WO2023203761A1

WO2023203761A1 - Electromagnetic valve mechanism and fuel supply pump

Info

Publication number: WO2023203761A1
Application number: PCT/JP2022/018575
Authority: WO
Inventors: 将通谷貝; 亨小野瀬; 章吾南原
Original assignee: 日立Astemo株式会社
Priority date: 2022-04-22
Filing date: 2022-04-22
Publication date: 2023-10-26

Abstract

The present invention addresses the problem of reducing radiation sound from an electromagnetic valve mechanism. The electromagnetic valve mechanism is provided with a solenoid that drives a valve part. The solenoid has an electromagnetic coil, a stator that is disposed on an inner side in a radial direction of the electromagnetic coil, a mover that engages the valve part and generates a magnetic suction force between the mover and the stator, a yoke that is formed in a cylindrical shape surrounding the electromagnetic coil, and a lid member that blocks an opening part of the yoke. The stator protrudes from one opening of the yoke. The lid member is formed in a substantially annular shape having an inner peripheral part and an outer peripheral part. The inner peripheral part of the lid member is in contact with the stator, and the outer peripheral part of the lid member is fixed to the inner peripheral part of the yoke.

Description

Solenoid valve mechanism and fuel supply pump

The present invention relates to a solenoid valve mechanism and a fuel supply pump.

High-pressure fuel supply pumps that forcefully feed fuel to fuel injection valves of internal combustion engines have been known. This high-pressure fuel supply pump is described in, for example, Patent Document 1. The high-pressure fuel supply pump described in Patent Document 1 includes an electromagnetic valve mechanism driven by a solenoid. The electromagnetic valve mechanism includes an electromagnetic coil, a yoke that is disposed radially outside the electromagnetic coil and has one end open, and a lid member (second yoke) that closes the opening of the yoke. The yoke, the lid member, and the fixed core constitute a part of the magnetic path of the solenoid. The lid member is formed in an annular shape. The inner diameter side of the lid member is held by a fixed core.

International Publication No. 2020/085041

However, in the high-pressure fuel supply pump described in Patent Document 1, the lid member that forms part of the magnetic path of the solenoid is held by a fixed core on its inner diameter side. Therefore, when the collision force generated within the solenoid is transmitted to the lid member via the fixed core, the lid member vibrates with respect to the yoke. As a result, there was a problem in that the sound radiated from the solenoid valve mechanism became louder.

An object of the present invention is to provide an electromagnetic valve mechanism and a fuel supply pump that can reduce radiated sound in consideration of the above problems.

In order to solve the above problems and achieve the present object, the electromagnetic valve mechanism includes a valve part that opens and closes the fuel introduction opening, and a solenoid that moves the valve part in the opening and closing direction. A solenoid consists of an electromagnetic coil, a stator placed radially inside the electromagnetic coil, a movable element that engages with a valve part and generates a magnetic attraction force between it and the stator, and a cylinder surrounding the electromagnetic coil. It has a yoke formed in the shape of a shape, and a lid member that closes an opening of the yoke. A stator protrudes from one opening of the yoke. The lid member is formed into a substantially annular shape having an inner circumferential portion and an outer circumferential portion. The inner peripheral part of the lid member contacts the stator, and the outer peripheral part of the lid member is fixed to the inner peripheral part of the yoke.

Further, the fuel supply pump of the present invention includes a body including a pressurizing chamber, a plunger that is supported by the body so as to be able to reciprocate and increases or decreases the capacity of the pressurizing chamber by reciprocating movement, and a plunger that discharges fuel into the pressurizing chamber. and the above electromagnetic valve mechanism.

According to the electromagnetic valve mechanism configured as described above, vibration of the lid member can be suppressed and radiated sound can be reduced.
Note that problems, configurations, and effects other than those described above will be made clear by the description of the embodiments below.

1 is an overall configuration diagram of a fuel supply system using a high-pressure fuel supply pump according to a first embodiment of the present invention. FIG. 1 is a longitudinal cross-sectional view of a high-pressure fuel supply pump according to a first embodiment of the present invention. FIG. 1 is a horizontal cross-sectional view of the high-pressure fuel supply pump according to the first embodiment of the present invention, viewed from above. FIG. 2 is an enlarged longitudinal sectional view of the electromagnetic suction valve mechanism in the high-pressure fuel supply pump according to the first embodiment of the present invention, showing a state in which the electromagnetic suction valve mechanism is open. FIG. 2 is a diagram of the electromagnetic suction valve mechanism of the high-pressure fuel supply pump according to the first embodiment of the present invention, viewed from the side opposite to the pressurizing chamber. FIG. 7 is an enlarged longitudinal sectional view of the electromagnetic suction valve mechanism in the high-pressure fuel supply pump according to the second embodiment of the present invention, showing a state in which the electromagnetic suction valve mechanism is open.

1. Embodiment Hereinafter, a high-pressure fuel supply pump according to an embodiment of the present invention will be described. Note that common members in each figure are given the same reference numerals.

[Fuel supply system]
First, a fuel supply system using a high-pressure fuel supply pump according to the present embodiment will be explained using FIG. 1.
FIG. 1 is an overall configuration diagram of a fuel supply system using a high-pressure fuel supply pump according to this embodiment.

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

Fuel in the fuel tank 103 is pumped up by a feed pump 102 that is 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 is sent to the low-pressure fuel inlet 51 of the high-pressure fuel supply pump 100 through the low-pressure pipe 104.

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

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

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

The high-pressure fuel supply pump 100 includes a pressure pulsation reduction mechanism 9, an electromagnetic suction valve mechanism 3 that is a variable capacity mechanism, a relief valve mechanism 4 (see FIG. 2), and a discharge valve mechanism 8. Fuel flowing from the low-pressure fuel intake port 51 reaches the intake port 31b of the electromagnetic intake valve mechanism 3 via the pressure pulsation reduction mechanism 9 and the intake passage 10b.

The fuel that has flowed into the electromagnetic suction valve mechanism 3 passes through the suction valve 32, flows through the suction passage 1a formed in the body 1, and then flows into the pressurizing chamber 11. A plunger 2 is slidably held in the pressurizing chamber 11 . The plunger 2 reciprocates as power is transmitted by a cam 91 of the engine (see FIG. 2).

In the pressurizing chamber 11, fuel is sucked from the electromagnetic intake valve mechanism 3 during the downward stroke of the plunger 2, and the fuel is pressurized during the compression stroke. When the fuel pressure in the pressurizing chamber 11 exceeds a set value, the discharge valve mechanism 8 opens, and high-pressure fuel is force-fed to the common rail 106 through the discharge passage 1f. The discharge of fuel by the high-pressure fuel supply pump 100 is controlled by opening and closing the electromagnetic intake valve mechanism 3. Opening and closing of the electromagnetic intake valve mechanism 3 is controlled by the ECU 101.

Abnormally high pressure may occur in the fuel in the common rail 106 etc. due to a failure of the injector 107 or the like. In this case, when the differential pressure between the fuel at the fuel discharge port 12a (see FIG. 2) communicating with the common rail 106 and the fuel in the pressurizing chamber 11 exceeds a preset value, the relief valve mechanism 4 opens. . As a result, the abnormally high pressure fuel is returned to the pressurizing chamber 11 through the relief valve mechanism 4. As a result, even if the fuel becomes abnormally high pressure, the pipes such as the common rail 106 are protected.

[High pressure fuel supply pump]
Next, the configuration of the high-pressure fuel supply pump 100 will be explained using FIGS. 2 and 3.
FIG. 2 is a longitudinal cross-sectional view of the high-pressure fuel supply pump 100 taken in a cross section orthogonal to the horizontal direction. FIG. 3 is a horizontal cross-sectional view of the high-pressure fuel supply pump 100 taken along a cross section perpendicular to the vertical direction.

As shown in FIGS. 2 and 3, the body 1 of the high-pressure fuel supply pump 100 is provided with the above-mentioned suction passage 1a and the mounting flange 1b. The mounting flange 1b is in close contact with a fuel pump mounting portion 90 of an engine (internal combustion engine), and is fixed with a plurality of bolts (screws) not shown. That is, the high-pressure fuel supply pump 100 is fixed to the fuel pump mounting portion 90 by the mounting flange 1b.

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

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

The body 1 is provided with a fixing portion 1c that engages with the center portion of the cylinder 6 in the axial direction. The fixing portion 1c of the body 1 presses the cylinder 6 upward (upward in FIG. 2). Thereby, the fuel pressurized in the pressurizing chamber 11 can be prevented from leaking from between the upper end surface of the cylinder 6 and the body 1.

A tappet 92 is provided at the lower end of the plunger 2. Tappet 92 converts the rotational motion of cam 91 attached to the camshaft of the engine into vertical motion and transmits it to plunger 2 . The plunger 2 is urged toward the cam 91 by a spring 16 via a retainer 15. Thereby, the plunger 2 is crimped onto the tappet 92. The tappet 92 reciprocates as the cam 91 rotates. The plunger 2 reciprocates together with the tappet 92 to change the volume of the pressurizing chamber 11.

A seal holder 17 is arranged between the cylinder 6 and the retainer 15. The seal holder 17 is formed into a cylindrical shape into which the plunger 2 is inserted. A subchamber 17a is formed between the upper part of the seal holder 17 and the pump body 1. Further, the seal holder 17 holds a plunger seal 18 at a lower end portion on the retainer 15 side.

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

In FIG. 2, the plunger 2 reciprocates in the vertical direction. When the plunger 2 descends, the volume of the pressurizing chamber 11 increases, and when the plunger 2 ascends, the volume of the pressurizing chamber 11 decreases. That is, the plunger 2 is arranged so as to reciprocate in the direction of expanding and contracting the volume of the pressurizing chamber 11.

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

The auxiliary chamber 17a communicates with the low-pressure fuel chamber 10 through a fuel passage 10c (see FIG. 3). When the plunger 2 descends, fuel flows from the auxiliary chamber 17a to the low pressure fuel chamber 10. When the plunger 2 is raised, fuel flows from the low pressure fuel chamber 10 to the auxiliary chamber 17a. Thereby, the fuel flow rate into and out of the pump during the suction stroke or return stroke of the high-pressure fuel supply pump 100 can be reduced. As a result, pressure pulsations occurring inside the high-pressure fuel supply pump 100 can be reduced.

The body 1 is provided with a relief valve mechanism 4 that communicates with the pressurizing chamber 11. The relief valve mechanism 4 opens when some problem occurs in the common rail 106 or a member beyond it and the pressure of the fuel in the common rail 106 becomes high pressure equal to or higher than a predetermined value. As a result, the fuel in the discharge passage 1f returns to the pressurizing chamber 11.

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 of the relief spring 41 is in contact with the body 1. The other end of the relief spring 41 is in contact with the relief valve holder 42 . The relief valve holder 42 is engaged with the relief valve 43. The urging force of the relief spring 41 acts on the relief valve 43 via the relief valve holder 42 .

The relief valve 43 is pressed by the urging force of the relief spring 41. This blocks the fuel passage of the seat member 44. The fuel passage of the seat member 44 communicates with the discharge passage 1f. Movement of fuel between the pressurizing chamber 11 (upstream side) and the seat member 44 (downstream side) is blocked by the relief valve 43 coming into contact with (adhering to) the seat member 44 .

When the pressure of the fuel in the common rail 106 and the members beyond it increases, the fuel on the seat member 44 side presses the relief valve 43. As a result, the relief valve 43 moves against the biasing force of the relief spring 41. As a result, the relief valve 43 opens, and the fuel in the discharge passage 1f returns to the pressurizing 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.

Note that although the relief valve mechanism 4 of this embodiment communicates with the pressurizing chamber 11, it is not limited to this. The relief valve mechanism according to the present invention may, for example, communicate with a low pressure passage (low pressure fuel inlet 51, suction passage 10b, etc.).

As shown in FIG. 3, a suction joint 5 is attached to the side surface of the body 1. The suction joint 5 is connected to a low pressure pipe 104 through which fuel supplied from a fuel tank 103 passes. Fuel in the fuel tank 103 is supplied into the high-pressure fuel supply pump 100 from the suction joint 5.

The suction joint 5 has a low-pressure fuel suction port 51 connected to the low-pressure pipe 104 and a suction flow path 52 communicating with the low-pressure fuel suction port 51. A suction filter (not shown) is disposed within the suction flow path 52. The suction filter removes foreign matter present in the fuel and prevents foreign matter from entering the high-pressure fuel supply pump 100. The fuel that has passed through the intake flow path 52 reaches the intake port 31b (see FIG. 2) of the electromagnetic intake valve mechanism 3 via the pressure pulsation reduction mechanism 9 provided in the low-pressure fuel chamber 10 and the intake passage 10b (see FIG. 2). do.

As shown in FIG. 2, the body 1 of the high-pressure fuel supply pump 100 is provided with a low-pressure fuel chamber 10. The low pressure fuel chamber 10 is covered by a damper cover 14. The low pressure fuel chamber 10 is provided with a low pressure fuel passage 10a and an intake passage 10b. The suction passage 10b communicates with the suction port 31b (see FIG. 2) of the electromagnetic suction valve mechanism 3, and the fuel that has passed through the low-pressure fuel passage 10a passes through the suction passage 10b to the suction port 31b of the electromagnetic suction valve mechanism 3. 31b is reached.

A pressure pulsation reduction mechanism 9 is provided in the low pressure fuel flow path 10a. When the fuel that has flowed into the pressurizing chamber 11 is returned to the suction passage 10b (see FIG. 2) through the electromagnetic suction valve mechanism 3 which is in an open state again, pressure pulsations occur in the low pressure fuel chamber 10. The pressure pulsation reduction mechanism 9 reduces pressure pulsations generated within the high-pressure fuel supply pump 100 from spreading to the low-pressure piping 104.

The pressure pulsation reduction mechanism 9 has a metal diaphragm damper made by laminating two corrugated disk-shaped metal plates together at their outer peripheries. An inert gas such as argon is injected into the metal diaphragm damper. A metal diaphragm damper absorbs or reduces pressure pulsations by expanding and contracting.

As shown in FIG. 3, the discharge valve mechanism 8 is connected to the outlet side of the pressurizing chamber 11. The discharge valve mechanism 8 is housed in a discharge valve chamber 1d formed in the body 1. The discharge valve mechanism 8 includes a discharge valve seat member 81 and a discharge valve 82 that comes into contact with and separates from the discharge valve seat member 81. The discharge valve mechanism 8 also includes a discharge valve spring 83 that biases the discharge valve 82 toward the discharge valve seat member 81, a discharge valve stopper 84 that determines the lift amount (movement distance) of the discharge valve 82, and a discharge valve stopper 84 that determines the lift amount (movement distance) of the discharge valve 82. It is provided with a plug 85 that locks the movement of. The discharge valve stopper 84 is press-fitted into the plug 85. Plug 85 is joined to body 1 by welding.

A discharge joint 12 is joined to the body 1 by a welded portion 12b. The discharge joint 12 has a fuel discharge port 12a. The fuel discharge port 12a communicates with the discharge valve chamber 1d via a discharge passage 1f. The discharge passage 1f extends horizontally inside the body 1. The fuel discharge port 12a is connected to the common rail 106.

When the fuel pressure in the pressurizing chamber 11 is lower than the fuel pressure in the discharge valve chamber 1d, the differential pressure acting on the discharge valve 82 and the biasing force of the discharge valve spring 83 cause the discharge valve 82 to be pressed against the discharge valve seat member 81. Ru. As a result, the discharge valve mechanism 8 enters the closed state. On the other hand, when the fuel pressure in the pressurizing chamber 11 becomes greater than the fuel pressure in the discharge valve chamber 1d and the differential pressure acting on the discharge valve 82 becomes greater than the biasing force of the discharge valve spring 83, the discharge valve 82 becomes a discharge valve. It separates from the sheet member 81. As a result, the discharge valve mechanism 8 becomes open.

When the discharge valve mechanism 8 is in the open state, the fuel in the pressurizing chamber 11 is discharged to the common rail 106 (see FIG. 1) through the discharge valve chamber 1d, the discharge passage 1f, and the fuel discharge port 12a of the discharge joint 12. Ru. With the above configuration, the discharge valve mechanism 8 functions as a check valve that restricts the direction of fuel flow.

[Solenoid suction valve mechanism]
Next, the configuration of the electromagnetic intake valve mechanism 3 will be explained using FIGS. 4 and 5.
FIG. 4 is a longitudinal sectional view showing a state in which the electromagnetic intake valve mechanism 3 is opened. FIG. 5 is a diagram of the electromagnetic suction valve mechanism 3 viewed from the side opposite to the pressurizing chamber 11.

As shown in FIG. 4, the electromagnetic intake valve mechanism 3 is inserted into a side hole formed in the body 1. The electromagnetic suction valve mechanism 3 includes a suction valve seat 31 press-fitted into a horizontal hole formed in the body 1, a suction valve 32, a rod 33, a rod biasing spring 34, an electromagnetic coil 35, and an anchor 36. are doing. The suction valve 32 is a specific example of the valve portion according to the present invention. The rod 33 and the anchor 36 represent a specific example of the mover according to the present invention.

The suction valve seat 31 is formed into a cylindrical shape. A seating portion 31a is provided on the inner peripheral portion of the suction valve seat 31. The suction valve seat 31 is formed with a suction port 31b that reaches from the outer circumference to the inner circumference. The suction port 31b communicates with the suction passage 10b in the low pressure fuel chamber 10 described above. Further, the suction valve seat 31 has a rod guide 31c through which the rod 33 passes.

A stopper 37 facing the seating portion 31a of the suction valve seat 31 is arranged in the side hole formed in the body 1. The suction valve 32 is arranged between the stopper 37 and the seating portion 31a. Further, a valve biasing spring 38 is interposed between the stopper 37 and the suction valve 32. The valve biasing spring 38 biases the suction valve 32 toward the seating portion 31a.

The suction valve 32 closes the communication portion between the suction port 31b and the pressurizing chamber 11 by coming into contact with the seating portion 31a. As a result, the electromagnetic intake valve mechanism 3 enters the closed state. On the other hand, the suction valve 32 opens the communication portion between the suction port 31b and the pressurizing chamber 11 by coming into contact with the stopper 37. As a result, the electromagnetic intake valve mechanism 3 becomes open.

The rod 33 passes through the rod guide 31c of the suction valve seat 31 and the anchor 36. The rod 33 is formed with a rod flange 33a. One end of a rod biasing spring 34 is engaged with the rod flange 33a. The other end of the rod biasing spring 34 is engaged with a fixed core 39 arranged to surround the rod biasing spring 34 . The rod biasing spring 34 biases the suction valve 32 via the rod 33 in the valve opening direction, which is the stopper 37 side. Note that the fixed core 39 represents a specific example of the stator according to the present invention.

The anchor 36 is formed into a substantially cylindrical shape. One end of an anchor biasing spring 40 contacts one end of the anchor 36 in the axial direction. The other end of the anchor 36 in the axial direction faces the end surface of the fixed core 39. The other end of the anchor 36 in the axial direction is formed with a flange abutting portion against which the rod flange 33a of the rod 33 abuts.

The other end of the anchor biasing spring 40 is in contact with the rod guide 31c. The anchor biasing spring 40 biases the anchor 36 toward the rod flange 33a of the rod 33. The movable distance of the anchor 36 is set longer than the movable distance of the suction valve 32. Thereby, the suction valve 32 can be reliably brought into contact (seated) with the seating portion 31a. As a result, the electromagnetic intake valve mechanism 3 can be reliably brought into the closed state.

An anchor guide 310 is connected to the opening of the side hole formed in the body 1. Anchor guide 310 is formed into a substantially cylindrical shape. An outer peripheral portion of the anchor guide 310 at one end in the axial direction is fitted into a horizontal hole formed in the body 1. Anchor guide 310 is fixed to body 1 by welding.

The anchor 36 is slidably engaged with the inner peripheral portion of the anchor guide 310. That is, the anchor 36 is guided by the inner peripheral portion of the anchor guide 310 and moves in the axial direction (the valve opening direction and the valve closing direction). The other end of the anchor guide 310 in the axial direction protrudes from the body 1. A yoke 320 is fitted to the outer circumferential portion of the other end of the anchor guide 310 in the axial direction. Anchor guide 310 is press-fitted and fixed to yoke 320.

The yoke 320 is formed into a cylindrical shape with a bottom that surrounds the electromagnetic coil 35. The yoke 320 includes a cylindrical portion 321 surrounding the electromagnetic coil 35 and a fitting portion 322 provided at one end of the cylindrical portion 321 in the axial direction. The fixed core 39 protrudes from the other end of the cylindrical portion 321 in the axial direction. Fitting portion 322 forms the bottom of yoke 320 . A fitting hole for fitting the anchor guide 310 is formed in the center of the fitting portion 322 .

The opening of the cylinder portion 321 on the opposite side to the fitting portion 322 is closed by a lid member 330. Yoke 320 and lid member 330 constitute a magnetic circuit. The lid member 330 is made of the same material as the yoke 320. Examples of the material for the yoke 320 and the lid member 330 include magnetic stainless steel material.

As shown in FIG. 5, the lid member 330 is made of a substantially annular plate. The lid member 330 has an inner peripheral part 331 and an outer peripheral part 332. The inner peripheral portion 331 is formed by providing a circular through hole approximately in the center of the lid member 330 .

The fixed core 39 passes through the through hole of the lid member 330. The inner circumferential portion 331 of the lid member 330 is in contact with the outer circumferential portion of the fixed core 39. The outer peripheral portion 332 of the lid member 330 has an arcuate arc portion 332a and a straight portion 332b continuous to both ends of the arcuate portion 332a. The arcuate portion 332a of the lid member 330 is press-fitted and fixed to the inner peripheral portion of the cylindrical portion 321 of the yoke 320.

As shown in FIG. 4, the electromagnetic coil 35 is arranged so as to go around the fixed core 39 inside the cylindrical portion 321 of the yoke 320. A terminal member 30 (see FIG. 2) is electrically connected to the electromagnetic coil 35. A current flows through the electromagnetic coil 35 via the terminal member 30. The terminal member 30 is arranged in the recess of the connector 30a. The connector 30a is integrally molded with the terminal member 30 and the electromagnetic coil 35.

The connector 30a passes through a notch in the yoke 320. A lower portion of the connector 30a faces the straight portion 332b of the lid member 330. The straight portion 332b of the lid member 330 is a cutout portion for avoiding interference between the connector 30a and the lid member 330.

A sealing 340 is provided on the inner circumference of the electromagnetic coil 35. A sealing 340 provided at one end of the electromagnetic coil 35 in the axial direction is fixed to the anchor guide 310 by welding. On the other hand, a sealing 340 provided at the other end of the electromagnetic coil 35 in the axial direction is fixed to the fixed core 39 by welding.

On the inner circumferential side of the ceiling 340 and the anchor guide 310, an anchor 36 and a rod 33, which are movers, a rod guide 31c, which is a fixed part, a rod biasing spring 34, and an anchor biasing spring 40 are arranged. .

In a non-energized state where no current flows through the electromagnetic coil 35, the rod 33 is biased in the valve opening direction by the biasing force of the rod biasing spring 34, and presses the suction valve 32 in the valve opening direction. As a result, the suction valve 32 is separated from the seating portion 31a and comes into contact with the stopper 37, and the electromagnetic suction valve mechanism 3 is in an open state. That is, the electromagnetic suction valve mechanism 3 is of a normally open type that opens in a non-energized state.

When the electromagnetic suction valve mechanism 3 is in the open state, fuel in the suction port 31b passes between the suction valve 32 and the seating portion 31a, passes through a plurality of fuel passage holes (not shown) in the stopper 37, and the suction passage 1a. It flows into the pressurizing chamber 11. When the electromagnetic suction valve mechanism 3 is in the open state, the suction valve 32 comes into contact with the stopper 37, so that the position of the suction valve 32 in the opening direction is regulated. When the electromagnetic suction valve mechanism 3 is in the open state, the gap existing between the suction valve 32 and the seating portion 31a is the movable range of the suction valve 32, and this is the valve opening stroke 32S.

When current flows through the electromagnetic coil 35, magnetic flux is generated. The generated magnetic flux passes through the fixed core 39, the lid member 330, the yoke 320, the anchor guide 310, and the anchor 36 as a magnetic path. Then, a magnetic attraction force acts on each of the magnetic attraction surfaces S of the anchor 36 and the fixed core 39. As a result, the anchor 36 moves against the biasing force of the rod biasing spring 34 and comes into contact with the fixed core 39.

When the anchor 36 moves toward the fixed core 39 in the valve closing direction, the rod 33 that the anchor 36 engages moves together with the anchor 36. As a result, the suction valve 32 is released from the biasing force in the valve-opening direction and moves in the valve-closing direction by the biasing force of the valve biasing spring 38. When the suction valve 32 comes into contact with the seating portion 31a of the suction valve seat 31, the electromagnetic suction valve mechanism 3 enters the closed state.

There should be no air gap between the components constituting the magnetic path described above, except between the fixed core 39 and the anchor 36, which are magnetic attraction surfaces, and between the anchor 36 and the anchor guide 310, which are sliding surfaces. is desirable. In this embodiment, the yoke 320 and the anchor guide 310 are press-fitted and fixed, so there is no air gap between the yoke 320 and the anchor guide 310.

Furthermore, the outer circumferential portion 332 (arc portion 332a) of the lid member 330 is press-fitted and fixed to the inner circumferential portion of the cylindrical portion 321 of the yoke 320. Therefore, there is no air gap between the lid member 330 and the yoke 320. Further, the inner peripheral portion 331 of the lid member 330 is in contact with the fixed core 39. Therefore, there is no air gap between the lid member 330 and the fixed core 39. With the above structure, the air gap in the magnetic path of the electromagnetic intake valve mechanism 3 can be minimized. As a result, the magnetic efficiency of the electromagnetic intake valve mechanism 3 can be improved.

Further, as shown in FIG. 5, the outer peripheral portion 332 of the lid member 330 has an arcuate portion 332a. The entire area of the arcuate portion 332a is press-fitted into the inner peripheral portion of the cylindrical portion 321 of the yoke 320. Thereby, vibration of the lid member 330 can be suppressed when the electromagnetic suction valve mechanism 3 is operated. As a result, the radiated sound generated due to the vibration of the lid member 330 can be reduced.

[High pressure fuel pump operation]
Next, the operation of the high-pressure fuel pump according to this embodiment will be explained using FIG. 2.

In FIG. 2, when the plunger 2 is lowered and the electromagnetic intake valve mechanism 3 is open, fuel flows into the pressurizing chamber 11 from the intake passage 1a. Hereinafter, the stroke in which the plunger 2 descends will be referred to as a suction stroke. On the other hand, when the plunger 2 is raised and the electromagnetic intake valve mechanism 3 is closed, the pressure of the fuel in the pressurizing chamber 11 is increased. Thereby, the fuel in the pressurizing chamber 11 is forced to pass through the discharge valve mechanism 8 and to the common rail 106 (see FIG. 1). Hereinafter, the process in which the plunger 2 moves upward will be referred to as a compression stroke.

If the electromagnetic suction valve mechanism 3 is closed during the compression stroke, the fuel sucked into the pressurizing chamber 11 during the suction stroke is pressurized and discharged to the common rail 106 side. On the other hand, if the electromagnetic suction valve mechanism 3 is open during the compression stroke, the fuel in the pressurizing chamber 11 is pushed back to the suction passage 1a side and is not discharged to the common rail 106 side. In this way, the discharge of fuel by the high-pressure fuel supply pump 100 is controlled by opening and closing the electromagnetic intake valve mechanism 3. Opening and closing of the electromagnetic intake valve mechanism 3 is controlled by the ECU 101.

In the suction stroke, the volume of the pressurizing chamber 11 increases and the fuel pressure within the pressurizing chamber 11 decreases. Thereby, the fuel pressure in the pressurizing chamber 11 becomes lower than the fuel pressure in the suction port 31b. When the biasing force due to the pressure difference between the two exceeds the biasing force due to the valve biasing spring 38, the suction valve 32 separates from the seating portion 31a. As a result, the electromagnetic suction valve mechanism 3 becomes open. As a result, the fuel on the suction port 31b side passes between the suction valve 32 and the seating portion 31a, passes through the plurality of holes provided in the stopper 37, and flows into the pressurizing chamber 11.

After completing the suction stroke, move on to the compression stroke. At this time, the electromagnetic coil 35 remains in a non-energized state, and no magnetic attraction force is acting between the anchor 36 and the fixed core 39. Then, a biasing force in the valve opening direction is applied to the suction valve 32 in accordance with the difference in the biasing forces between the anchor biasing spring 40 and the rod biasing spring 34. Furthermore, fluid force (pressure force in the valve closing direction) generated when fuel flows backward from the pressurizing chamber 11 to the low-pressure fuel flow path 10a is applied to the suction valve 32.

In this state, in order for the electromagnetic suction valve mechanism 3 to maintain the valve open state, the difference between the biasing forces between the anchor biasing spring 40 and the rod biasing spring 34 is set to be larger than the fluid force. The volume of the pressurizing chamber 11 decreases as the plunger 2 rises. Therefore, the fuel that has been sucked into the pressurizing chamber 11 passes between the suction valve 32 and the suction valve seat 31 and is returned to the suction port 31b. Therefore, the fuel pressure inside the pressurizing chamber 11 does not increase. This stroke is called a return stroke.

In the return process, when a control signal from the ECU 101 (see FIG. 1) is applied to the electromagnetic intake valve mechanism 3, a current flows through the electromagnetic coil 35 via the terminal member 30. When a current flows through the electromagnetic coil 35, a magnetic attraction force acts on the magnetic attraction surface S of the fixed core 39 and the anchor 36, and the anchor 36 is attracted to the fixed core 39.

Then, when the magnetic attraction force becomes larger than the biasing force of the rod biasing spring 34, the anchor 36 moves toward the fixed core 39 (in the valve closing direction) against the biasing force of the rod biasing spring 34. As a result, the rod 33 that engages with the anchor 36 moves in a direction away from the suction valve 32. As a result, the suction valve 32 is seated on the seating portion 31a due to the biasing force of the valve biasing spring 38 and the fluid force caused by the fuel flowing into the suction passage 10b. When the suction valve 32 is seated on the seating portion 31a, the electromagnetic suction valve mechanism 3 is in a closed state.

After the electromagnetic intake valve mechanism 3 enters the closed state, the pressure of the fuel in the pressurizing chamber 11 is increased as the plunger 2 rises. When the pressure in the pressurizing chamber 11 exceeds a predetermined pressure, the fuel in the pressurizing chamber 11 passes through the discharge valve mechanism 8 and is discharged to the common rail 106 (see FIG. 1). This stroke is called a discharge stroke. That is, the compression stroke from the lower starting point to the upper starting point of the plunger 2 consists of a return stroke and a discharge stroke. By controlling the timing at which the electromagnetic coil 35 of the electromagnetic intake valve mechanism 3 is energized, the amount of high-pressure fuel discharged can be controlled.

If the timing of energizing the electromagnetic coil 35 is made earlier, the proportion of the return stroke during the compression stroke becomes smaller and the proportion of the discharge stroke becomes larger. As a result, less fuel is returned to the suction passage 10b, and more fuel is discharged under high pressure. On the other hand, if the timing of energizing the electromagnetic coil 35 is delayed, the proportion of the return stroke during the compression stroke will increase, and the proportion of the discharge stroke will decrease. As a result, more fuel is returned to the suction passage 10b, and less fuel is discharged under high pressure. In this way, by controlling the timing of energization to the electromagnetic coil 35, the amount of fuel discharged at high pressure can be controlled to the amount required by the engine (internal combustion engine).

2. Second Embodiment Next, a high-pressure fuel pump according to a second embodiment will be described with reference to FIG. 6.
FIG. 6 is a longitudinal sectional view showing an open state of the electromagnetic intake valve mechanism 3A according to the second embodiment.

The high-pressure fuel supply pump according to the second embodiment has the same configuration as the high-pressure fuel supply pump 100 according to the first embodiment. The only difference between the high-pressure fuel supply pump according to the second embodiment and the high-pressure fuel supply pump 100 (see FIG. 2) is the electromagnetic intake valve mechanism 3A. Therefore, here, the configuration of the electromagnetic intake valve mechanism 3A will be explained, and the explanation of the configuration common to the high-pressure fuel supply pump 100 will be omitted.

[Solenoid suction valve mechanism]
As shown in FIG. 6, the electromagnetic suction valve mechanism 3A is inserted into a side hole formed in the body 1. The electromagnetic suction valve mechanism 3A includes a suction valve seat 31, a suction valve 32, a rod 33, a rod biasing spring 34, an electromagnetic coil 35, and an anchor 36.

An anchor guide 310 is connected to the opening of the side hole formed in the body 1. Anchor guide 310 is press-fitted and fixed to yoke 320. The yoke 320 includes a cylindrical portion 321 surrounding the electromagnetic coil 35 and a fitting portion 322 provided at one end of the cylindrical portion 321 in the axial direction. An opening in the cylindrical portion 321 on the side opposite to the fitting portion 322 is closed by a lid member 330.

The lid member 330 has an inner peripheral part 331 and an outer peripheral part 332 (see FIG. 5). An inner peripheral portion 331 of the lid member 330 is in contact with the fixed core 39. Therefore, there is no air gap between the lid member 330 and the fixed core 39.

The outer circumferential portion 332 of the lid member 330 has an arc-shaped arc portion 332a and a straight portion 332b continuous to both ends of the arc portion 332a. The arcuate portion 332a of the lid member 330 is fixed to the inner peripheral portion of the cylindrical portion 321 of the yoke 320 by a welded portion 350. The welded portion 350 is continuously formed along the arcuate portion 332a. Therefore, there is no air gap between the lid member 330 and the yoke 320.

With the above structure, the air gap in the magnetic path of the electromagnetic intake valve mechanism 3 can be minimized. As a result, the magnetic efficiency of the electromagnetic intake valve mechanism 3 can be improved. Furthermore, vibration of the lid member 330 can be suppressed during operation of the electromagnetic intake valve mechanism 3. As a result, the radiated sound generated due to the vibration of the lid member 330 can be reduced.

Note that as a method of fixing the lid member 330, for example, caulking fixing or adhesive fixing using an adhesive can also be adopted. At this time, it is preferable that the arcuate portion 332a of the lid member 330 is connected to the inner peripheral portion of the cylindrical portion 321 of the yoke 320 without any gap. Thereby, the air gap in the magnetic path of the electromagnetic suction valve mechanism 3 can be minimized, and the magnetic efficiency of the electromagnetic suction valve mechanism 3 can be improved.

Furthermore, in the electromagnetic intake valve mechanism according to the present invention, the inner peripheral portion 331 of the lid member 330 may be fixed to the fixed core 39. That is, the lid member 330 may be held by the fixed core 39. Thereby, vibration of the lid member 330 can be suppressed more than when the lid member 330 is not fixed to the fixed core 39. As a result, radiated sound can be reduced more than when the lid member 330 is fixed to the fixed core 39.

As explained above, the electromagnetic intake valve mechanism 3 (electromagnetic valve mechanism) includes an intake valve 32 (valve part) that opens and closes the intake valve seat 31 (fuel introduction opening), and a solenoid that operates when the intake valve 32 is moved in the opening/closing direction. Equipped with The solenoid engages with the electromagnetic coil 35, a fixed core 39 (stator) disposed radially inside the electromagnetic coil 35, and the intake valve 32, and generates a magnetic attraction force between the electromagnetic coil 35 and the fixed core 39. It has an anchor 36 (mover), a cylindrical yoke 320 that surrounds the electromagnetic coil 35, and a lid member 330 that closes the opening of the yoke 320. Fixed core 39 protrudes from one opening of yoke 320. The lid member 330 is formed into a substantially annular shape having an inner peripheral part 331 and an outer peripheral part 332. An inner peripheral part 331 of the lid member 330 contacts the fixed core 39, and an outer peripheral part 332 of the lid member 330 is fixed to the inner peripheral part of the yoke 320.
Thereby, vibration of the lid member 330 can be suppressed when the electromagnetic suction valve mechanism 3 is operated. As a result, the radiated sound generated due to the vibration of the lid member 330 can be reduced. Furthermore, the air gap in the magnetic path of the electromagnetic suction valve mechanism 3 can be minimized, and the magnetic efficiency of the electromagnetic suction valve mechanism 3 can be improved.

Further, the lid member 330 of the electromagnetic suction valve mechanism 3 is press-fitted and fixed to the yoke 320.
Thereby, the lid member 330 can be easily fixed to the yoke 320. Further, it is possible to prevent an air gap from occurring between the lid member 330 and the yoke 320.

Further, the lid member 330 of the electromagnetic suction valve mechanism 3A is welded and fixed to the yoke 320 by a welding portion 350.
Thereby, the lid member 330 can be firmly fixed to the yoke 320. Further, it is possible to prevent an air gap from occurring between the lid member 330 and the yoke 320.

Further, the lid member 330 of the electromagnetic suction valve mechanism 3 may be fixed to the yoke 320 by caulking.
Thereby, the lid member 330 can be easily fixed to the yoke 320. Further, it is possible to prevent an air gap from occurring between the lid member 330 and the yoke 320.

Further, the lid member 330 of the electromagnetic suction valve mechanism 3 may be adhesively fixed to the yoke 320.
Thereby, the lid member 330 can be easily fixed to the yoke 320. Further, it is possible to prevent an air gap from occurring between the lid member 330 and the yoke 320.

Further, the outer peripheral portion 332 of the lid member 330 in the electromagnetic suction valve mechanism 3 includes an arcuate portion 332a and a straight portion 332b continuous to both ends of the arcuate portion 332a. The arc portion 332a is fixed to the yoke 320.
Thereby, the straight part 332b becomes a notch part for avoiding interference between the lid member 330 and other parts (the connector 30a) of the electromagnetic suction valve mechanism 3. Further, the arc portion 332a can be easily fixed to the inner peripheral portion of the yoke 320. Furthermore, the arc portion 332a can be easily aligned along the inner peripheral portion of the yoke 320. Thereby, it is possible to prevent an air gap from occurring between the arc portion 332a and the yoke 320.

Further, an inner peripheral portion 331 of the lid member 330 in the electromagnetic suction valve mechanism 3 is fixed to a fixed core 39 (stator).
Thereby, vibration of the lid member 330 can be suppressed more than when the lid member 330 is not fixed to the fixed core 39. As a result, radiated sound can be reduced more than when the lid member 330 is fixed to the fixed core 39.

The high-pressure fuel supply pump 100 (fuel supply pump) includes a body 1 having a pressurizing chamber 11, and a plunger 2 that is supported by the body 1 so as to be able to reciprocate and increase or decrease the capacity of the pressurizing chamber 11 through the reciprocating movement. Equipped with Further, the high-pressure fuel supply pump 100 includes the above-described electromagnetic intake valve mechanism 3 (electromagnetic valve mechanism) that discharges fuel into the pressurizing chamber 11.
Thereby, vibration of the lid member 330 can be suppressed when the electromagnetic suction valve mechanism 3 is operated. As a result, the radiated sound generated due to the vibration of the lid member 330 can be reduced. Furthermore, the air gap in the magnetic path of the electromagnetic suction valve mechanism 3 can be minimized, and the magnetic efficiency of the electromagnetic suction valve mechanism 3 can be improved.

The present invention is not limited to the embodiments described above and shown in the drawings, and various modifications can be made without departing from the gist of the invention as set forth in the claims.

Furthermore, the embodiments described above are described in detail to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the configurations described. Furthermore, it is possible to replace a part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment. Furthermore, it is possible to add, delete, or replace some of the configurations of each embodiment with other configurations.

1... Body, 1a... Suction passage, 1b... Flange, 1c... Fixed part, 1d... Discharge valve chamber, 1f... Discharge passage, 2... Plunger, 3, 3A... Electromagnetic suction valve mechanism, 4... Relief valve mechanism, 5... Suction joint, 6... Cylinder, 8... Discharge valve mechanism, 9... Pressure pulsation reduction mechanism, 10... Low pressure fuel chamber, 11... Pressurizing chamber, 12... Discharge joint, 14... Damper cover, 15... Retainer, 17... Seal holder , 17a... subchamber, 18... plunger seal, 30... terminal member, 30a... connector, 31... suction valve seat, 31a... seating section, 31b... suction port, 31c... rod guide, 32... suction valve, 32S... valve opening Stroke, 33... Rod, 33a... Rod flange, 35... Electromagnetic coil, 36... Anchor, 37... Stopper, 39... Fixed core, 42... Relief valve holder, 43... Relief valve, 44... Seat member, 51... Low pressure fuel Suction port, 52... Suction channel, 81... Discharge valve seat member, 82... Discharge valve, 83... Discharge valve spring, 84... Discharge valve stopper, 85... Plug, 90... Fuel pump mounting part, 91... Cam, 92... Tappet, 93...O-ring, 100...High pressure fuel supply pump, 101...ECU, 102...Feed pump, 103...Fuel tank, 104...Low pressure piping, 105...Fuel pressure sensor, 106...Common rail, 107...Injector, 310...Anchor Guide, 320... Yoke, 321... Cylindrical part, 322... Fitting part, 330... Lid member, 331... Inner peripheral part, 332... Outer peripheral part, 332a... Arc part, 332b... Straight part, 340... Sealing, 350... Welding Department

Claims

An electromagnetic valve mechanism comprising a valve part that opens and closes a fuel introduction opening, and a solenoid that moves the valve part in an opening and closing direction,
The solenoid is
an electromagnetic coil,
a stator disposed radially inside the electromagnetic coil;
a movable element that engages with the valve portion and generates a magnetic attraction force between it and the stator;
a yoke formed in a cylindrical shape that surrounds the electromagnetic coil, and from which the stator protrudes from one opening;
a lid member that closes the opening of the yoke;
The lid member is formed in a substantially annular shape having an inner circumferential portion and an outer circumferential portion,
an inner peripheral portion of the lid member contacts the stator;
An outer circumferential portion of the lid member is fixed to an inner circumferential portion of the yoke.
The electromagnetic valve mechanism according to claim 1, wherein the lid member is press-fitted and fixed to the yoke.
The electromagnetic valve mechanism according to claim 1, wherein the lid member is welded and fixed to the yoke.
The electromagnetic valve mechanism according to claim 1, wherein the lid member is caulked and fixed to the yoke.
The electromagnetic valve mechanism according to claim 1, wherein the lid member is adhesively fixed to the yoke.
The outer peripheral portion of the lid member has an arcuate arc portion and a straight portion continuous to both ends of the arcuate portion,
The electromagnetic valve mechanism according to claim 1, wherein the arc portion is fixed to the yoke.
The electromagnetic valve mechanism according to claim 1, wherein an inner peripheral portion of the lid member is fixed to the stator.
A body equipped with a pressurized chamber,
a plunger that is reciprocatably supported by the body and increases or decreases the capacity of the pressurizing chamber by reciprocating;
A fuel supply pump comprising: a solenoid valve mechanism that discharges fuel into the pressurizing chamber;
The solenoid valve mechanism is
A valve part that opens and closes a fuel introduction opening, and a solenoid that drives the valve part,
The solenoid is
an electromagnetic coil,
a stator disposed radially inside the electromagnetic coil;
a movable element that engages with the valve portion and generates a magnetic attraction force between it and the stator;
a yoke formed in a cylindrical shape that surrounds the electromagnetic coil, and from which the stator protrudes from one opening;
a lid member that closes the opening of the yoke;
The lid member is formed in a substantially annular shape having an inner circumferential portion and an outer circumferential portion,
an inner peripheral portion of the lid member contacts the stator;
An outer circumferential portion of the lid member is fixed to an inner circumferential portion of the yoke.