WO2023058287A1 - Electromagnetic intake valve mechanism and fuel pump - Google Patents

Abstract

The present invention provides an electromagnetic intake valve mechanism and a fuel pump that can reduce the force of fuel pushing a valve body in the valve closing direction. The electromagnetic intake valve mechanism comprises a valve body, a valve seat on which the valve body is seated, and a stopper that restricts the movement of the valve body in the valve opening direction. The valve body has a first surface (seating surface) in contact with the valve seat and an outer peripheral surface substantially perpendicular to the first surface. The stopper has a press-fitting part for fixing that is formed in a cylindrical shape and has an inner peripheral surface facing the outer peripheral surface of the valve body and an outer peripheral surface opposite to the inner peripheral surface, and a plurality of communication grooves formed in the outer peripheral surface of the press-fitting part. A portion (end face side) of the press-fitting part is located closer to the valve seat than the first surface of the valve body when the valve is open.

Description

Electromagnetic suction valve mechanism and fuel pump

The present invention relates to an electromagnetic intake valve mechanism and a fuel pump equipped with the electromagnetic intake valve mechanism.

In recent years, the global expansion of internal combustion engines has progressed along with the trend toward higher output and lower emissions. In a fuel pump (high-pressure fuel supply pump) that supplies fuel to a direct injection engine, it is important to manufacture the fuel pump with a simple structure at low cost. Fuel pumps that are widely used in the market today include piston pumps equipped with electromagnetic intake valves. Some electromagnetic intake valves are composed of an intake valve that passively opens and closes with respect to fluid movement, and an electromagnetic actuator that engages with the intake valve to regulate the operation of the intake valve.

For example, in the pump described in Patent Document 1, a spring pushes the valve body toward the valve opening side when the electromagnetic intake valve is open. At that time, the valve body is also pushed to the valve opening side by the fluid force of the fuel flowing in from the upstream side of the fuel passage. On the other hand, when the electromagnetic suction valve closes, the magnetic attraction force generated by the magnetic circuit causes the mover to move the valve body in the valve closing direction. Further, the electromagnetic suction valve is provided with a spring that pushes the valve body in the valve closing direction. When the electromagnetic suction valve closes, the valve body is also pushed in the valve closing direction by the fluid force of the fuel flowing back from the pressurizing chamber side.

JP 2014-114722 A

However, as in the pump described in Patent Document 1, if the valve element moves in the valve closing direction without control by the magnetic circuit due to the fluid force of the fuel flowing back from the pressurizing chamber side, the fuel will not be discharged. The discharge flow rate cannot be set to 0 during cutting.

An object of the present invention is to provide an electromagnetic intake valve mechanism and a fuel pump that can reduce the force of fuel pushing the valve body in the valve closing direction, in consideration of the above problems.

In order to solve the above problems and achieve the object of the present invention, the electromagnetic suction valve mechanism of the present invention comprises a valve body, a valve seat on which the valve body is seated, and a stopper that restricts the movement of the valve body in the valve opening direction. and The valve body has a seating surface in contact with the valve seat and an outer peripheral surface substantially orthogonal to the seating surface. The stopper is formed in a cylindrical shape and has an inner peripheral surface facing the outer peripheral surface of the valve body and an outer peripheral surface opposite to the inner peripheral surface. and a plurality of communication grooves serving as fuel passages. A portion of the press-fitting portion is positioned closer to the valve seat than the seating surface of the valve disc when the valve disc is in the valve-open state where movement in the valve-opening direction is restricted by the stopper.

Further, the fuel pump of the present invention comprises a body having a pressurizing chamber, a plunger supported by the body so as to be able to reciprocate and increasing or decreasing the capacity of the pressurizing chamber by reciprocating motion, and the plunger for discharging fuel into the pressurizing chamber. and an intake valve mechanism.

According to the intake valve mechanism configured as described above, it is possible to reduce the force of the fuel pushing the valve body in the valve closing direction.
Problems, configurations, and effects other than those described above will be clarified by the following description of the embodiments.

1 is an overall configuration diagram of a fuel supply system using a high-pressure fuel supply pump according to a first embodiment of the present invention; FIG. 1 is a longitudinal sectional view of a high-pressure fuel supply pump according to a first embodiment of the invention; FIG. FIG. 3 is a cross-sectional view taken along line AA shown in FIG. 2; FIG. 4 is a cross-sectional view showing an enlarged valve open state of the electromagnetic intake valve mechanism according to the first embodiment of the present invention; 5 is a cross-sectional view obtained by rotating the cross-sectional view shown in FIG. 4 by 45° about the central axis of the rod; FIG. FIG. 3 is an enlarged cross-sectional view showing a closed state of the electromagnetic suction valve mechanism according to the first embodiment of the present invention; 7 is a cross-sectional view obtained by rotating the cross-sectional view shown in FIG. 6 by 45° around the central axis of the rod; FIG. FIG. 4 is a perspective view of a stopper of the electromagnetic intake valve mechanism according to the first embodiment of the present invention; FIG. 4 is a front view of a stopper of the electromagnetic intake valve mechanism according to the first embodiment of the present invention; FIG. 5 is a cross-sectional view showing a second example of the stopper of the electromagnetic suction valve mechanism according to the first embodiment of the present invention; FIG. 7 is a cross-sectional view showing a third example of the stopper of the electromagnetic intake valve mechanism according to the first embodiment of the invention; FIG. 4 is an explanatory diagram showing the flow of fuel in the valve open state of the electromagnetic intake valve mechanism according to the first embodiment of the present invention; FIG. 8 is a perspective view of a stopper of the electromagnetic suction valve mechanism according to the second embodiment of the invention; FIG. 8 is a front view of a stopper of an electromagnetic intake valve mechanism according to a second embodiment of the invention; FIG. 10 is a perspective view of a stopper of an electromagnetic suction valve mechanism according to a third embodiment of the invention; FIG. 11 is a front view of a stopper of an electromagnetic intake valve mechanism according to a third embodiment of the invention; FIG. 11 is a cross-sectional view showing an enlarged open state of an electromagnetic intake valve mechanism according to a fourth embodiment of the present invention;

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

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

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

The fuel in the fuel tank 103 is pumped up by a feed pump 102 driven based on a signal from the ECU 101. The pumped fuel is pressurized to an appropriate pressure by a pressure regulator (not shown) and sent to the low-pressure fuel suction port 81 of the high-pressure fuel supply pump 100 through the low-pressure pipe 104 .

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

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

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

The high-pressure fuel supply pump 100 has a pressure pulsation reduction mechanism 9, an electromagnetic intake valve mechanism 3 that is a variable displacement mechanism, a discharge valve mechanism 5, and a relief valve mechanism 6 (see FIG. 2). The fuel flowing from the low-pressure fuel intake port 81 reaches the intake port 31b of the electromagnetic intake valve mechanism 3 via the pressure pulsation reducing mechanism 9 and the intake passage 10b.

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

In the pressurization chamber 11, fuel is sucked from the electromagnetic intake valve mechanism 3 during the downward stroke of the plunger 2, and is pressurized during the upward stroke. When the fuel pressure in the pressurization chamber 11 exceeds a predetermined value, the discharge valve mechanism 5 is opened, and high pressure fuel is pressure-fed to the common rail 106 through the fuel discharge port 12a. The discharge of fuel by the high-pressure fuel supply pump 100 is operated by opening and closing the electromagnetic intake valve mechanism 3 . The opening and closing of the electromagnetic intake valve mechanism 3 is controlled by the ECU 101 .

[High pressure fuel supply pump]
Next, the configuration of the high-pressure fuel supply pump 100 will be described with reference to FIGS. 2 and 3. FIG. FIG. 2 is a vertical cross-sectional view of the high-pressure fuel supply pump 100 seen in a cross section perpendicular to the horizontal direction. 3 is a cross-sectional view taken along line AA shown in FIG. 2. FIG.

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

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

A cylinder 4 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 4 is formed in a cylindrical shape and is press-fitted into the body 1 at its outer peripheral side. The body 1 and the cylinder 4 form a pressure chamber 11 together with the electromagnetic suction valve mechanism 3, the plunger 2, and the discharge valve mechanism 5 (see FIG. 3).

The body 1 is provided with a fixing portion 1c that engages with the central portion of the cylinder 4 in the axial direction. The fixed portion 1c of the body 1 is plastically deformed by applying a load from below (lower side in FIG. 2), and presses the cylinder 4 upward. Thereby, the cylinder 4 is press-fitted into the body 1 . As a result, the fuel pressurized in the pressurization chamber 11 can be prevented from leaking from between the cylinder 4 and the body 1 .

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

A seal holder 17 is arranged between the cylinder 4 and the retainer 15 . The seal holder 17 is formed in a cylindrical shape into which the plunger 2 is inserted, and has an auxiliary chamber 17a at its upper end on the cylinder 4 side. In addition, the seal holder 17 holds a plunger seal 18 at the lower end on the retainer 15 side.

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

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

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

The sub-chamber 17a communicates with the low-pressure fuel chamber 10 through a fuel passage 10c (see FIG. 3). When the plunger 2 moves downward, fuel flows from the auxiliary chamber 17a to the low-pressure fuel chamber 10. When the plunger 2 moves upward, fuel flows from the low-pressure fuel chamber 10 to the auxiliary chamber 17a. As a result, the flow rate of fuel into and out of the high-pressure fuel supply pump 100 during the intake stroke or return stroke of the high-pressure fuel supply pump 100 can be reduced, and the pressure pulsation generated inside the high-pressure fuel supply pump 100 can be reduced.

As shown in FIG. 3, a suction joint 8 is attached to the side surface of the body 1. The suction joint 8 is connected to a low-pressure pipe 104 (see FIG. 1) through which fuel supplied from a fuel tank 103 passes. Fuel in the fuel tank 103 is supplied from the intake joint 8 to the inside of the high-pressure fuel supply pump 100 .

The suction joint 8 has a low-pressure fuel suction port 81 connected to the low-pressure pipe 104 and a suction passage 82 communicating with the low-pressure fuel suction port 81 . Fuel passing through the intake passage 82 reaches the intake port 31b (see FIG. 2) of the electromagnetic intake valve mechanism 3 via the pressure pulsation reduction mechanism 9 and the intake passage 10b (see FIG. 2) provided in the low-pressure fuel chamber 10. do. A suction filter 83 is arranged in the fuel passage communicating with the suction passage 82 . The suction filter 83 removes foreign matter present in the fuel and prevents foreign matter from entering the high-pressure fuel supply pump 100 .

As shown in FIG. 2, the body 1 of the high-pressure fuel supply pump 100 is provided with a low-pressure fuel chamber (damper chamber) 10 . This low-pressure fuel chamber 10 is covered with a damper cover 14 . The damper cover 14 is formed, for example, in a tubular (cup-like) shape with one side closed.

The low-pressure fuel chamber 10 has a low-pressure fuel flow path 10a and an intake passage 10b. The intake passage 10 b communicates with the intake port 31 b of the electromagnetic intake valve mechanism 3 . The fuel that has passed through the low-pressure fuel passage 10a reaches the intake port 31b of the electromagnetic intake valve mechanism 3 via the intake passage 10b.

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

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

As shown in FIG. 3 , the body 1 is provided with a discharge valve mechanism 5 that communicates with the pressurization chamber 11 . The discharge valve mechanism 5 includes a discharge valve seat 51, a valve body 52 that can be seated and separated from the discharge valve seat 51, a discharge valve spring 53 that biases the valve body 52 toward the discharge valve seat 51, and a discharge valve guide 54 that slides and guides the valve body 52 .

The discharge valve seat 51, the valve body 52, the discharge valve spring 53, and the discharge valve guide 54 are housed in a discharge valve chamber 1d formed in the body 1. The discharge valve chamber 1d is a substantially cylindrical space extending in the horizontal direction. One end of the discharge valve chamber 1d communicates with the pressure chamber 11 via the fuel passage 1e. The other end of the discharge valve chamber 1 d is open to the side surface of the body 1 . A plug 55 seals the opening of the other end of the discharge valve chamber 1d. The plug 55 and the body 1 are joined by welding, for example.

A discharge joint 12 is also welded to the body 1 . 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 extending horizontally inside the body 1. As shown in FIG. A fuel discharge port 12a of the discharge joint 12 is connected to a common rail 106 (see FIG. 1).

When there is no difference in fuel pressure between the pressure chamber 11 and the discharge valve chamber 1d, the valve body 52 is pressed against the discharge valve seat 51 by the biasing force of the discharge valve spring 53. As a result, the discharge valve mechanism 5 is closed. When the fuel pressure in the pressure chamber 11 becomes higher than the fuel pressure in the discharge valve chamber 1d, the valve element 52 moves against the biasing force of the discharge valve spring 53 and leaves the discharge valve seat 51. As a result, the discharge valve mechanism 5 is opened.

When the discharge valve mechanism 5 is opened, the high-pressure fuel in the pressure 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. When the discharge valve mechanism 5 is open, the valve body 52 contacts the discharge valve guide 54 and the stroke of the valve body 52 is restricted.

The stroke of the valve body 52 is appropriately determined by the discharge valve guide 54. As a result, delay in closing of the discharge valve mechanism 5 due to the long stroke of the valve element 52 can be prevented. As a result, the fuel discharged into the discharge valve chamber 1d can be prevented from flowing back into the pressurizing chamber 11 again, and a decrease in the efficiency of the high-pressure fuel supply pump 100 can be suppressed. In this manner, the discharge valve mechanism 5 functions as a check valve that restricts the flow direction of fuel.

Also, the body 1 is provided with a relief valve mechanism 6 communicating with the pressurization chamber 11 . The relief valve mechanism 6 has a relief valve seat 61 , a relief valve 62 that contacts and separates from the relief valve seat 61 , and a relief valve holder 63 that holds the relief valve 62 . The relief valve mechanism 6 also has a relief spring 64 that biases the relief valve 62 toward the relief valve seat 61 and a relief valve housing 65 .

The relief valve housing 65 is fitted into a relief valve chamber 1g formed in the body 1. The relief valve chamber 1g is a substantially cylindrical space extending in the horizontal direction. One end of the relief valve chamber 1g communicates with the pressure chamber 11 via the fuel passage 1h. The discharge joint 12 described above is joined to the other end of the relief valve chamber 1g.

The relief valve housing 65 contains the relief spring 64, the relief valve holder 63, the relief valve 62, and the relief valve seat 61. In the relief valve housing 65, the relief spring 64, the relief valve holder 63, and the relief valve 62 are inserted in this order. After that, the relief valve seat 61 is press-fitted and fixed to the relief valve housing 65 .

The relief spring 64 has one end in contact with the relief valve housing 65 and the other end in contact with the relief valve holder 63 . The relief valve holder 63 is engaged with the relief valve 62 . The biasing force of the relief spring 64 acts on the relief valve 62 via the relief valve holder 63 .

The relief valve 62 is pressed by the biasing force of the relief spring 64 and closes the fuel passage of the relief valve seat 61 . A fuel passage of the relief valve seat 61 communicates with the discharge passage 1f. The movement of fuel between the pressure chamber 11 (upstream side) and the relief valve seat 61 (downstream side) is blocked by the relief valve 62 contacting (adhering to) the relief valve seat 61 .

When the pressure in the common rail 106 and the members beyond it rises, the fuel on the side of the fuel discharge port 12a presses the relief valve 62 and moves the relief valve 62 against the urging force of the relief spring 64. As a result, the relief valve 62 is opened, and the fuel in the discharge passage 1f returns to the pressurization chamber 11 through the fuel passage of the relief valve seat 61. Therefore, the pressure for opening the relief valve 62 is determined by the biasing force of the relief spring 64 .

Although the relief valve mechanism 6 of the present embodiment communicates with the pressurizing chamber 11, it is not limited to this, and communicates with, for example, a low-pressure passage (low-pressure fuel suction port 81, suction passage 10b, etc.). You may make it

[Electromagnetic suction valve mechanism]
As shown in FIGS. 2 and 3, the electromagnetic suction valve mechanism 3 is inserted into a lateral hole 1i formed in the body 1. As shown in FIG. The electromagnetic suction valve mechanism 3 has a suction valve housing 31 press-fitted into the lateral hole 1i, a valve body 32, a rod 33, a rod biasing spring 34, an electromagnetic coil 35, and an anchor . The electromagnetic suction valve mechanism 3 is roughly divided into a suction valve mechanism portion including the valve body 32 and a solenoid mechanism portion including the electromagnetic coil 35 , the anchor 36 and the rod 33 .

The intake valve housing 31 is formed in a cylindrical shape, and has a valve seat 31a on its inner periphery. Further, the intake valve housing 31 is formed with an intake port 31b reaching from the outer peripheral portion to the inner peripheral portion. The intake port 31b communicates with the intake passage 10b in the low-pressure fuel chamber 10 described above. The intake valve housing 31 also has a rod guide 31c through which the rod 33 passes.

A stopper 37 facing the valve seat 31a of the intake valve housing 31 is arranged in the lateral hole 1i formed in the body 1. The valve body 32 is arranged between the stopper 37 and the valve seat 31a. A valve biasing spring 38 is interposed between the stopper 37 and the valve body 32 . A valve biasing spring 38 biases the valve body 32 toward the valve seat 31a.

The valve body 32 closes the communicating portion between the suction port 31b and the pressurizing chamber 11 by abutting (seating) on the valve seat 31a. When the valve body 32 closes the communicating portion between the suction port 31b and the pressurizing chamber 11, the electromagnetic suction valve mechanism 3 is closed. The valve body 32 opens the communicating portion between the intake port 31 b and the pressurizing chamber 11 by abutting against the stopper 37 . When the valve body 32 opens the communicating portion between the suction port 31b and the pressurizing chamber 11, the electromagnetic suction valve mechanism 3 is opened.

The rod 33 passes through the rod guide 31c of the intake valve housing 31 and the anchor 36. A rod collar portion 33a is formed on the rod 33 . One end of a rod biasing spring 34 is engaged with the rod collar portion 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 valve body 32 in the valve opening direction, which is the stopper 37 side, via the rod 33 .

The anchor 36 is formed in a substantially cylindrical shape. One end of an anchor biasing spring 40 abuts against one axial end of the anchor 36 . The other axial end of the anchor 36 faces the end face of the fixed core 39 . A flange contact portion is formed at the other axial end of the anchor 36 with which the rod collar portion 33a of the rod 33 contacts.

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 collar portion 33 a of the rod 33 . The movable distance of the anchor 36 is set longer than the movable distance of the valve body 32 . As a result, the valve body 32 can be reliably brought into contact (seated) on the valve seat 31a, and the electromagnetic intake valve mechanism 3 can be reliably closed.

The electromagnetic coil 35 is arranged so as to go around the fixed core 39 . 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 . In a non-energized state in which 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 valve body 32 in the valve opening direction. As a result, the valve body 32 separates from the valve seat 31a and comes into contact with the stopper 37, and the electromagnetic suction valve mechanism 3 is opened. That is, the electromagnetic intake valve mechanism 3 is of a normally open type that opens when no power is supplied.

When the electromagnetic intake valve mechanism 3 is open, the fuel in the intake port 31b passes between the valve body 32 and the valve seat 31a, through the plurality of communication grooves 377c (see FIG. 6) of the stopper 37, and the intake passage 1a. and flows into the pressurization chamber 11. When the electromagnetic suction valve mechanism 3 is in the open state, the valve body 32 contacts the stopper 37, so the position of the valve body 32 in the valve opening direction is restricted. In the open state of the electromagnetic intake valve mechanism 3, the gap between the valve body 32 and the valve seat 31a is the movable range of the valve body 32, which is the valve opening stroke.

When a current flows through the electromagnetic coil 35, a magnetic attraction force is generated on each magnetic attraction surface (facing surface) of the anchor 36 and the fixed core 39. The electromagnetic coil 35, the anchor 36, and the fixed core 39 constitute the magnetic attraction force generator according to the present invention. The anchor 36 is attracted to the fixed core 39 when a magnetic attraction force is generated on the magnetic attraction surface. As a result, the anchor 36 moves against the biasing force of the rod biasing spring 34 and contacts the fixed core 39 .

When the anchor 36 moves in the valve closing direction on the side of the fixed core 39 , the rod 33 with which the anchor 36 engages moves together with the anchor 36 . As a result, the valve body 32 is released from the biasing force in the valve opening direction, and moves in the valve closing direction due to the biasing force of the valve biasing spring 38 . When the valve body 32 contacts the valve seat 31a of the intake valve housing 31, the electromagnetic intake valve mechanism 3 is closed.

[Operation of high-pressure fuel supply pump]
Next, the operation of the high-pressure fuel supply pump according to this embodiment will be described.
When the cam 91 shown in FIG. 2 rotates and the plunger 2 descends, if the electromagnetic intake valve mechanism 3 is open, fuel flows into the pressurization chamber 11 from the intake passage 1a. Hereinafter, the stroke in which the plunger 2 descends will be referred to as a suction stroke. On the other hand, if the electromagnetic intake valve mechanism 3 is closed when the plunger 2 rises, the pressure of the fuel in the pressurization chamber 11 is increased, and the fuel in the pressure chamber 11 passes through the discharge valve mechanism 5 (see FIG. 3) to reach the common rail 106 (see FIG. 3). 1). Hereinafter, the process in which the plunger 2 rises will be referred to as a compression stroke.

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

In the intake stroke, the volume of the pressurization chamber 11 increases and the fuel pressure in the pressurization chamber 11 decreases. In this intake stroke, the fuel pressure in the pressure chamber 11 becomes lower than the pressure in the intake port 31b, and when the biasing force due to the pressure difference between the two exceeds the biasing force of the valve biasing spring 38, the valve body 32 moves toward the valve seat 31a. , and the electromagnetic suction valve mechanism 3 is opened. As a result, the fuel flows between the valve body 32 and the valve seat 31a and into the pressure chamber 11 through a plurality of communication grooves 377c (see FIG. 6) provided in the stopper 37. As shown in FIG.

After completing the intake stroke, the plunger 2 turns to upward movement and shifts to the compression stroke. At this time, the electromagnetic coil 35 remains in a non-energized state, and no magnetic attraction force acts between the anchor 36 and the fixed core 39 . The rod biasing spring 34 is set to have a necessary and sufficient biasing force to maintain the valve body 32 at the valve open position away from the valve seat 31a in the non-energized state.

In this state, even if the plunger 2 moves upward, the rod 33 stays at the valve open position, so the valve body 32 urged by the rod 33 also stays at the valve open position. Therefore, the volume of the pressurization chamber 11 decreases as the plunger 2 moves upward, but in this state, the fuel once flowing into the pressurization chamber 11 flows through the electromagnetic intake valve mechanism 3 in the open state again to the intake passage. 10b, the pressure in the pressurizing chamber 11 does not rise. 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, current flows through the electromagnetic coil 35 via the terminal member 30. When an electric current flows through the electromagnetic coil 35 , a magnetic attraction force acts on the magnetic attraction surfaces of the fixed core 39 and the anchor 36 , and the anchor 36 is attracted to the fixed core 39 . 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 against the biasing force of the rod biasing spring 34 , and the rod engages with the anchor 36 . 33 moves away from the valve body 32 . As a result, the valve body 32 is seated on the valve seat 31a by the biasing force of the valve biasing spring 38 and the fluid force due to the fuel flowing into the intake passage 10b, and the electromagnetic intake valve mechanism 3 is closed.

After the electromagnetic intake valve mechanism 3 is closed, the pressure of the fuel in the pressure chamber 11 increases as the plunger 2 rises. It passes through and is discharged to common rail 106 (see FIG. 1). This stroke is called a discharge stroke. That is, the compression stroke from the bottom dead center to the top dead center of the plunger 2 consists of a return stroke and a discharge stroke. By controlling the timing of energization of the electromagnetic coil 35 of the electromagnetic intake valve mechanism 3, the amount of fuel to be discharged can be controlled.

If the timing of energizing the electromagnetic coil 35 is advanced, the proportion of the return stroke in the compression stroke becomes smaller and the proportion of the discharge stroke becomes larger. As a result, less fuel is returned to the intake passage 10b, and more fuel is discharged at high pressure. On the other hand, if the timing of energizing the electromagnetic coil 35 is delayed, the ratio of the return stroke in the compression stroke increases and the ratio of the discharge stroke decreases. As a result, more fuel is returned to the intake passage 10b, and less fuel is discharged at high pressure. By controlling the timing of energization of the electromagnetic coil 35 in this way, the amount of fuel discharged at high pressure can be controlled to the amount required by the engine (internal combustion engine).

[Construction of valve body, valve seat and stopper]
Next, configurations of the valve body 32, the valve seat 31a and the stopper 37 will be described with reference to FIGS. 4 to 9. FIG.
FIG. 4 is an enlarged cross-sectional view showing the open state of the electromagnetic intake valve mechanism 3. As shown in FIG. FIG. 5 is a cross-sectional view obtained by rotating the cross-sectional view shown in FIG. 4 by 45° about the central axis of the rod. FIG. 6 is a cross-sectional view showing an enlarged closed state of the electromagnetic suction valve mechanism 3. As shown in FIG. FIG. 7 is a cross-sectional view obtained by rotating the cross-sectional view shown in FIG. 6 by 45° about the central axis of the rod. 8 is a perspective view of the stopper 37. FIG. 9 is a front view of the stopper 37. FIG.

As shown in FIGS. 4 to 7, the valve body 32 has a valve portion 321 and a fitting projection 322 projecting from the valve portion 321. As shown in FIGS. The valve portion 321 is formed in a disc shape having an appropriate thickness. The valve portion 321 has a first surface 321 a facing the valve seat 31 a and a second surface 321 b facing the stopper 37 . The first surface 321a corresponds to the valve upstream end surface according to the present invention.

The fitting protrusion 322 protrudes substantially perpendicularly from the second surface 321b of the valve portion 321 . The fitting protrusion 322 is formed in a cylindrical shape having a cylindrical hole 322a. The fitting protrusion 322 is slidably fitted into a guide hole 375 of the stopper 37, which will be described later. One end of the valve biasing spring 38 abuts on the bottom surface of the cylindrical hole 322 a of the fitting protrusion 322 .

The fitting protrusion 322 is provided with a through hole 322b penetrating from the outer peripheral surface to the inner peripheral surface. The through hole 322b serves as a breather passage through which the fuel in the cylindrical hole 322a of the fitting protrusion 322 flows to the outside of the fitting protrusion 322. As shown in FIG. An end face 322c, which is one axial end of the fitting protrusion 322, is chamfered.

The valve seat 31 a of the intake valve housing 31 has a seat portion 311 against which the first surface 321 a of the valve body 32 abuts, and a seat outer peripheral portion 312 forming the periphery of the seat portion 311 . The seat portion 311 is formed as an annular projecting portion projecting toward the valve body 32 from the seat outer peripheral portion 312 . That is, the seat outer peripheral portion 312 has a shape recessed with respect to the seat portion 311 . Also, the seat portion 311 has an inclined surface 311 a that is continuous with the seat outer peripheral portion 312 .

The stopper 37 is fixed to the intake valve housing 31. As shown in FIGS. 8 and 9, the stopper 37 is formed in a substantially cylindrical shape with a bottom. The stopper 37 has a plurality of inner peripheral surfaces with different diameters.

The stopper 37 has a spring bearing surface 372 , a stopper surface 373 and a facing surface 374 . The spring seat surface 372 forms the bottom surface of a hole that forms the inner peripheral surface of the stopper 37 with the smallest diameter. The other end of the valve biasing spring 38 contacts the spring seat surface 372 . A stopper convex portion 37a is formed on the outer side of the spring seat surface 372 .

The stopper surface 373 forms the bottom surface of a guide hole 375 having a diameter larger than that of the spring bearing surface 372 . The end face 322c of the valve body 32 in the valve open state contacts the stopper face 373 . The fitting protrusion 322 of the valve body 32 is slidably fitted to the inner peripheral surface of the guide hole 375 . An appropriate gap is provided between the inner peripheral surface of the guide hole 375 and the fitting protrusion 322 . In addition, the axial length of the inner peripheral surface of the guide hole 375 is set to an appropriate sliding length of the fitting protrusion 322 . As a result, eccentricity and inclination of the valve body 32 can be suppressed.

The facing surface 374 forms the bottom surface of a hole forming an inner peripheral surface 377b of the stopper 37 having the largest diameter. A valve portion 321 of the valve body 32 is inserted into the hole forming the inner peripheral surface 377 b of the stopper 37 . An appropriate gap is formed between the inner peripheral surface 377b of the stopper 37 and the outer peripheral surface of the valve portion 321 (see FIGS. 4 to 7). The second surface 321 b of the valve portion 321 faces the facing surface 374 .

Also, the stopper 37 has a press-fit portion 377 . The press-fit portion 377 forms the outermost diameter portion of the stopper 37 . The press-fit portion 377 is formed in a tubular shape having an inner peripheral surface 377b. Also, the press-fit portion 377 has an end surface 377a substantially parallel to the facing surface 374 . As shown in FIGS. 4 and 5, when the electromagnetic intake valve mechanism 3 is open, the end surface 377a of the press-fit portion 377 is located closer to the valve seat 31a than the first surface 321a of the valve body 32 is.

The press-fit portion 377 is press-fit into the intake valve housing 31 . The stopper 37 is fixed to the intake valve housing 31 by press-fitting the press-fit portion 377 into the intake valve housing 31 . A plurality of communication grooves 377c are provided on the outer peripheral surface of the press-fit portion 377 . As shown in FIGS. 5 and 7, the communication groove 377c forms a communication path between the intake valve housing 31 and the stopper 37 through which fuel passes. The communication path serves as a flow path that connects the suction port 31 b and the pressurization chamber 11 .

As shown in FIGS. 8 and 9, the plurality of communication grooves 377c are arranged at equal intervals in the circumferential direction of the press-fit portion 377. As shown in FIG. As a result, variations in pressure and turbulence in the flow of fuel that occur near the end face 377a of the press-fit portion 377 can be reduced. Furthermore, the stress generated by pressing the stopper 37 into the intake valve housing 31 can be dispersed.

The communication groove 377c has a curved surface that forms a concentric circle with the inner peripheral surface 377b and a curved surface that forms two tangential circles that are continuous with this concentric circle. Such a communication groove 377c does not need to be formed with sharp corners, and thus can be easily processed. Also, the thickness between the communication groove 377c and the inner peripheral surface 377b can be made uniform. As a result, it is possible to suppress the formation of a low-rigidity portion by providing the communication groove 377c.

In this embodiment, four communication grooves 377c are provided. However, the number of communicating grooves of the stopper according to the present invention may be five or more, or may be three or less. In general, machining an axially symmetrical part in the vertical direction increases the number of machining steps, but it is possible to reduce the number of machining steps by reducing the number of grooves. Also, by providing the communicating groove 377c, it is possible to facilitate gripping the stopper 37 with a tool or the like during processing.

An inner peripheral surface 377b of the press-fit portion 377 faces the outer peripheral surface of the valve portion 321 with a gap therebetween. Thus, the press-fitting portion 377 also serves as a shielding portion that shields the fuel flowing from the pressurizing chamber 11 side into the plurality of communication grooves 377 c from traveling toward the outer peripheral surface of the valve portion 321 . As a result, the shape of the stopper can be made simpler than when the shielding portion is provided separately from the press-fitting portion 377, and the number of man-hours for processing the stopper can be reduced.

The size of the gap between the inner peripheral surface 377b and the outer peripheral surface of the valve portion 321 is uniform over the entire circumference. If the size of this gap is not constant over the entire circumference, the flow of backflow fuel that flows back from the pressure chamber 11 to the side of the electromagnetic intake valve mechanism 3 becomes uneven. As a result, the fuel pressure varies near the end surface 377 a of the press-fit portion 377 . On the other hand, in the present embodiment, variations in fuel pressure in the gap between the inner peripheral surface 377b and the outer peripheral surface of the valve portion 321 can be reduced. Thereby, the operation of the valve body 32 can be stabilized.

Also, the channel cross-sectional area of the gap generated between the press-fitting portion 377 and the valve portion 321 is set to be equal to or larger than the channel cross-sectional area of the through hole 322 b in the valve body 32 . This prevents the fuel returning from the intake passage 1a (see FIG. 2) from interfering with the operation of the valve body 32. As shown in FIG.

[Other examples of stoppers]
Next, another example of the stopper will be described with reference to FIGS. 10 and 11. FIG.
FIG. 10 is a cross-sectional view showing a second example of the stopper. FIG. 11 is a cross-sectional view showing a third example of the stopper.

A stopper 37A shown in FIG. 10 is a second example of the stopper. The stopper 37A has the same configuration as the stopper 37 shown in FIG. The difference between the stopper 37A and the stopper 37 is the facing surface 374A. Therefore, here, the facing surface 374A will be described, and the description of the configuration common to the stopper 37 will be omitted.

The stopper 37A has a spring bearing surface 372, a stopper surface 373, and a facing surface 374A. The facing surface 374A intersects the inner peripheral surface 377b at an obtuse angle. The opposing surface 374 of the stopper 37 (see FIG. 4) intersects the inner peripheral surface 377b at right angles. As a stopper according to the present invention, the opposing surface may intersect the inner peripheral surface at an acute angle.

A stopper 37B shown in FIG. 11 is a third example of the stopper. The stopper 37B has the same configuration as the stopper 37 shown in FIG. The stopper 37B differs from the stopper 37 in the stopper protrusion 37b. Therefore, here, the stopper convex portion 37b will be described, and the description of the configuration common to the stopper 37 will be omitted.

The stopper 37B has a spring bearing surface 372, a stopper surface 373, and a facing surface 374. A stopper convex portion 37b is formed on the outer side of the spring seat surface 372 . The stopper convex portion 37b has an end face facing the suction passage 1a and an arc-shaped curved surface continuous with the end face. A stopper projection 37a of the stopper 37 (see FIG. 4) has an end surface facing the suction passage 1a and a tapered surface (inclined surface) continuous with the end surface.

When the fuel in the pressurization chamber 11 is pressurized, the fuel flows backward from the pressurization chamber 11 to the side of the electromagnetic intake valve mechanism 3 through the intake passage 1a. This backflow fuel flows toward the stopper protrusions 37a and the stopper protrusions 37b. In this case, since the stopper protrusions 37a and 37b have tapered surfaces (inclined surfaces) and curved surfaces, the backflow fuel smoothly flows along the tapered surfaces (inclined surfaces) and curved surfaces. As a result, the pressure loss of the counterflow fuel can be reduced.

[Fuel flow in valve open state]
Next, the flow of fuel when the electromagnetic intake valve mechanism 3 is open will be described with reference to FIG.
FIG. 12 is an explanatory diagram showing the flow of fuel when the electromagnetic intake valve mechanism 3 is open.

FIG. 12 shows the flow of fuel that flows backward during the return process when the electromagnetic intake valve mechanism 3 is in the open state. As shown in FIG. 12 , the seat outer peripheral portion 312 of the intake valve housing 31 is recessed from the seat portion 311 . A press-fit portion 377 of the stopper 37 faces the seat outer peripheral portion 312 .

In the return process, the fuel 300 flowing back toward the electromagnetic intake valve mechanism 3 (hereinafter referred to as "backflow fuel 300") passes through the communicating groove 377c of the stopper 37. After that, the backflow fuel 300 passes through a curved flow path formed by the press-fit portion 377 of the stopper 37 and the seat outer peripheral portion 312 . At this time, the backflow fuel 300 passes through the end surface 377a of the press-fit portion 377 while increasing the flow velocity because the flow path is narrowed.

At this time, the end surface 377a of the press-fitting portion 377 is located closer to the valve seat 31a than the first surface 321a of the valve body 32 is. Therefore, immediately after the backflow fuel 300 passes through the end surface 377 a , flow separation occurs in part of the backflow fuel 300 in the vicinity of the end surface 377 a of the press-fit portion 377 .

When flow separation occurs in part of the backflow fuel 300, the backflow fuel 300 continues to flow in an apparently narrow flow path, and the flow velocity remains increased. As a result, the fuel pressure between the inclined surface 311a of the valve seat 31a and the first surface 321a of the valve body 32 decreases. The fuel pressure between the inclined surface 311a and the first surface 321a of the valve body 32 and the fuel pressure in the gap between the outer peripheral surface of the valve portion 321 and the inner peripheral surface 377b It becomes the same as the pressure of the fuel that presses the second surface 321b. Therefore, the pressure of the fuel pressing the second surface 321b of the valve body 32 decreases.

When the pressure of the fuel pressing the second surface 321b of the valve body 32 decreases, the force of the fuel pressing the valve body 32 in the valve closing direction decreases. As a result, it is possible to prevent the valve body 32 from moving in the valve closing direction when the control by the magnetic circuit (the electromagnetic coil 35, the anchor 36, etc.) is not performed. can do.

Further, by reducing the force that presses the valve body 32 in the valve closing direction, it is possible to reduce the size of the anchor 36 and the rod urging spring 34, and to reduce the spring force of the rod urging spring 34. . As a result, collision noise between the anchor 36 and the fixed core 39 and collision noise between the valve element 32 and the valve seat 31a can be reduced.

When the electromagnetic suction valve mechanism 3 is open, the end face 377a of the press-fit portion 377 is located closer to the valve seat 31a than the first face 321a of the valve body 32 is. The stopper 37 arranges the press-fit portion 377 and the communication groove 377c, which is the fuel passage, within the same ring. As a result, the shape of the stopper can be made simpler than when the press-fit portion 377 and the fuel passage are arranged separately. As a result, the processing method of the stopper 37 can be diversified.

2. Second Embodiment Next, a stopper of an electromagnetic suction valve mechanism according to a second embodiment of the present invention will be described with reference to FIGS. 13 and 14. FIG.
FIG. 13 is a perspective view of the stopper of the electromagnetic intake valve mechanism according to the second embodiment. FIG. 14 is a front view of the stopper of the electromagnetic intake valve mechanism 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 high-pressure fuel supply pump according to the second embodiment differs from the high-pressure fuel supply pump 100 according to the first embodiment in the stopper 137 . Therefore, here, the stopper 137 will be described, and the description of the configuration common to the high-pressure fuel supply pump 100 will be omitted.

[Structure of stopper]
As shown in FIGS. 13 and 14, the stopper 137 according to the second embodiment has the same configuration as the stopper according to the first embodiment. That is, the stopper 137 is formed in a substantially cylindrical shape with a bottom. The stopper 137 has a spring seat surface 372 , a stopper surface 373 , a facing surface 374 and a guide hole 375 .

Also, the stopper 137 has a press-fitting portion 1377 that is press-fitted into the intake valve housing 31 . The press-fit portion 1377 forms the outermost diameter portion of the stopper 137 . The press-fit portion 1377 is formed in a tubular shape having an inner peripheral surface 1377b. The press-fit portion 1377 also has an end surface 1377 a substantially parallel to the facing surface 374 . When the electromagnetic intake valve mechanism 3 is open, the end surface 1377a of the press-fitting portion 1377 is located closer to the valve seat 31a than the first surface 321a (see FIG. 4) of the valve body 32 is.

A plurality of communication grooves 1377c are provided on the outer peripheral surface of the press-fit portion 1377. The communication groove 1377c forms a communication path between the intake valve housing 31 (see FIG. 5) and the stopper 37 through which fuel passes. The communication path serves as a flow path that connects the suction port 31 b and the pressurization chamber 11 .

The plurality of communication grooves 1377c are arranged at equal intervals in the circumferential direction of the press-fit portion 1377. As a result, it is possible to reduce variations in pressure and turbulence in the flow of fuel that occur in the vicinity of the end surface 1377a of the press-fit portion 1377. FIG. Furthermore, the stress generated by pressing the stopper 137 into the intake valve housing 31 can be dispersed.

The communication groove 1377c is formed in an arc shape when viewed from the direction orthogonal to the end surface 1377a. Such a communication groove 1377c does not need to form a sharp corner, and can be easily processed. The arc shape of the communication groove according to the present invention may be a part of a circle or a part of an ellipse. Further, when the circular arc shape of the communicating groove is a part of an ellipse, the groove depth may be set to the long axis side of the ellipse, or the short axis side of the ellipse may be set to the groove depth.

An inner peripheral surface 1377b of the press-fit portion 1377 faces the outer peripheral surface of the valve portion 321 (see FIG. 4) with a gap therebetween. As a result, the press-fit portion 1377 also serves as a shielding portion that shields the fuel flowing from the pressurizing chamber 11 side into the plurality of communication grooves 1377 c from traveling toward the outer peripheral surface of the valve portion 321 . Further, the channel cross-sectional area of the gap generated between the press-fitting portion 1377 and the valve portion 321 is set to be equal to or larger than the channel cross-sectional area of the through hole 322 b in the valve body 32 .

3. Third Embodiment Next, a stopper of an electromagnetic suction valve mechanism according to a third embodiment of the present invention will be described with reference to FIGS. 15 and 16. FIG.
FIG. 15 is a perspective view of the stopper of the electromagnetic intake valve mechanism according to the third embodiment. FIG. 16 is a front view of the stopper of the electromagnetic intake valve mechanism according to the third embodiment.

[Structure of stopper]
As shown in FIGS. 15 and 16, a stopper 237 according to the third embodiment has the same configuration as the stopper according to the first embodiment. That is, the stopper 237 is formed in a substantially cylindrical shape with a bottom. The stopper 237 has a spring seat surface 372 , a stopper surface 373 , a facing surface 374 and a guide hole 375 .

The stopper 237 also has a press-fit portion 2377 that is press-fitted into the intake valve housing 31 . The press-fit portion 2377 forms the outermost diameter portion of the stopper 237 . The press-fit portion 2377 is formed in a tubular shape having an inner peripheral surface 2377b. Also, the press-fit portion 2377 has an end surface 2377a substantially parallel to the facing surface 374 . When the electromagnetic suction valve mechanism 3 is open, the end surface 2377a of the press-fitting portion 2377 is located closer to the valve seat 31a than the first surface 321a (see FIG. 4) of the valve body 32 is.

A plurality of communication grooves 2377c are provided on the outer peripheral surface of the press-fit portion 2377. The communication groove 2377c forms a communication path through which fuel flows between the intake valve housing 31 (see FIG. 5) and the stopper 237. As shown in FIG. The communication path serves as a flow path that connects the suction port 31 b and the pressurization chamber 11 .

The plurality of communication grooves 2377c are arranged at equal intervals in the circumferential direction of the press-fit portion 2377. As a result, it is possible to reduce variations in pressure and turbulence in the flow of fuel that occur near the end surface 2377a of the press-fit portion 2377 . Furthermore, the stress generated by pressing the stopper 237 into the intake valve housing 31 can be dispersed.

The communication groove 2377c is formed in a substantially rectangular shape with one side open when viewed from the direction perpendicular to the end surface 2377a. Four corners of the communication groove 2377c are formed in a substantially arcuate shape so as to be rounded. Such a communication groove 2377c can be easily processed because it is not necessary to form a sharp corner. The aspect ratio of the substantially rectangular shape of the communicating groove according to the present invention can be set as appropriate.

An inner peripheral surface 2377b of the press-fit portion 2377 faces the outer peripheral surface of the valve portion 321 (see FIG. 4) with a gap therebetween. Thus, the press-fitting portion 2377 also serves as a shielding portion that shields fuel flowing from the pressurizing chamber 11 side into the plurality of communication grooves 2377c from traveling toward the outer peripheral surface of the valve portion 321 . Further, the channel cross-sectional area of the gap generated between the press-fit portion 2377 and the valve portion 321 is set to be equal to or larger than the channel cross-sectional area of the through hole 322b in the valve body 32 .

4. Fourth Embodiment Next, an electromagnetic suction valve mechanism according to a fourth embodiment of the present invention will be described with reference to FIG.
FIG. 17 is a cross-sectional view showing an enlarged open state of the electromagnetic suction valve mechanism according to the fourth embodiment.

A high-pressure fuel supply pump according to the fourth embodiment has the same configuration as the high-pressure fuel supply pump 100 according to the first embodiment. The high-pressure fuel supply pump according to the fourth embodiment differs from the high-pressure fuel supply pump 100 according to the first embodiment in the stopper 337 of the electromagnetic intake valve mechanism 3A. Therefore, here, the stopper 337 of the electromagnetic intake valve mechanism 3A will be described, and the description of the configuration common to the high-pressure fuel supply pump 100 will be omitted.

[Structure of stopper]
As shown in FIG. 17, a stopper 337 according to the fourth embodiment has the same configuration as the stopper according to the first embodiment. That is, the stopper 337 is formed in a substantially cylindrical shape with a bottom. The stopper 337 has a spring bearing surface 372 , a stopper surface 373 , a facing surface 374 and a guide hole 375 . A stopper convex portion 37a is formed on the outer side of the spring seat surface 372 .

Also, the stopper 237 has a press-fitting portion 3377 that is press-fitted into the intake valve housing 31 . The press-fit portion 3377 forms the outermost diameter portion of the stopper 337 . The press-fit portion 3377 is formed in a tubular shape having an inner peripheral surface 3377b. The press-fitting portion 3377 is press-fitted into the intake valve housing 31 . The stopper 337 is fixed to the intake valve housing 31 by press-fitting the press-fit portion 3377 into the intake valve housing 31 .

The press-fit portion 3377 has an end surface 3377a, an abutment surface 3378, and a plurality of communication grooves (not shown). The plurality of communicating grooves are the same as the plurality of communicating grooves 377c according to the first embodiment. The end surface 3377a of the press-fit portion 3377 is located closer to the valve seat 31a than the first surface 321a of the valve body 32 when the electromagnetic intake valve mechanism 3A is in the open state.

An inner peripheral surface 3377b of the press-fit portion 3377 faces the outer peripheral surface of the valve portion 321 with a gap therebetween. Thus, the press-fitting portion 3377 also serves as a shielding portion that shields fuel flowing from the pressurizing chamber 11 side into the plurality of communication grooves (not shown) from traveling toward the outer peripheral surface of the valve portion 321 . Further, the channel cross-sectional area of the gap generated between the press-fit portion 2377 and the valve portion 321 is set to be equal to or larger than the channel cross-sectional area of the through hole 322b in the valve body 32 .

The abutment surface 3378 is the surface opposite to the end surface 3377a. The abutment surface 3378 intersects the outer peripheral surface of the press-fit portion 3377 at right angles. The abutting surface 3378 abuts against a stepped portion of the lateral hole 1 i formed in the body 1 .

The abutment surface 3378 forms the same plane as the opening end surface of the intake valve housing 31 . Therefore, when the stopper 337 is press-fitted into the intake valve housing 31 , the abutment surface 3378 is set at the same height as the opening end surface of the intake valve housing 31 . This makes it possible to easily position the stopper 337 and the intake valve housing 31 relative to each other.

As a result, variations in the stroke of the valve body 32 can be reduced. If the variation in the stroke of the valve body 32 can be reduced, the variation in fluid force caused by the fuel flowing back from the pressure chamber 11 to the electromagnetic intake valve mechanism 3A side can also be reduced. Furthermore, variations in the movement time of the valve body 32 can be reduced. Therefore, in terms of pump performance, variations in discharge flow rate can be reduced.

A concave portion 3371 is provided on the inner diameter side (stopper convex portion 37a side) of the abutment surface 3378 . This makes it possible to clarify the place where the abutment surface 3378 is provided in the region between the stopper protrusion 37a and the outer peripheral surface of the press-fitting portion 3377 . As a result, the range of the abutment surface 3378 required to be machined with high precision is geometrically determined, so that machining and measurement of dimensions can be made easier than in the case where the recess 3371 is not provided. Therefore, variation in the stroke of the valve body 32 can be reduced while reducing manufacturing costs.

The stopper projection 37 a has a side peripheral surface 3379 . The side peripheral surface 3379 is parallel to the outer peripheral surface of the press-fit portion 3377 and has a smaller diameter than the outer peripheral surface of the press-fit portion 3377 . Since the press-fitting portion 3377 has the side peripheral surface 3379, the side peripheral surface 3379 can be gripped with a tool or the like when assembling the stopper 337, so that the ease of assembly can be improved.

5. Summary As described above, the electromagnetic intake valve mechanism 3 according to the first embodiment includes the valve body 32, the valve seat 31a on which the valve body 32 is seated, and the movement of the valve body 32 in the valve opening direction. A stopper 37 is provided. The valve body 32 has a first surface 321a (seating surface) that contacts the valve seat 31a, and an outer peripheral surface substantially orthogonal to the first surface 321a. The stopper 37 is formed in a cylindrical shape, and has an inner peripheral surface 377b facing the outer peripheral surface of the valve body 32 and an outer peripheral surface opposite to the inner peripheral surface 377b. It has a plurality of communication grooves 377c that are formed in the outer peripheral surface and serve as fuel passages. A portion of the press-fitting portion 377 (on the side of the end surface 377a) is closer to the valve seat 31a than the first surface 321a of the valve body 32 when the valve body 32 is in the valve-open state where movement in the valve-opening direction is restricted by the stopper 37. To position.

As a result, the backflow fuel 300 passing through the communication groove 377c and heading between the outer peripheral surface of the valve body 32 and the inner peripheral surface 377b of the press-fit portion 377 is shielded by the press-fit portion 377. Therefore, the backflow fuel 300 that has passed through the communication groove 377c passes between the press-fit portion 377 and the valve seat 31a. Then, flow separation occurs in part of the backflow fuel 300 that has passed between the press-fit portion 377 and the valve seat 31a. As a result, the fuel pressure between the valve seat 31a and the first surface 321a of the valve body 32 decreases. The fuel pressure between the valve seat 31a and the first surface 321a of the valve body 32 and the fuel pressure in the gap between the outer peripheral surface of the valve body 32 and the inner peripheral surface 377b of the press-fit portion 377 are It becomes the same as the pressure of the fuel that presses the body 32 toward the valve seat 31a. Therefore, the fuel pressure that presses the valve body 32 toward the valve seat 31a decreases. As a result, the valve body 32 can be prevented from moving toward the valve seat 31a (in the valve closing direction), and the discharge flow rate can be reduced to 0 during fuel cut, in which no fuel is discharged.

Also, the size of the gap between the outer peripheral surface of the valve body 32 and the inner peripheral surface 377b of the press-fit portion 377 according to the first embodiment is uniform over the entire circumference. As a result, variations in fuel pressure in the gap between the outer peripheral surface of the valve body 32 and the inner peripheral surface 377b of the press-fit portion 377 can be reduced. As a result, the operation of the valve body 32 can be stabilized.

Also, the plurality of communication grooves 377c according to the first embodiment described above are arranged at equal intervals in the circumferential direction on the outer peripheral surface of the press-fitting portion 377 . As a result, it is possible to reduce variations in pressure and turbulence in the flow of fuel that occur near the valve seat 31a side of the press-fit portion 377 . Furthermore, the stress generated by press-fitting the press-fitting portion 377 of the stopper 37 into the component (intake valve housing 31) into which the press-fitting portion is press-fitted can be dispersed.

Also, the plurality of communication grooves 377c according to the first embodiment described above have a circular shape concentric with the inner peripheral surface 377b of the press-fit portion 377 . Thereby, the thickness portion between the communication groove 377c and the inner peripheral surface 377b of the press-fit portion 377 can be made uniform. As a result, it is possible to suppress the formation of a low-rigidity portion by providing the communication groove 377c. In addition, it is possible to increase the size of the communication passage formed by the communication groove 377c through which the fuel passes.

Further, the stopper 337 according to the fourth embodiment described above has an abutment surface 3378 on the opposite side of the press-fit portion 3377 from the valve seat 31a side. The abutment surface 3378 forms the same plane as the opening end surface of the component (intake valve housing 31) into which the press-fitting portion 3377 is press-fitted. This makes it possible to easily position the parts into which the stopper 337 and the press-fit portion 3377 are press-fit.

Also, the stopper 337 according to the fourth embodiment described above has a side peripheral surface 3379 having a smaller diameter than the outer peripheral surface of the press-fit portion 3377 . As a result, when assembling the stopper 337, the side peripheral surface 3379 can be gripped with a tool or the like, so that the ease of assembly can be improved.

Further, the valve body 32 according to the first embodiment described above has a cylindrical fitting protrusion 322 that is slidably fitted to the stopper 37 . The fitting protrusion 322 has a through hole 322 b that communicates the gap between the outer peripheral surface of the valve body 32 and the inner peripheral surface 377 b of the press-fitting portion 377 with the inside of the fitting protrusion 322 . As a result, the through hole 322b serves as a breather channel, and the fuel inside the fitting protrusion 322 (inside the cylindrical hole 322a) can flow to the outside of the fitting protrusion 322.

Further, the channel cross-sectional area of the gap between the outer peripheral surface of the valve body 32 and the inner peripheral surface 377b of the press-fit portion 377 according to the first embodiment is equal to or larger than the channel cross-sectional area of the through hole 322b. As a result, the fuel (backflow fuel 300) flowing into the communication grooves 377c from the pressurizing chamber 11 side can be prevented from interfering with the operation of the valve body 32.

Further, the high-pressure fuel supply pump 100 (fuel pump) according to the first embodiment described above is supported by the body 1 having the pressurizing chamber 11 and the body 1 so as to be able to reciprocate. It has a plunger 2 for increasing or decreasing the capacity, and the electromagnetic intake valve mechanism 3 for discharging fuel into the pressurizing chamber 11 . As a result, the fuel pressure between the valve seat 31a and the first surface 321a of the valve body 32 and the fuel pressure in the gap between the outer peripheral surface of the valve body 32 and the inner peripheral surface 377b of the press-fit portion 377 are This is the same as the fuel pressure that presses the valve body 32 toward the valve seat 31a. Therefore, the fuel pressure that presses the valve body 32 toward the valve seat 31a decreases. As a result, the valve body 32 can be prevented from moving toward the valve seat 31a (valve closing direction), and the discharge flow rate can be reduced to 0 during fuel cut, in which fuel is not discharged.

The embodiments of the electromagnetic intake valve mechanism and the fuel pump of the present invention have been described above, including their effects. However, the electromagnetic intake valve mechanism and fuel 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.

In addition, the above-described embodiments have been described in detail for easy-to-understand description of the present invention, and are not necessarily limited to those having all the described configurations. Also, part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Moreover, it is possible to add, delete, or replace part of the configuration of each embodiment with another configuration.

1... pump body, 2... plunger, 3, 3A... electromagnetic intake valve mechanism, 4... cylinder, 5... discharge valve mechanism, 6... relief valve mechanism, 8... intake joint, 9... pressure pulsation reduction mechanism, 10... low pressure fuel Chamber 11 Pressurization chamber 12 Discharge joint 12a Fuel discharge port 30 Terminal member 31 Suction valve housing 31a Valve seat 31b Suction port 31c Rod guide 32 Valve element 33... Rod 33a... Rod flange 35... Electromagnetic coil 36... Anchor 37, 37A, 37B, 137, 237, 337... Stopper 37a, 37b... Stopper projection 39... Fixed core 100... High pressure fuel Supply pump 101... ECU 102... Feed pump 103... Fuel tank 104... Low pressure pipe 105... Fuel pressure sensor 106... Common rail 107... Injector 300... Backflow fuel 311... Seat part 311a... Inclined surface 312...seat outer peripheral portion 321...valve portion 321a...first surface 321b...second surface 322...fitting protrusion 322a...cylindrical hole 322b...through hole 322c...end face 372...seat surface 373... Stopper surface 374, 374A... Opposite surface 375... Guide hole 377, 1377, 2377, 3377... Press fitting part 377a, 1377a, 2377a, 3377a... End surface 377b, 1377b, 2377b, 3377b... Inner peripheral surface, 377c, 1377c, 2377c...Communicating groove, 3371...Recessed part, 3378...Abutment surface, 3379...Side peripheral surface

Claims (9)

1. a valve body;
   a valve seat on which the valve body is seated;
   a stopper that restricts the movement of the valve body in the valve opening direction,
   The valve body has a seating surface that contacts the valve seat and an outer peripheral surface that is substantially perpendicular to the seating surface,
   The stopper is formed in a cylindrical shape and has an inner peripheral surface facing the outer peripheral surface of the valve body, an outer peripheral surface opposite to the inner peripheral surface, and an outer peripheral surface of the press-fitted portion. a plurality of communication grooves formed in and serving as fuel passages,
   A part of the press-fitting portion is positioned closer to the valve seat than the seating surface of the valve body when the valve body is in a valve-open state in which movement of the valve body in a valve-opening direction is restricted by the stopper. .
2. 2. The electromagnetic suction valve mechanism according to claim 1, wherein the size of the gap between the outer peripheral surface of the valve body and the inner peripheral surface of the press-fit portion is uniform over the entire circumference.
3. 2. The electromagnetic suction valve mechanism according to claim 1, wherein the plurality of communication grooves are arranged at equal intervals in the circumferential direction on the outer peripheral surface of the press-fit portion.
4. 2. The electromagnetic suction valve mechanism according to claim 1, wherein the plurality of communication grooves have a circular shape concentric with the inner peripheral surface of the press-fit portion.
5. The stopper has an abutment surface on the side opposite to the valve seat side of the press-fit portion,
   2. The electromagnetic suction valve mechanism according to claim 1, wherein the abutment surface forms the same plane as an opening end surface of a component into which the press-fitting portion is press-fitted.
6. 2. The electromagnetic suction valve mechanism according to claim 1, wherein the stopper has a side peripheral surface with a smaller diameter than the outer peripheral surface of the press-fit portion.
7. The valve body has a cylindrical fitting protrusion that is slidably fitted to the stopper,
   The electromagnetic intake according to claim 1, wherein the fitting protrusion has a through hole that communicates a gap between the outer peripheral surface of the valve body and the inner peripheral surface of the press-fitting portion with the inner side of the fitting protrusion. valve mechanism.
8. 8. The electromagnetic intake valve mechanism according to claim 7, wherein a channel cross-sectional area of a gap between the outer peripheral surface of the valve body and the inner peripheral surface of the press-fit portion is equal to or larger than the flow channel cross-sectional area of the through hole.
9. a body with a pressurized chamber;
   a plunger that is reciprocally supported by the body and that reciprocates to increase or decrease the volume of the pressurizing chamber;
   an electromagnetic intake valve mechanism for discharging fuel into the pressurized chamber,
   The electromagnetic intake valve mechanism is
   a valve body;
   a valve seat on which the valve body is seated;
   a stopper that restricts the movement of the valve body in the valve opening direction,
   The valve body has a seating surface that contacts the valve seat and an outer peripheral surface that is substantially perpendicular to the seating surface,
   The stopper is formed in a cylindrical shape and has an inner peripheral surface facing the outer peripheral surface of the valve body, an outer peripheral surface opposite to the inner peripheral surface, and an outer peripheral surface of the press-fitted portion. a plurality of communication grooves formed in and serving as fuel passages,
   A part of the press-fitting portion is positioned closer to the valve seat than the seating surface of the valve body in a valve open state in which movement of the valve body in a valve opening direction is restricted by the stopper.

Images