Electromagnetic inlet valve and high-pressure fuel supply pump

Abstract

Electromagnetic inlet valve (3) comprising: a valve element (332) having a rod portion (338) and a valve portion (339) connected to an end portion of the rod portion (338); a seat member having a guide portion (337) guiding an outer periphery of the rod portion (338) and a seat surface (335b) on which the valve portion (339) sits; a valve biasing element (334) biasing the rod portion (338) in a valve closing direction in which the valve portion (339) approaches the seat surface (335b); and a stopper (34) which restricts the movement of the valve element (332) in a valve opening direction, which is a direction opposite to the valve closing direction, by contact of the valve portion (339) when the valve element (332) moves in the valve opening direction, wherein the valve preloading element (334) is arranged closer to the side of the valve closing direction than the guide portion (337), and a length from a center of the guide portion (337), which is a center in a direction parallel to the valve closing direction, to the other end portion of the rod portion (338) is shorter than a length from the center of the guide portion (337) to a tip of the valve portion (339), wherein the stopper (34) has an engagement hole (341a) into which an engagement projection (339c) of the valve portion (339) can engage.

Description

Technical area

[0001] The present invention relates to an electromagnetic intake valve and a high pressure fuel supply pump. State of the art

[0002] For example, a high-pressure fuel supply pump is described in PTL 1. The high-pressure fuel supply pump described in PTL 1 includes an electromagnetic intake valve. When the electromagnetic intake valve is in a de-energized state in which an electromagnetic coil is de-energized, a valve body is preloaded by a biasing force of a spring, and thus the electromagnetic intake valve is opened. Meanwhile, when the electromagnetic coil is energized, a magnetic attraction force is generated, and thus the valve body moves against the biasing force of the spring, and the electromagnetic intake valve is closed. As described above, the electromagnetic intake valve performs an opening / closing motion depending on whether the electromagnetic coil is energized and controls a supply amount of high-pressure fuel.

[0003] PTL 2 discloses an electronic control unit including a drive control unit for controlling a pressure control valve of a high pressure fuel pump.

[0004] PTL 3 discloses a high pressure fuel supply pump including a seal having a low probability of leakage. Citation listPatent document(s) PTL 1: JP 2013-148025 A PTL 2: DE 10 2018 220 138 A1 PTL 3: JP 2013 - 194 616 A Summary of the inventionTechnical problem

[0005] However, in the electromagnetic intake valve of the high-pressure fuel supply pump described in PTL 1, the spring that preloads the valve body is disposed in a pressure chamber. Therefore, a dead volume in the pressure chamber increases, and the volumetric efficiency of the high-pressure fuel supply pump deteriorates.

[0006] 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

[0007] To solve the above problems and the object of the present invention, a high-pressure fuel supply pump of the present invention comprises a valve element, a seat element, and a preload element. The valve element includes a rod portion and a valve portion provided at an end portion of the rod portion. The seat element 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 preload element preloads the rod portion in a direction in which the valve portion is seated on the seat portion.A stopper is provided that restricts the movement of the valve element in a valve-opening direction, which is a direction opposite to the valve-closing direction, by contact with the valve portion when the valve element moves in the valve-opening direction. The stopper has an engagement hole into which an engagement projection of the valve portion can engage. 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

[0008] 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. Brief description of the drawings [ Fig. 1] Fig. 1 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. [ Fig. 2] Fig. 2 is a longitudinal sectional view (part 1) of the high-pressure fuel supply pump according to the embodiment of the present invention. [ Fig. 3] Fig. 3 is a longitudinal sectional view (part 2) of the high-pressure fuel supply pump according to the embodiment of the present invention. [ Fig. 4] Fig. 4 is a horizontal cross-sectional view of the high-pressure fuel supply pump according to the embodiment of the present invention when viewed from above. [ Fig. 5] Fig. 5 is an exploded cross-sectional view of the electromagnetic intake valve in the high-pressure fuel supply pump according to the embodiment of the present invention. [ Fig. 6] Fig. 6 is an enlarged cross-sectional view of an 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 opened. [ Fig. 7] Fig. 7 is an enlarged cross-sectional view of an 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. Description of embodiments1. Embodiment

[0009] 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 numerals. [Fuel supply system]

[0010] 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.

[0011] Fig. 1 is an overall configuration diagram of the fuel supply system using the high-pressure fuel supply pump according to the present embodiment.

[0012] As it is in Fig. 1, 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.

[0013] 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 through a low-pressure pipe 104 to a low-pressure fuel inlet port 51 of the high-pressure fuel supply pump 100.

[0014] 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. A plurality of injectors 107 and a fuel pressure sensor 105 are mounted on the common rail 106. The plurality of injectors 107 are mounted according to the number of cylinders (combustion chambers) and inject 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.

[0015] 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.

[0016] Furthermore, the ECU 101 controls the 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.

[0017] 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 Fig. 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 intake valve 3 via the pressure pulsation reducing mechanism 9 and an intake passage 10b.

[0018] 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 slidably held in the pressure chamber 11. The piston 2 reciprocates when force from a cam 91 (see Fig. 2) is transmitted to the engine.

[0019] In the pressure chamber 11, fuel is sucked from the electromagnetic intake valve 3 during a downward stroke of the piston 2, and the fuel is pressurized during an upward stroke. When the fuel pressure in the pressure chamber 11 exceeds a predetermined value, the exhaust valve 8 is opened, and 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 electromagnetic intake valve 3. The opening or closing of the electromagnetic intake valve 3 is controlled by the ECU 101. [High-pressure fuel supply pump]

[0020] Next, a configuration of the high-pressure fuel supply pump 100 will be described with reference to Fig. 2 to 4.

[0021] Fig. 2 is a longitudinal cross-sectional view (part 1) of the high-pressure fuel supply pump 100 when viewed in a cross section perpendicular to a horizontal direction and Fig. 3 is a longitudinal cross-sectional view (part 2) of the high-pressure fuel supply pump 100 when viewed in a cross section perpendicular to the horizontal direction. Fig. 4 is a horizontal cross-sectional view of the high-pressure fuel supply pump 100 when viewed in a cross section perpendicular to the vertical direction.

[0022] As it is in Fig. As shown in FIGS. 2 to 4, the body 1 of the high-pressure fuel supply pump 100 includes the above-described intake passage 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 (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.

[0023] As it is in Fig. As shown in Fig. 2, an O-ring 93, which is a specific example of a seat member, is disposed between the fuel pump mounting portion 90 and the body 1. The O-ring 93 prevents engine oil from leaking out of the engine (internal combustion engine) between the fuel pump mounting portion 90 and the body 1.

[0024] A cylinder 6, which guides the reciprocating movement of the piston 2, is fixed to the body 1 of the high-pressure fuel supply pump 100. A cylinder 6 is tubular and press-fitted into the body 1 on an outer peripheral side thereof. The body 1 and the cylinder 6 form the pressure chamber 11 together with the electromagnetic intake valve 3, the piston 2, and the exhaust valve 8 (see Fig. 4).

[0025] The body 1 is provided with a fixing portion 1c that engages 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 Fig. 2 upwards), so that the fuel pressurized in the pressure chamber 11 does not escape between an upper end surface of the cylinder 6 and the body 1.

[0026] A lower end of the piston 2 is provided with a tappet 92, which converts the rotational movement of a cam 91 attached to a camshaft of the engine into a vertical movement and transmits the vertical movement to the piston 2. The piston 2 is biased toward the cam 91 by a spring 16 via a retainer 15 and is squeezed against the tappet 92. The tappet 92 reciprocates according to the rotation of the cam 91. The piston 2 reciprocates together with the tappet 92 to change a volume of the pressure chamber 11.

[0027] 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. Furthermore, the seal holder 17 holds a piston seal 18 at the lower end portion on the holder 15 side.

[0028] The piston seal 18 slidably contacts an outer periphery of the piston 2 and seals the fuel in the auxiliary chamber 17a when the piston 2 reciprocates, preventing the fuel in the auxiliary chamber 17a from flowing 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.

[0029] In Fig. 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.

[0030] 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 located in the auxiliary chamber 17a. Therefore, the volume of the auxiliary chamber 17a increases or decreases due to the reciprocating movement of the piston 2.

[0031] The auxiliary chamber 17a is connected to the low-pressure fuel chamber 10 through a fuel channel 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 generated in the high-pressure fuel supply pump 100 can be reduced.

[0032] The body 1 is provided with a relief valve mechanism 4 that communicates with the pressure chamber 11. The relief valve mechanism 4 is a valve designed to act and return the fuel in the outlet 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 reaches a high pressure that exceeds a predetermined pressure.

[0033] The relief valve mechanism 4 includes a relief spring 41, a relief valve holder 42, a relief valve 43, and a seat member 44. One end portion of the relief spring 41 abuts the body 1, and the other end portion abuts the relief valve holder 42. The relief valve holder 42 engages the relief valve 43, and the preload force of the relief spring 41 acts on the relief valve 43 via the relief valve holder 42.

[0034] The relief valve 43 is pressed by the biasing force of the relief spring 41, closing the fuel passage of the seat member 44. The fuel passage of the seat member 44 communicates with the exhaust 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 (tight contact) of the relief valve 43 with the seat member 44.

[0035] When the pressure in the common rail 106 or an element upstream of the common rail increases, the fuel on the seat member 44 side presses on 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.

[0036] 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, the inlet passage 10b, or the like).

[0037] As it is in Fig. As shown in Figure 3, 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 into the interior of the high-pressure fuel supply pump 100.

[0038] The inlet connection 5 includes the low-pressure fuel inlet port 51 connected to the low-pressure pipe 104, and an inlet flow path 52 connected to the low-pressure fuel inlet port 51. The fuel that has passed through the inlet flow path 52 reaches an inlet port 335a (see Fig. 2) of the electromagnetic intake valve 3 via the pressure pulsation reducing mechanism 9 and the intake port 10b (see Fig. 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.

[0039] The low-pressure fuel chamber 10 is provided with a low-pressure fuel flow path 10a and an inlet channel 10b. The inlet channel 10b is connected to the inlet port 335a (see Fig. 2) of the electromagnetic intake valve 3, and the fuel that has passed through the low-pressure fuel flow path 10a reaches the inlet port 335a of the electromagnetic intake valve 3 via the intake passage 10b.

[0040] 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 is returned to the intake port 10b through the electromagnetic intake valve 3 in the valve opening state (see Fig. 2), pressure pulsation occurs in the low-pressure fuel chamber 10. The pressure pulsation reducing mechanism 9 reduces the propagation of the pressure pulsation generated in the high-pressure fuel supply pump 100 into the low-pressure pipe 104.

[0041] The pressure pulsation reduction mechanism 9 consists of a metal diaphragm damper in which two corrugated disc-shaped metal plates are bonded together 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 reduction mechanism 9 expands and contracts to absorb or reduce pressure pulsations.

[0042] The outlet valve 8 is connected to the outlet side of the pressure chamber 11. As shown in Fig. 4, 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 exhaust valve seat 81 side, and an exhaust valve stopper 84 determining a stroke (a moving distance) of the valve body 82.

[0043] The outlet valve 8 includes a plug 85 that blocks fuel from escaping to the outside. The outlet valve stop 84 is press-fitted into the plug 85. The plug 85 is connected to the pump body 1 by welding at a welded portion 86. The outlet valve 8 communicates with an outlet valve chamber 87, which is opened and closed by the valve portion 82. The outlet valve chamber 87 is formed in the body 1 and communicates with the fuel outlet port 12b via a side hole formed in the body 1 and extending in the horizontal direction.

[0044] An exhaust joint 12 is inserted into the side hole formed in the body 1. The exhaust joint 12 includes the exhaust passage 12a, which communicates with the side hole, and the fuel outlet port 12b, which is one end of the exhaust passage 12a. The fuel outlet port 12b of the exhaust joint 12 communicates with the common rail 106. The exhaust joint 12 is fixed to the body 1 by welding through a welded portion 12c.

[0045] In a state where there is no difference in fuel pressure (fuel differential pressure) between the pressure chamber 11 and the exhaust valve chamber 87, the valve portion 82 is pressed against the exhaust valve seat 81 by the biasing force of the exhaust valve spring 83, and thus the exhaust valve 8 is in a closed state. When the fuel pressure in the pressure chamber 11 becomes greater than the fuel pressure in the exhaust valve chamber 87, the valve portion 82 moves against the biasing force of the exhaust valve spring 83, and thus the exhaust valve 8 is opened.

[0046] 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 supplied via the fuel outlet port 12b of the outlet connection 12 to the common rail 106 (see Fig. 1). In the above configuration, the outlet valve 8 functions as a check valve that restricts a flow direction of the fuel. [Electromagnetic intake valve]

[0047] Next, a configuration of the electromagnetic intake valve 3 will be described with reference to Fig. 2 and Fig. 5 described.

[0048] Fig. 5 is an exploded cross-sectional view of the electromagnetic inlet valve of the high-pressure fuel supply pump 100.

[0049] As it is in Fig. 2, the electromagnetic intake valve 3 comprises a coil unit 31, an armature unit 32, a valve body unit 33 and a stopper 34. (coil unit)

[0050] 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.

[0051] The base member 311 is formed of a resin material or the like, and a coil body 315 is joined thereto. The coil body 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 coil body 315 and is arranged to make one circuit around the armature unit 32 fitted into the fitting hole 316.

[0052] One portion of the terminal element 313 is embedded in the base element 311 and electrically connected to the electromagnetic coil 312. Meanwhile, the other portion of the terminal element 313 is exposed to the outside to enable connection between the terminal element 313 and the outside (power supply). That is, a current flows through the electromagnetic coil 312 via the terminal element 313. (Anchor unit)

[0053] As it is in Fig. 5, 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 preload spring 326. The armature sleeve preload spring 326 represents a specific example of a preload member for the movable portion according to the present invention.

[0054] The housing 321 includes a housing main body 321a formed in a cylindrical shape with a bottom, and a connecting projection 321b provided on an outer peripheral portion on an opening side of the housing main body 321a. The connecting projection 321b is continuous in the circumferential direction of the housing main body 321a and fitted into a fitting hole provided in the body 1 (see Fig. 2). In addition, the coil unit 31 abuts against an end surface of the connecting projection 321b facing a bottom portion side of the housing main body 321a.

[0055] The armature guide 322 is arranged in the housing main body 321a. The armature guide 322 is columnar and includes a large-diameter portion 322a fixed to the bottom portion of the housing main 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.

[0056] The magnetic core 323 is arranged in the housing main body 321a. The magnetic core 323 is formed in a cylindrical shape, and an outer peripheral portion thereof contacts an inner peripheral portion of the housing main body 321a. Furthermore, the large-diameter portion 322a of the armature guide 322 is attached to one end portion (an end portion on the bottom portion side of the housing main body 321a) of the magnetic core 323 in the axial direction. An inner peripheral portion, except for one 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.

[0057] The armature 324 and the armature sleeve 325 are integrally assembled movable portions 320 and are movably disposed in the housing 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 housing main body 321a. One end of the armature 324 in the axial direction faces the other end of the magnetic core 323.

[0058] The armature sleeve 325 includes a fixed tubular portion 328 press-fitted and fixed to the inner peripheral portion of the armature 324, and an abutment portion 329 continuous with the fixed tubular portion. An inner peripheral portion of the fixed tubular portion 328 is slidably engaged with an outer peripheral portion of the small-diameter portion 322b of the armature guide 322. One end of the fixed tubular portion 328 in the axial direction is disposed 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 disc shape with 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 abutment portion 329.

[0059] The armature sleeve preload spring 326 is fitted between the outer peripheral portion of the small-diameter portion 322b of the armature guide 322 and the inner peripheral portion of the magnetic core 323. One end of the armature sleeve preload spring 326 abuts the large-diameter portion 322a of the armature guide 322, and the other end of the armature sleeve preload spring 326 abuts the fixed tubular portion 328 of the armature sleeve 325.

[0060] The armature sleeve preload spring 326 preloads the movable portion 320 in a direction away from the magnetic core 323. Therefore, when no magnetic attraction force acts between the armature 324 and the magnetic core 323, a clearance is created 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 preload spring 326, and the armature 324 comes into contact with the magnetic core 323.

[0061] When the movable portion 320 moves in a direction away from the magnetic core 323, the valve element 332 of the valve body unit 33 (described later) is pushed, and the valve portion 339 of the valve element 332 is separated from the intake valve seat 331 (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 bias spring 326 biases the movable portion 320 in the valve-opening direction. (valve body unit)

[0062] The valve body unit 33 includes an intake valve seat 331, a valve element 332, a spring retainer 333, and an intake valve preload spring 334. The intake valve seat 331 is a specific example of a seat element according to the present invention. The spring retainer 333 is a specific example of a preload element retainer according to the present invention, and the intake valve preload spring 334 is a specific example of a valve preload element according to the present invention.

[0063] 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.

[0064] The large-diameter seat portion 335 is formed with the inlet port 335a, which reaches the inner peripheral portion from the outer peripheral portion. The inlet port 335a communicates with the inlet passage 10b (see Fig. 2) in the above-described low-pressure fuel chamber 10. An end surface of the large-diameter seat portion 335 on the opposite side to the small-diameter seat portion 336 is a seat surface 332b on which a valve portion 339, described later, of the valve element 335 is seated. The seat surface 335b is formed on a plane perpendicular to an axial direction of the large-diameter seat portion 335.

[0065] Furthermore, an inner peripheral guide portion 337 is provided on an inner peripheral portion of the large-diameter seat portion 335. The inner peripheral guide portion 337 is formed in a plate shape with 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, to be described later, of the valve element 332 passes. The inner peripheral guide portion 337 slidably supports the rod portion 338 of the valve element 332.

[0066] The valve element 332 includes a rod portion 338 formed in a columnar shape and a valve portion 339 connected to one 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 seat surface 335b of the intake valve seat 331. An intermediate portion of the rod portion 338 is slidably supported by the inner peripheral guide portion 337 of the intake valve seat 331. Furthermore, the abutment portion 329 of the armature sleeve 325 engages the other end portion of the rod portion 338 in the axial direction in the intake valve seat 331.

[0067] The valve portion 339 is formed in a disk 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 abutment surface 339b which is a surface opposite to the valve portion seat surface 339a.

[0068] The valve portion seat surface 339a is formed in a plane perpendicular to the valve opening direction (valve closing direction) and abuts 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.

[0069] The abutment surface 339b of the valve portion 339 is formed in a tapered shape protruding toward the central portion. The abutment surface 339b abuts against a bottom portion 341 of the stopper 34 (described later) in the valve-opening state of the electromagnetic intake valve 3. Furthermore, the abutment surface 339b is provided with an engagement projection 339c for engaging with an engagement hole 341a of the stopper 34 (described later).

[0070] The spring retainer 333 is formed in a cylindrical shape and has a flange against which one end of the intake valve preload 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 the valve portion 339. That is, the spring retainer 333 is integrally mounted with the valve element 332 and forms the movable portion 330.

[0071] 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 the side of the rod portion 338 (tip of an engaging projection 339c, which will be described later). As a result, the length from the center of the guide portion, at which 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). As a result, the responsiveness of the movable portion 330 can be improved.

[0072] In the intake valve preload spring 334, the intake valve preload spring 334 is disposed on an upstream side (opposite 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.

[0073] The intake valve preload spring 334 preloads the valve element 332 in a direction in which the valve portion 339 approaches the seat surface 335b of the intake valve seat 331. Hereinafter, a direction in which the valve portion 339 approaches the seat surface 335b of the intake valve seat 331 is defined as the valve closing direction. That is, the intake valve preload spring 334 preloads the valve element 332 (the movable portion 330) in the valve closing direction.

[0074] The preload force of the intake valve preload spring 334 is set smaller than the preload force of the armature sleeve preload spring 326. Therefore, when no magnetic attraction 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 preloaded in the valve opening direction by the armature sleeve preload spring 326.

[0075] 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 electromagnetic intake valve 3 is opened. (Stop)

[0076] The stop 34 is fixed to the body 1 (see Fig. 2). The stopper 34 is formed in a bottomed cylindrical shape with the valve element 332 open side 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.

[0077] An engagement hole 341a and a plurality of fuel passage holes 341b are formed in the bottom portion 341 of the stopper 34. 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 at intervals applicable to the circumference of the engagement hole 341a. In the valve-opening state of the electromagnetic intake valve 3, the engagement projection 339c of the valve portion 339 engages with the engagement hole 341a of the stopper 34, and the abutment surface 339b of the valve portion 339 abuts against the bottom portion 341 of the stopper 34. Therefore, a valve-opening stroke (a stroke from a valve-closing state to a valve-opening state) of the valve element 332 is defined by the stopper 34. [Operation of the high-pressure fuel pump]

[0078] Next, the operation of the high pressure fuel pump according to the present embodiment will be described with reference to Fig. 2, Fig. 6 and Fig. 7 described.

[0079] Fig. 6 is a cross-sectional view illustrating 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 illustrating a state in which the electromagnetic intake valve 3 in the high-pressure fuel supply pump 100 is closed.

[0080] In Fig. 2, the fuel flows from the intake port 1a into the pressure chamber 11 when the piston 2 is lowered and the electromagnetic intake valve 3 is opened. Hereinafter, the downward stroke of the piston 2 is referred to as the intake stroke. However, when the piston 2 is raised and the electromagnetic intake valve 3 is closed, the fuel in the pressure chamber 11 is pressurized, passes through the exhaust valve 8, and is supplied to the common rail 106 under pressure (see Fig. 1). In the following, the process of raising the piston 2 is referred to as the upward stroke.

[0081] As described above, when the electromagnetic intake 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 electromagnetic intake valve 3 is opened during the upstroke, the fuel in the pressure chamber 11 is pushed back toward the intake port 1a side and is not discharged to the common rail 106. In this way, the fuel discharge by the high-pressure fuel supply pump 100 is actuated by opening and closing the electromagnetic intake valve 3. The opening or closing of the electromagnetic intake valve 3 is controlled by the ECU 101.

[0082] 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 pressure differential (hereinafter referred to as "fluid pressure differential before and after the valve portion 339") between the intake port 335a and the pressure chamber 11 decreases. Then, when the biasing force of the armature sleeve biasing spring 326 becomes greater than the fluid pressure differential 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, the valve portion 339 is separated from the seat surface 335b of the intake valve seat 331 and the electromagnetic intake valve 3 is opened.

[0083] 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 into 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 movement range of the valve portion 339, which is a valve-opening stroke.

[0084] After the intake stroke is completed, the process proceeds to the upstroke. At this time, the electromagnetic coil 312 remains in a de-energized state, and no magnetic attraction force acts between the armature 324 and the magnetic core 323. Then, a bias force in the valve opening direction corresponding to a difference in bias forces between the armature sleeve bias spring 326 and the intake valve bias spring 334 and a pressure force in the valve closing direction by a fluid force generated when the fuel flows back from the pressure chamber 11 to the low-pressure fuel flow path 10a act on the valve element 332 (the movable portion 330).

[0085] In this state, to maintain the electromagnetic intake 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 to be greater than the fluid force. The volume of the pressure chamber 11 decreases as the piston 2 is lifted. Therefore, the fuel sucked into the pressure chamber 11 passes again between the valve portion 339 and the intake valve seat 331 and is returned to the intake port 335a, thus preventing the pressure in the pressure chamber 11 from rising. This stroke is called the return stroke.

[0086] In the reversing process, when a control signal from the ECU 101 (see Fig. 1) is applied to the electromagnetic intake valve 3, a current flows through the electromagnetic coil 312 via the terminal element 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 to 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 of the armature sleeve biasing spring 326.

[0087] A clearance between the armature 324 and the magnetic core 323 is set larger than the valve opening stroke between the valve portion 339 and the intake valve seat 331. For example, if the clearance between the armature 324 and the magnetic core 323 is smaller than the valve opening stroke, the armature 324 abuts 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-closing state.

[0088] If the clearance between the armature 324 and the magnetic core 323 is too large, even if the electromagnetic coil 312 is energized, sufficient magnetic attraction cannot be obtained, and thus the electromagnetic intake valve 3 cannot be brought into the valve-closing state. Even if the electromagnetic intake valve 3 can be brought into the valve-closing state, the responsiveness of the electromagnetic intake valve 3 deteriorates. Accordingly, the amount of fuel discharged at high pressure cannot be controlled during high-speed operation of the internal combustion engine (during 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.

[0089] 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 in the valve closing direction by the biasing force of the intake valve biasing spring 334 and the fluid force caused by the fuel flowing into the intake passage 10b. As shown in Fig. 7, when the valve portion seat surface 339a of the valve portion 339 comes into contact with the seat surface 335b of the intake valve seat 331 (the valve portion 339 sits on the seat surface 335b), the electromagnetic intake valve 3 is closed.

[0090] After the electromagnetic inlet valve 3 is closed, the fuel in the pressure chamber 11 is pressurized when the piston 2 is lifted, and then, when the pressure becomes greater than or equal to a predetermined pressure, the fuel flows through the outlet valve 8 and is supplied to the common rail 106 (see Fig. 1). This stroke is called the exhaust stroke. That is, the upward stroke from a lower starting point to an upper starting point of the piston 2 includes the return stroke and the exhaust stroke. Then, by controlling the energization timing of the electromagnetic coil 312 of the electromagnetic intake valve 3, the discharged amount of high-pressure fuel can be controlled.

[0091] When the energization timing of the electromagnetic coil 312 is earlier, a proportion of the return stroke is small and a proportion of the exhaust stroke is large in the upstroke. That is, the fuel returned to the intake port 10b decreases, and the fuel discharged at high pressure increases. Meanwhile, when the energization timing of the electromagnetic coil 312 is delayed, the proportion of the return stroke increases and the proportion of the exhaust stroke decreases in the upstroke. That is, the fuel returned to the intake port 10b increases, and the fuel discharged at high pressure decreases. According to the configuration described above, by controlling the energization timing of the electromagnetic coil 312, the amount of fuel discharged at high pressure can be controlled to an amount required by the internal combustion engine. 2. Summary

[0092] As described above, the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment includes the valve element 332 (valve element), the intake valve seat 331 (seat element), and the intake valve preload spring 334 (valve preload element). The valve element 332 includes the rod portion 338 (rod portion) and the valve portion 339 (valve portion) connected to one 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 preload spring 334 preloads the rod portion 338 in the valve closing direction in which the valve portion 339 approaches the seat surface 335b.The intake valve bias spring 334 is arranged 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).

[0093] 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 preload spring 334 is disposed on the upstream side (intake port 335a side) of the valve portion 339. Therefore, it is not necessary to provide a space for disposing 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 arranged 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 fuel having high fuel pressure, and the durability of the intake valve preload spring 334 can be improved.

[0094] 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.

[0095] The electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment includes the spring retainer 333 (preloading element retainer) attached to the other end portion of the rod portion 338 (rod portion) and holding the intake valve preloading spring (valve preloading element) 334. As a result, the intake valve preloading spring 334 can be easily engaged with the rod portion 338. In the above-described embodiment, 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.

[0096] In the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment, the valve element 332 (valve element), the intake valve seat 331 (seat element), the intake valve preload spring 334 (valve preload element), and the spring retainer 333 (preload element retainer) are assembled as a valve body unit (valve body unit 33). As a result, the valve element 332 preloaded by the intake valve preload spring 334 can be easily mounted on 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.

[0097] Furthermore, the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment 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 through the contact of the valve portion 339 (valve portion) when the valve element 332 (valve element) moves in the valve-opening direction, which is the direction opposite to the valve-closing direction. Thus, the valve-opening stroke can be defined. In addition, the fluid force exerted on the valve portion 339 during the above-described return stroke can be reduced, and the force required to maintain the valve opening of the electromagnetic intake valve 3 can be reduced. Furthermore, since the stopper 34 is formed separately from the valve body unit 33, the stopper 34 can be mounted solely on the body 1.

[0098] 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 equal and double press-fitted.

[0099] Then, when the stopper 34 is press-fitted into the intake valve seat 331, the outer peripheral portion of the stopper 34 is deformed first. Since the deformation amount of the stopper 34 varies, the variation in the press-fit load increases when the intake valve seat 331 is press-fitted into the body 1. As a result, the press-fit load tends to be excessive when the intake valve seat 331 is press-fitted into the body 1, and the intake valve seat 331 cannot be mounted on the body 1.

[0100] Meanwhile, in the electromagnetic intake valve 3 according to the above-described embodiment, double press-fitting can be avoided. 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 it is possible to prevent the press-fitting load from becoming excessive.

[0101] In the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment, 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.

[0102] In the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment, the movable portion 320 (movable portion) urges 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 can be applied to the rod portion 338 (the valve element 332) against the biasing force of the intake-valve biasing spring 334, and the valve-opening state of the electromagnetic intake valve 3 can be easily maintained.

[0103] The electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment includes the armature sleeve biasing spring 326 (the movable portion biasing member) that is disposed on the valve closing direction side with respect to the movable portion 320 (movable portion) and biases 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 320 in the valve opening direction by the armature sleeve bias spring 326 and moves the valve element 332 in the valve opening direction against the biasing force of the. Intake valve preload spring 334 (of the valve preload element). 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 element 332 is not added to the collision. Therefore, the mass colliding with the magnetic core 323 can be reduced, and the noise generated by the collision can be reduced. When the electromagnetic coil 312 is not energized, the electromagnetic intake valve 3 can be opened.

[0104] In the electromagnetic intake valve 3 (electromagnetic intake 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 urges 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, thus adjusting the valve-opening stroke of the valve portion 339. 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.

[0105] In the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment, the valve portion 339 (valve portion) has the valve portion seat surface 339a (valve portion seat surface) formed on a plane perpendicular to the valve closing direction and abutting against the seat surface 335b (seat surface), and the seat surface 335b (seat surface) of the intake valve seat 331 (seat member) is formed on a plane perpendicular to the valve closing direction. As a result, it is possible to ensure the sealing performance when the valve portion seat surface 339a abuts against the seat surface 335b and to improve the processability of the valve portion seat surface 339a and the seat surface 335b.For example, in a case where the valve portion seat surface 339a and the seat surface 335b are tapered surfaces, it is necessary to increase the accuracy of the taper angle between the valve portion seat surface 339a and the seat surface 335b, so that the sealing performance and the workability of the valve portion seat surface 339a and the seat surface 335b are deteriorated.

[0106] In the electromagnetic intake valve 3 (electromagnetic intake valve) according to the above-described embodiment, 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). 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 (the movable portion 330) can be improved.

[0107] 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 the claims. For example, the embodiments are described in detail to clearly explain the present invention and are not necessarily limited to those having all of the described configurations.

[0108] For example, in the above-described embodiment, the valve opening stroke of the valve portion 339 is adjusted by bringing the valve portion 339 of the valve element 332 into contact with the stopper 34. However, in the electromagnetic intake valve according to the present invention, the spring retainer 333 may be brought into contact with the inner peripheral guide portion 337, and at this time, a predetermined valve opening stroke can be set.

[0109] However, in the configuration where the spring retainer 333 is brought into contact with the inner peripheral guide portion 337, when the impact generated by the valve opening and closing exceeds the press-in load of the spring retainer 333 while the electromagnetic intake valve repeats the valve opening and closing, the press-in position of the spring retainer 333 is shifted. As a result, the valve opening stroke may change.

[0110] 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 the electromagnetic coil 312 is energized to the time the valve element comes into contact with the intake valve seat 331 to the time the valve element is fully closed becomes longer than when the valve opening lift is the predetermined amount. Therefore, the responsiveness during high-speed operation of the internal combustion engine (during high-speed rotation of the cam) is insufficient, the electromagnetic intake valve 3 cannot be closed at a target timing, and the amount of high-pressure fuel discharged 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.

[0111] When the valve opening lift is smaller than the predetermined amount, the fluid force (valve-closing force generated by the fuel flowing from the pressure chamber 11 back to the low-pressure fuel flow path 10a) generated in the valve portion 339 during the return process of the high-pressure fuel supply pump 100 increases. In this case, the electromagnetic intake valve 3 is closed at an unexpected timing during the return process, and the amount of fuel discharged under high pressure cannot be controlled. Therefore, the valve opening lift is set to a value at which the electromagnetic intake valve 3 is not closed even when the cam rotates at high speed. List of reference symbols 1 body 2 pistons 3 Electromagnetic inlet valve 4 Relief valve mechanism 5 Inlet connection 6 cylinders 8 exhaust 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 unit 34 stop 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 connecting element 315 coil body 316 Pass hole 320 Movable section 321 housing 322 anchor guide 323 magnetic core 324 anchors 325 anchor sleeve 330 Movable section 331 Inlet valve seat section 332 valve element 333 pen holders 335a Inlet connection 335b Seat 337 inner circumferential guide section 338 rod section 339 Valve section 339a Valve section seat surface 339b contact surface 339c engagement projection 341 floor section 341a Intervention hole 341b Fuel passage opening

Claims

[1] Electromagnetic inlet valve (3) comprising: a valve element (332) having a rod portion (338) and a valve portion (339) connected to an end portion of the rod portion (338); a seat member having a guide portion (337) guiding an outer periphery of the rod portion (338) and a seat surface (335b) on which the valve portion (339) sits; a valve biasing element (334) biasing the rod portion (338) in a valve closing direction in which the valve portion (339) approaches the seat surface (335b); and a stopper (34) which restricts the movement of the valve element (332) in a valve opening direction, which is a direction opposite to the valve closing direction, by contact of the valve portion (339) when the valve element (332) moves in the valve opening direction, wherein the valve preloading element (334) is arranged closer to the side of the valve closing direction than the guide portion (337), and a length from a center of the guide portion (337), which is a center in a direction parallel to the valve closing direction, to the other end portion of the rod portion (338) is shorter than a length from the center of the guide portion (337) to a tip of the valve portion (339), wherein the stopper (34) has an engagement hole (341a) into which an engagement projection (339c) of the valve portion (339) can engage. [2] The electromagnetic intake valve (3) according to claim 1, further comprising a biasing member holder (333) attached to the other end portion of the rod portion (338) and holding the valve biasing member (334). [3] An electromagnetic intake valve (3) according to claim 2, wherein the valve element (332), the seat element, the valve preloading element (334) and the preloading element holder (333) are assembled as a valve body unit. [4] The electromagnetic intake valve (3) according to claim 3, further comprising a stopper (34) formed separately from the valve body unit (33) for restricting movement of the valve element (332) in a valve opening direction, which is a direction opposite to the valve closing direction, by contact of the valve portion (339) when the valve element (332) moves in the valve opening direction. [5] The electromagnetic intake valve (3) according to claim 1, wherein the other end portion of the rod portion (338) is formed separately from the rod portion (338) and is in contact with a movable portion that drives the rod portion (338). [6] The electromagnetic intake valve (3) according to claim 5, wherein the movable portion urges the other end portion of the rod portion (338) 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. [7] Electromagnetic intake valve (3) according to claim 5, further comprising: a movable portion biasing member (334) disposed closer to the valve closing direction side than the movable portion and biasing the movable portion in a valve opening direction that is a direction opposite to the valve closing direction; and a magnetic core (323) which attracts the movable portion in the valve closing direction by an electromagnetic attraction force generated by energizing a coil, wherein the movable portion is preloaded in the valve opening direction by the movable portion biasing member (334) in a state where the coil is not energized, and moves the valve element (332) in the valve opening direction against a biasing force of the valve biasing member (334). [8] Electromagnetic intake valve (3) according to claim 7, further comprising: a stopper (34) that restricts the movement of the valve element (332) in a valve opening direction, which is a direction opposite to the valve closing direction, by contact of the valve portion (339) when the valve element (332) moves in the valve opening direction; and a preloading element holder (333) attached to the other end portion of the rod portion (338) and holding the valve preloading element (334), wherein the valve element (332), the seat element, the valve preloading element (334) and the preloading element holder (333) are assembled as a valve body unit (33), and in a state where the movable portion is attached to the valve body unit (33), the movable portion biases the other end portion of the rod portion (338) in the valve opening direction, and the valve portion (339) of the valve element (332) comes into contact with the stopper (34) to adjust a valve opening stroke of the valve portion (339). [9] Electromagnetic inlet valve (3) according to claim 1, wherein the valve portion (339) has a valve portion seat surface (335b) formed in a plane perpendicular to the valve closing direction and abutting against the seat surface (335b), and the seat surface (335b) of the seat element is formed in a plane perpendicular to the valve closing direction. [10] An electromagnetic intake valve (3) according to claim 5, wherein the movable portion comes into contact with the other end portion of the rod portion (338) on the valve closing direction side with respect to the guide portion (337) in the seat member. [11] High-pressure fuel supply pump comprising: a body having a pressure chamber; a piston carried by the body in a reciprocating manner and increasing or decreasing a capacity of the pressure chamber by a reciprocating movement; and an electromagnetic inlet valve (3) which releases a fuel into the pressure chamber, wherein the electromagnetic inlet valve comprises: a valve element (332) having a rod portion (338) and a valve portion (339) connected to an end portion of the rod portion (338); a seat member having a guide portion (337) guiding an outer periphery of the rod portion (338) and a seat surface (335b) on which the valve portion (339) sits; a valve biasing element (334) biasing the rod portion (338) in a valve closing direction in which the valve portion (339) approaches the seat surface (335b); and a stopper (34) which restricts the movement of the valve element (332) in a valve opening direction, which is a direction opposite to the valve closing direction, by contact of the valve portion (339) when the valve element (332) moves in the valve opening direction, wherein the valve preloading element (334) is arranged closer to the side of the valve closing direction than the guide portion (337), and a length from a center of the guide portion (337), which is a center in a direction parallel to the valve closing direction, to the other end portion of the rod portion (338) is shorter than a length from the center of the guide portion (337) to a tip of the valve portion (339), wherein the stopper (34) has an engagement hole (341a) into which an engagement projection (339c) of the valve portion (339) can engage.

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