and the movable portion 320 in the valve opening direction, which is a direction opposite to the valve closing direction, and the magnetic core 323 (magnetic core) that attracts the movable portion 320 in the valve closing direction by the electromagnetic attractive force generated by energizing the electromagnetic coil 312 (coil). . Then, in the state where the electromagnetic coil 312 is not energized, the movable portion 320 is biased in the valve opening direction by the armature sleeve biasing spring 326 320 and moves the valve member 332 in the valve opening direction against the biasing force of the intake valve biasing spring 334 (the valve biasing member). As a result, only the movable portion 320 collides with the magnetic core 323 by the magnetic attraction force, and a mass of the valve element 332 is not added to the collision. Therefore, the mass that collides with the magnetic core 323 can be reduced, and noise generated by the collision can be reduced. When the electromagnetic coil 312 is not energized, the intake electromagnetic valve 3 can be opened.

In the electromagnetic intake valve 3 (electromagnetic intake valve) according to the embodiment described above, 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 loads the other end portion of the rod portion 338 ( rod portion) in the valve opening direction and the valve portion 339 of the valve element 332 comes into contact with the stopper 34 and thus the valve opening lift of the valve portion 339 is adjusted. As a result, the valve opening stroke can be adjusted simply by assembling the electromagnetic intake valve 3 with the components such as the valve body unit 33, the stopper 34, and the movable portion 320.

In the electromagnetic intake valve 3 (electromagnetic intake valve) according to the embodiment described above, the valve portion 339 (valve portion) has the valve portion seat surface 339a (valve portion seat surface) which is formed in a plane perpendicular to the valve closing direction and which abuts on the seat surface 335b (seat surface). and the seat surface 335b (seat surface) of the intake valve seat 331 (seat member) is formed in a plane perpendicular to the valve closing direction. As a result, it is possible to ensure the sealing ability when the valve portion seating surface 339a abuts against the seating surface 335b, and improve the workability of the valve portion seating surface 339a and the seating surface 335b. For example, in a case where the valve portion seating surface 339a and the seating surface 335b are tapered surfaces, it is necessary to increase the accuracy of the taper angle between the valve portion seating surface 339a and the seating surface 335b in order to improve the sealing ability and workability of the valve portion seating surface 339a and the seating surface 335b is degraded.

In the electromagnetic intake valve 3 (electromagnetic intake valve) according to the embodiment described above, the movable portion 320 (the movable portion) comes into contact with the other end portion of the rod portion 338 on the valve closing direction side of the inner peripheral guide portion 337 (guide portion) in the intake valve seat 331 (seat member). Contact. Since the other end portion of the rod portion 338 does not protrude to the outside of the intake valve seat 331, the rod portion 338 can be downsized and the responsiveness of the valve element 332 (movable portion 330) can be improved.

The embodiments of the electromagnetic intake valve and the high-pressure fuel supply pump of the present invention have been described above along with their operational effects. However, the electromagnetic intake valve and the 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 claims. For example, the embodiments in one are described individually to clearly explain the present invention, and are not necessarily limited to those having all configurations described.

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

However, in the configuration in which the spring retainer 333 is brought into contact with the inner peripheral guide portion 337, when the impact generated by opening the valve and closing the valve exceeds the pressing load of the spring retainer 333 while the intake electromagnetic valve is performing the opening and closing of the valve repeatedly, the press-in position of the spring retainer 333 shifted. As a result, the valve opening lift may change.

When the valve opening lift is larger than the predetermined amount, the time from the start of movement of the valve element 332 in the valve closing direction after energizing the electromagnetic coil 312 to the point at which the valve element comes into contact with the intake valve seat 331 becomes up to longer at the time when the valve element is fully closed than when the valve opening lift is the predetermined amount. Therefore, the responsiveness during the high-speed operation of the engine (during the high-speed rotation of the cam) is insufficient, the intake electromagnetic valve 3 cannot be closed at a target timing, and the amount of fuel discharged at high pressure cannot be controlled. Therefore, the valve opening lift is set to a value at which the amount of high-pressure fuel can be controlled even during high-speed cam rotation.

When the valve opening lift is smaller than the predetermined amount, the fluid force (force in the valve closing direction generated by the fuel flowing back from the pressure chamber 11 to the low-pressure fuel flow path 10a) generated in the valve portion 339 in the return operation of the high-pressure fuel supply pump 100 increases . In this case, the intake electromagnetic valve 3 is closed at an unexpected timing during the return process, and the amount of high-pressure fuel discharged cannot be controlled. Therefore, the valve opening lift is set to a value at which the intake electromagnetic valve 3 is not closed even when the cam rotates at high speed.

Reference List

1

body

2

Pistons

3

Electromagnetic inlet valve

4

relief valve mechanism

5

inlet connection

6

cylinder

8th

outlet valve

9

pressure pulsation reduction mechanism

10

low-pressure fuel chamber

10a

Low Pressure Fuel Flow Path

10b

inlet channel

11

pressure chamber

12

outlet connection

31

coil unit

32

anchor unit

33

valve body assembly

34

attack

100

high pressure fuel supply pump

101

ECU

102

feed pump

103

fuel tank

104

low pressure pipe

105

fuel pressure sensor

106

Common bar

107

injection device

311

base element

312

electromagnetic coil

313

connection element

315

bobbin

316

fitting hole

320

Movable section

321

housing

322

anchor guide

323

magnetic core

324

anchor

325

anchor sleeve

330

Movable section

331

intake valve seat section

332

valve element

333

pen holder

335a

inlet port

335b

seat

337

inner circumference guide section

338

bar section

339

valve section

339a

valve section seating surface

339b

contact surface

339c

engagement protrusion

341

bottom section

341a

engagement hole

341b

fuel port

QUOTES INCLUDED IN DESCRIPTION

This list of the documents cited by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent Literature Cited

• JP2013148025A [0003]

Claims (12)

Electromagnetic inlet valve, which includes: a valve element having a rod portion and a valve portion connected to an end portion of the rod portion; a seat member having a guide portion that guides an outer periphery of the rod portion and a seat surface on which the valve portion is seated; and a valve biasing member biasing the rod portion in a valve closing direction in which the valve portion approaches the seating surface, wherein the valve biasing member is disposed closer to the valve closing direction side than the guide portion, and a length from a center of the guide portion, which is a center in a direction parallel to the valve closing direction, to the other end portion of the rod portion is shorter than a length from the center of the guide portion to a tip of the valve portion. Electromagnetic inlet valve after claim 1 further comprising a biasing member holder attached to the other end portion of the rod portion and holding the valve biasing member. Electromagnetic inlet valve after claim 2 wherein the valve element, the seat element, the valve biasing element and the biasing element holder are assembled as a valve body unit. Electromagnetic inlet valve after claim 3 further comprising a stopper formed separately from the valve body unit to restrict movement of the valve element in a valve opening direction, which is a direction opposite to the valve closing direction, by contact of the valve portion when the valve element moves in the valve opening direction. Electromagnetic inlet valve after claim 1 further comprising a stopper that restricts movement of the valve element in a valve opening direction, which is a direction opposite to the valve closing direction, by contacting the valve portion when the valve element moves in the valve opening direction. Electromagnetic inlet valve after claim 1 wherein the other end portion of the rod portion is formed separately from the rod portion and is in contact with a movable portion that drives the rod portion. Electromagnetic inlet valve after claim 6 wherein the movable portion pushes the other end portion of the rod portion in a valve opening direction, which is a 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. Electromagnetic inlet valve after claim 6 further comprising: a movable-portion urging member that is disposed closer to the valve-closing direction side than the movable portion and biases the movable portion in a valve-opening direction that is a direction opposite to the valve-closing direction; and a magnetic core that attracts the movable portion in the valve-closing direction by an electromagnetic attraction force generated by energizing a coil, wherein the movable portion is biased in a state where the coil is not energized by the biasing member of the movable portion in the Valve opening direction is biased and moves the valve member against a biasing force of the valve biasing member in the valve opening direction. Electromagnetic inlet valve after claim 8 further comprising: a stopper that restricts movement of the valve element in a valve opening direction, which is a direction opposite to the valve closing direction, by contacting the valve portion when the valve element moves in the valve opening direction; and a biasing member holder attached to the other end portion of the rod portion and holding the valve biasing member, wherein the valve member, the seat member, the valve biasing member and the biasing member holder are assembled as a valve body unit, and in a state where 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 element comes into contact with the stopper to adjust a valve opening stroke of the valve portion. Electromagnetic inlet valve after claim 1 , wherein the valve portion has a valve portion seat surface which is formed in a plane perpendicular to the valve closing direction and abuts against the seat surface, and the seat surface of the seat member is formed in a plane perpendicular to the valve closing direction. Electromagnetic inlet valve after claim 6 , wherein the movable portion comes into contact with the other end portion of the rod portion on the valve closing direction side with respect to the guide portion in the seat member. High-pressure fuel supply pump, which includes: a body having a pressure chamber; a piston that is supported by the body in a reciprocating manner and increases or decreases a capacity of the pressure chamber by reciprocating motion; and an electromagnetic inlet valve that releases a fuel into the pressure chamber, wherein the electromagnetic inlet valve comprises: a valve element having a rod portion and a valve portion connected to an end portion of the rod portion; a seat member having a guide portion that guides an outer periphery of the rod portion and a seat surface on which the valve portion is seated; and a valve biasing member biasing the rod portion in a valve closing direction in which the valve portion approaches the seating surface, wherein the valve biasing member is disposed closer to the valve closing direction side than the guide portion, and a length from a center of the guide portion, which is a center in a direction parallel to the valve closing direction, to the other end portion of the rod portion is shorter than a length from the center of the guide portion to a tip of the valve portion.

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