CN110651117B

CN110651117B - Valve mechanism, electromagnetic suction valve mechanism, and high-pressure fuel pump

Info

Publication number: CN110651117B
Application number: CN201880033420.6A
Authority: CN
Inventors: 齐藤淳治; 臼井悟史; 根本雅史; 秋山壮嗣; 德丸千彰; 内山康久; 早谷政彦; 小野濑亨; 枇本亘; 住谷登
Original assignee: Hitachi Astemo Ltd
Current assignee: Hitachi Astemo Ltd
Priority date: 2017-05-31
Filing date: 2018-04-24
Publication date: 2021-10-08
Anticipated expiration: 2038-04-24
Also published as: WO2018221077A1; DE112018002027T5; JPWO2018221077A1; CN110651117A; JP6840238B2

Abstract

The invention provides a valve mechanism, an electromagnetic suction valve mechanism or a high-pressure fuel pump, which can restrain radial movement of a suction valve and improve flow control performance even though high pressure and large flow are promoted. To this end, the valve mechanism of the present invention includes: a spring member having a mounting collar portion and a movable portion and fixed by a spring support portion on the side opposite to the mounting collar portion; and a valve element which is forced by one side of the installation positioning ring part of the spring component; the valve body is formed with a convex portion that protrudes toward the spring support portion side and is positioned radially inward of the spring member, and a tip end portion of the convex portion is positioned on one side of the spring support portion with respect to a coil material cross section on both sides in a radial direction of at least a first turn of the movable portion adjacent to the attachment bezel portion in a cross-sectional view cut in an axial direction of the spring member through a radial center of the spring member.

Description

Valve mechanism, electromagnetic suction valve mechanism, and high-pressure fuel pump

Technical Field

The invention relates to a valve mechanism, an electromagnetic suction valve mechanism, and a high-pressure fuel pump.

Background

As background art of the high-pressure fuel pump of the present invention, there are techniques described in patent documents 1 and 2. Patent document 1 discloses "a high-pressure fuel pump including a pump housing 1, a plunger 2, and an electromagnetic intake valve 300, the electromagnetic intake valve 300 including a valve 301c, a valve seat 302a for opening and closing a fuel passage by separating and contacting the valve 301c, and a valve stopper 313 against which the valve 301c abuts when the valve is opened, the electromagnetic intake valve 300 being mounted in an electromagnetic intake valve insertion hole 1k formed in the pump housing 1, and the electromagnetic intake valve 300 being controlled to control an amount of discharged fuel, wherein a bottom portion 1ka abutting against the valve stopper 313 and a fuel passage hole 1a penetrating the bottom portion 1ka and communicating both sides of the bottom portion 1ka are provided in the electromagnetic intake valve insertion hole 1 k" (refer to an abstract).

Further, patent document 2 discloses that "includes: a housing main body 11 having a fuel passage 100 that guides fuel to a pressurizing chamber 121; a valve body 30 provided in the fuel passage 100; a valve member 40 including a disk portion 41 that is seated on or separated from the valve seat 34 of the valve body 30 and a hollow cylindrical guide portion 42; a stopper 50 having a cylindrical portion 51; a needle 60 that can abut against the valve member 40; and an electromagnetic drive unit 70 capable of attracting the needle 60 in the valve closing direction of the valve member 40. The stopper 50 covers a side wall surface of the pressurizing chamber 121 of the valve member 40 when viewed from the pressurizing chamber 121 side. The guide portion 42 has a cylindrical guide surface 43 on the inner wall thereof, which is slidable with the outer wall of the cylindrical portion 51 of the stopper 50. The spring 21 is arranged such that at least a part of the axial direction overlaps at least a part of the axial direction of the guide surface 43 "(refer to abstract).

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2016 & 191367

Patent document 2: japanese patent application laid-open No. 2010-156264

Disclosure of Invention

Problems to be solved by the invention

However, in the case of the suction valve structure described in patent document 1, if the suction valve is forced to tilt in the radial direction or if the suction valve is deflected in the radial direction, the movement cannot be controlled. This causes a problem that the sealing of the suction valve is not performed, and the flow rate is reduced or the flow rate control performance is deteriorated. Further, the suction valve contacts the suction valve seat portion obliquely, which causes abrasion of the suction valve seat portion, thereby causing a problem of deterioration of sealing performance.

On the other hand, in the case of the suction valve described in patent document 2, the convex portion of the suction valve is slidably guided by the inner diameter cylinder of the valve frame. However, this structure requires a high precision machining accuracy because a recess for holding the spring needs to be machined in the projection of the suction valve, and also has a problem of increased cost because a portion (recess) for holding the spring is machined.

Therefore, an object of the present invention is to provide a valve mechanism, an electromagnetic suction valve mechanism, or a high-pressure fuel pump that suppresses radial movement of a suction valve and improves flow rate control performance even when high pressure and large flow rate are increased.

Means for solving the problems

In order to solve the above problem, a valve mechanism according to the present invention includes: a spring member having a mounting collar portion and a movable portion and fixed by a spring support portion on the side opposite to the mounting collar portion; and a valve body that is biased by one side of the mounting collar portion of the spring member, wherein a convex portion that protrudes toward one side of the spring support portion and is positioned radially inward of the spring member is formed on the valve body, and a tip end portion of the convex portion is positioned on one side of the spring support portion with respect to a coil material cross section on both sides in a radial direction of at least a first turn of the movable portion adjacent to the mounting collar portion in a cross-sectional view that is cut in an axial direction of the spring member through a radial center of the spring member.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the present invention, it is possible to provide a valve mechanism, an electromagnetic suction valve mechanism, or a high-pressure fuel pump that suppresses radial movement of a suction valve and improves flow rate control even when high pressure and large flow rate are increased.

Problems, configurations, and effects other than those described above will be apparent from the following description of the embodiments.

Drawings

Fig. 1 is an overall sectional view of the high-pressure fuel pump, taken along the axial direction of the plunger.

Fig. 2 is an overall sectional view of the high-pressure fuel pump, taken along a direction perpendicular to the axial direction of the plunger, and is a sectional view taken at the axial center of the intake port and the axial center of the discharge port of the fuel.

Fig. 3 is an overall sectional view of the high-pressure fuel pump at another angle different from fig. 1, and is a sectional view at the center of the suction joint shaft.

Fig. 4 is an enlarged longitudinal sectional view of the electromagnetic suction valve mechanism of the high-pressure fuel pump.

Fig. 5 is a diagram showing the overall configuration of a system including a high-pressure fuel pump.

Fig. 6 is an enlarged view illustrating a structure of a suction valve of the high-pressure fuel pump according to the embodiment of the present invention.

Fig. 7 is an enlarged view illustrating a configuration of the suction valve in a state where the valve body (suction valve 30) is seated on the valve seat (suction valve seat portion 31a) according to the embodiment of the present invention.

Fig. 8 is an enlarged view illustrating a structure of the suction valve in a state where the valve body (suction valve 30) is in contact with the stopper 32 according to the embodiment of the present invention.

Detailed Description

Next, the configuration and operational effects of the high-pressure fuel pump according to the embodiment of the present invention will be described with reference to the drawings. The high-pressure fuel pump of the present embodiment is a high-pressure fuel pump that discharges high-pressure fuel of 20MPa or more. In the drawings, the same reference numerals denote the same elements.

Examples

(integral constitution)

First, the configuration and operation of the system will be described with reference to the overall configuration diagram of the engine system shown in fig. 5. The portion enclosed by the broken line indicates the main body of the high-pressure fuel pump, and the mechanism and parts shown in the broken line are integrally attached to the pump body 1.

The fuel of the fuel tank 20 is drawn up by the feed pump 21 in accordance with a signal from an engine control unit 27 (hereinafter referred to as ECU). The fuel is pressurized to the appropriate feed pressure and delivered to the low pressure fuel intake port 10a of the high pressure fuel pump via intake conduit 28. The fuel having passed through the suction joint 51 (see fig. 2) from the low-pressure fuel suction port 10a reaches the suction port 31b of the electromagnetic suction valve mechanism 300 constituting the variable capacity mechanism via the metal damper 9 (pressure pulsation reducing mechanism) and the suction passage 10 d.

The fuel that has flowed into the electromagnetic intake valve mechanism 300 flows into the compression chamber 11 through the intake valve 30.

The plunger 2 is given power for reciprocating motion by a cam 93 (see fig. 1) of an engine (internal combustion engine). By the reciprocation of the plunger 2, fuel is sucked from the suction valve 30 in the downward stroke of the plunger 2, and the fuel is pressurized in the upward stroke. The fuel is pressure-fed to the common rail 23, to which the pressure sensor 26 is attached, via the discharge valve mechanism 8. Then, the injector 24 injects fuel to the engine according to a signal from the ECU 27. The present embodiment is a high-pressure fuel pump suitable for a so-called direct injection engine system in which the injector 24 directly injects fuel into the cylinder of the engine. The high-pressure fuel pump discharges a desired fuel flow rate of the supply fuel in accordance with a signal from the ECU 27 to the electromagnetic suction valve mechanism 300.

(construction of high-pressure Fuel Pump)

Next, the structure of the high-pressure fuel pump will be described with reference to fig. 1 to 4. Fig. 1 is a longitudinal sectional view of the high-pressure fuel pump, and fig. 2 is a horizontal sectional view of the high-pressure fuel pump as viewed from above. Further, fig. 3 is a longitudinal sectional view of the high-pressure fuel pump viewed from another direction different from fig. 1. Fig. 4 is an enlarged view of the electromagnetic suction valve mechanism 300.

As shown in fig. 1, the high-pressure fuel pump includes: a metal buffer 9; a pump body 1 (pump body) forming a damper housing portion 1p housing the metal damper 9; a damper cover 14 attached to the pump body 1, covering the damper housing portion 1p, and holding the metal damper 9 between itself and the pump body 1; and a holding member 9a fixed to the bumper cover 14 and holding the metal bumper 9 from the side opposite to the bumper cover 14. The holding member 9a is disposed between the metal damper 9 and the pump body 1, and holds the metal damper 9 from one side of the pump body 1. The high-pressure fuel pump is closely attached to a high-pressure fuel pump mounting portion 90 of the internal combustion engine using a mounting flange 1e (see fig. 2) provided on the pump body 1, and is fixed by a plurality of bolts.

As shown in fig. 1, in order to seal the high-pressure fuel pump mounting portion 90 and the pump body 1, an O-ring 61 is fitted to the pump body 1 to prevent oil from leaking to the outside. A cylinder 6 that guides the reciprocating motion of the plunger 2 and forms a pressurizing chamber 11 together with the pump body 1 is attached to the pump body 1. Further, an electromagnetic intake valve mechanism 300 for supplying fuel to the pressurizing chamber 11 and a discharge valve mechanism 8 for discharging fuel from the pressurizing chamber 11 to a discharge passage are provided (refer to fig. 2).

As shown in fig. 1, the cylinder 6 is press-fitted into the cylinder 1 on the outer peripheral side thereof, and the cylinder 6 is pressed in the upward direction in the drawing by deforming the cylinder on the inner peripheral side at the fixing portion 6a, and the upper end surface of the cylinder 6 is sealed so that the fuel pressurized in the pressurizing chamber 11 does not leak to the low pressure side. A tappet 92 that converts a rotational motion of a cam 93 (cam mechanism) attached to a camshaft of an internal combustion engine into an up-and-down motion and transmits the up-and-down motion to the plunger 2 is provided at a lower end of the plunger 2. The plunger 2 is pressed against the tappet 92 by the spring 4 via the fastener 15. This allows the plunger 2 to reciprocate up and down in accordance with the rotational movement of the cam 93.

Further, a plunger seal 13 held at the lower end portion of the inner periphery of the seal holder 7 is provided at the lower portion in the drawing of the cylinder 6 in a state of slidably contacting the outer periphery of the plunger 2. This seals the fuel in the sub-chamber 7a from flowing into the internal combustion engine when the plunger 2 slides. At the same time, lubricating oil (including engine oil) for lubricating sliding portions in the internal combustion engine is prevented from flowing into the pump body 1.

A suction joint 51 is attached to a side surface portion of the pump body 1 of the high-pressure fuel pump. The suction fitting 51 is connected to a low-pressure pipe that supplies fuel from the vehicle fuel tank 20, from where the fuel is supplied to the inside of the high-pressure fuel pump. The suction filter 52 (refer to fig. 3) in the suction joint 51 has a function of preventing foreign matter existing between the fuel tank 20 and the low-pressure fuel suction port 10a from being absorbed into the high-pressure fuel pump due to the flow of fuel.

As shown in fig. 1, the fuel after passing through the low-pressure fuel suction port 10a reaches the suction port 31b of the electromagnetic suction valve mechanism 300 via the metal damper 9 and the suction passage 10d (low-pressure fuel flow path).

The electromagnetic suction valve mechanism 300 will be described in detail with reference to fig. 4. Although the electromagnetic intake valve mechanism 300 is shown in fig. 1, 2, and 4, the structure shown in these figures is shown for the case where the present invention is not applied.

The coil portion is composed of a 1 st yoke 42, an electromagnetic coil 43, a 2 nd yoke 44, a bobbin 45, a terminal 46, and a connector 47. An electromagnetic coil 43 formed by winding a copper wire on a bobbin 45 a plurality of times is disposed so as to be surrounded by the 1 st yoke 42 and the 2 nd yoke 44, and is molded and fixed integrally with a connector which is a resin member. One end of each of the two terminals 46 is connected to both ends of the copper wire of the coil in an electrically conductive manner. Similarly, the terminal 46 is molded integrally with the connector, and the remaining end thereof is configured to be connectable to the engine control unit side.

In the coil portion, a hole portion in the center portion of the 1 st yoke 42 is press-fitted and fixed to the outer core 38. At this time, the inner diameter side of the 2 nd yoke 44 is configured to contact the fixed core 39 or to be close to it with a slight gap.

In order to form the magnetic circuit, the 1 st and 2 nd yokes 42 and 44 are made of a magnetic stainless material in consideration of corrosion resistance, and the bobbin 45 and the connector 47 are made of a high-strength heat-resistant resin in consideration of strength and heat resistance. The electromagnetic coil 43 is made of copper, and the terminal 46 is made of brass plated with metal.

In this way, a magnetic circuit is formed by the outer core 38, the 1 st yoke 42, the 2 nd yoke 44, the fixed core 39, and the armature portion 36, and when a current is applied to the coil, a magnetic attraction force is generated between the fixed core 39 and the armature portion 36, and a force that pulls each other is generated. In the outer core 38, the axial portion of the fixed core 39 and the armature portion 36 that generates the magnetic attraction force therebetween is made as thin as possible, and thus almost all of the magnetic flux passes between the fixed core 39 and the armature portion 36, and the magnetic attraction force can be obtained efficiently.

The solenoid mechanism portion includes a valve rod 35 as a movable portion, an armature portion 36, a valve rod guide 37 as a fixed portion, an outer core 38, a fixed core 39, a valve rod biasing spring 40, and an armature portion biasing spring 41.

The stem 35 and the armature 36 as the movable portions are configured as different members. The valve rod 35 is slidably held on the inner peripheral side of the valve rod guide 37 in the axial direction, and the armature portion 36 is slidably held on the outer peripheral side of the valve rod 35 on the inner peripheral side. That is, the stem 35 and the armature portion 36 are both configured to be slidable in the axial direction within a geometrically limited range.

In order to move smoothly in the axial direction in the fuel, the armature portion 36 has 1 or more through holes 36a penetrating in the axial direction of the component, and the restriction of the movement by the pressure difference between the front and rear sides of the armature portion is eliminated as much as possible.

The valve rod guide 37 is inserted radially into the inner periphery of a hole of the pump body 1 into which the suction valve is inserted, abuts against one end of the suction valve seat in the axial direction, and is disposed so as to be sandwiched between an outer core 38 welded and fixed to the pump body 1 and the pump body 1. The stem guide 37 is also provided with a through hole 37a penetrating in the axial direction, similarly to the armature portion 36, so that the armature portion can move smoothly and the pressure of the fuel chamber on the armature portion side does not interfere with the movement of the armature portion.

The outer core 38 is formed in a thin cylindrical shape on the opposite side of the portion welded to the pump body 1, and is welded and fixed with the valve rod guide 37 inserted on the inner peripheral side thereof. The valve rod biasing spring 40 is disposed on the inner peripheral side of the fixed core 39 with the small diameter portion as a guide, and the valve rod 35 is in contact with the intake valve 30 to bias the intake valve in a direction of separating the intake valve from the intake valve seat portion 31a, that is, in a valve opening direction of the intake valve. The suction valve 30 contacts the stopper 32 at the maximum opening degree. The stopper 32 is formed by pressing a metal plate, and is fixed by press-fitting its outer peripheral surface into the seat member 31. A part of the outer peripheral surface is a notch, and the notch is configured to always communicate with the recess portion, thereby communicating the upstream side of the intake valve with the compression chamber 11. In the present embodiment, the suction valve seat portion 31a and the suction port 31b are formed in the same seat member 31.

The armature biasing spring 41 is disposed such that one end thereof is inserted into a central bearing portion 37b of the valve rod guide 37, which is provided on the center side and has a cylindrical diameter, to be held coaxially therewith, and such that the armature 36 is biased toward the valve rod flange portion 35 a. The moving amount 36e of the armature portion 36 is set larger than the moving amount 30e of the suction valve 30. The purpose of this is to reliably close the suction valve 30. In the present embodiment, the stem guide 37 is formed on the same member as the seat member 31.

Since the valve rod 35 and the valve rod guide 37 slide with each other and the valve rod 35 repeatedly collides with the intake valve 30, a material obtained by heat-treating martensitic stainless steel is used in consideration of hardness and corrosion resistance. In order to form a magnetic circuit, magnetic stainless steel is used for the armature portion 36 and the fixed core 39, and austenitic stainless steel is used for the stem biasing spring 40 and the armature portion biasing spring 41 in consideration of corrosion resistance.

According to the above configuration, the suction valve unit and the solenoid mechanism unit are organically arranged and configured with 3 springs. There are a suction valve biasing spring 33 formed in the suction valve portion, a stem biasing spring 40 and an armature portion biasing spring 41 formed in the solenoid mechanism portion. In the present embodiment, all the springs are coil springs, but any configuration may be employed as long as the springs can obtain the biasing force.

As shown in fig. 2, the discharge valve mechanism 8 provided at the outlet of the compression chamber 11 includes a discharge valve seat 8a, a discharge valve 8b that is in contact with and separated from the discharge valve seat 8a, a discharge valve spring 8c that biases the discharge valve 8b toward the discharge valve seat 8a, and a discharge valve stopper 8d that determines the stroke (movement distance) of the discharge valve 8 b. The discharge valve stopper 8d and the pump body 1 are joined by welding at the abutting portion 8e, and the fuel is isolated from the outside.

In a state where there is no fuel differential pressure between the compression chamber 11 and the discharge valve chamber 12a, the discharge valve 8b is pressed against the discharge valve seat 8a by the biasing force of the discharge valve spring 8c, and is closed. The discharge valve 8b is opened against the discharge valve spring 8c from the time when the fuel pressure in the pressurizing chamber 11 becomes higher than the fuel pressure in the discharge valve chamber 12 a. Then, the high-pressure fuel in the pressurizing chamber 11 is discharged to the common rail 23 through the discharge valve chamber 12a, the fuel discharge passage 12b, and the fuel discharge port 12.

When the discharge valve 8b is opened, it contacts the discharge valve stopper 8d, and the stroke is limited. Therefore, the stroke of the discharge valve 8b is appropriately determined by the discharge valve stopper 8 d. This prevents the fuel discharged at high pressure into the discharge valve chamber 12a from flowing back into the compression chamber 11 again due to a delay in closing the discharge valve 8b caused by an excessively large stroke, and thus can suppress a decrease in the efficiency of the high-pressure fuel pump. When the discharge valve 8b repeats the valve opening and closing movement, the discharge valve 8b is guided by the outer peripheral surface of the discharge valve stopper 8d so as to move only in the stroke direction. Thereby, the discharge valve mechanism 8 serves as a check valve that restricts the flow direction of the fuel. The compression chamber 11 is constituted by the pump body 1 (pump housing), the electromagnetic intake valve mechanism 300, the plunger 2, the pressure cylinder 6, and the discharge valve mechanism 8.

(operation of high-pressure Fuel Pump)

When the plunger 2 moves in the direction of the cam 93 and enters the intake stroke state by the rotation of the cam 93, the volume of the compression chamber 11 increases, and the fuel pressure in the compression chamber 11 decreases. In this stroke, when the fuel pressure in the compression chamber 11 is lower than the pressure of the inlet port 31b, the inlet valve 30 becomes an open state. As shown in fig. 4, the fuel flows into the pressurizing chamber 11 through the opening 30e of the intake valve 30.

After the plunger 2 finishes the intake stroke, it is shifted to the compression stroke by the upward movement. Here, the electromagnetic coil 43 is kept in the non-energized state, and does not generate a magnetic force. The valve-rod biasing spring 40 is set to have a sufficient biasing force required to open and maintain the suction valve 30 in a non-energized state. The volume of the compression chamber 11 decreases with the compression movement of the plunger 2, but in this state, the fuel once sucked into the compression chamber 11 is returned to the suction passage 10d through the opening 30e of the suction valve 30 in the valve-opened state again, and therefore the pressure in the compression chamber does not increase. This stroke is referred to as a loopback stroke.

In this state, when a control signal from the ECU 27 is applied to the electromagnetic intake valve mechanism 300, a current flows to the electromagnetic coil 43 via the terminal 46. Then, a magnetic attractive force is generated between the magnetic core 39 and the armature, and thereby the valve rod 35 is moved in a direction away from the intake valve 30 by the magnetic attractive force exceeding the urging force of the valve rod urging spring 40. Therefore, the suction valve 30 is closed by the urging force of the suction valve urging spring 33 and the fluid force caused by the inflow of the fuel into the suction passage 10 d. After the valve is closed, the fuel pressure in the pressurizing chamber 11 rises with the rising movement of the plunger 2, and when the fuel pressure becomes equal to or higher than the pressure at the fuel discharge port 12, the high-pressure fuel is discharged through the discharge valve mechanism 8 and supplied to the common rail 23. This stroke is referred to as a discharge stroke.

That is, the upward stroke between the lower start point and the upper start point of the plunger 2 is composed of a return stroke and a discharge stroke. Then, by controlling the timing of energization to the electromagnetic coil 43 of the electromagnetic intake valve mechanism 300, the amount of the discharged high-pressure fuel can be controlled. When the timing of energizing the solenoid 43 is set to be earlier, the proportion of the return stroke in the raising stroke is smaller, and the proportion of the discharge stroke is larger. That is, the fuel returned to the intake passage 10d is small, and the high-pressure discharged fuel is large. On the other hand, if the energization timing is made later, the proportion of the return stroke in the up stroke is large, and the proportion of the discharge stroke is small. That is, the amount of fuel returned to the intake passage 10d is large, and the amount of fuel discharged at high pressure is small. The timing of energization of the solenoid 43 is controlled by a command from the ECU 27. By controlling the timing of energization to the electromagnetic coil 43 in the above-described manner, the amount of fuel discharged at high pressure can be controlled to an amount required for the internal combustion engine.

(constitution of Metal buffer)

As shown in fig. 1, the low-pressure fuel chamber 10 is provided with a metal damper 9 that reduces the pressure pulsation generated in the high-pressure fuel pump from affecting the intake pipe 28 (fuel pipe). When the fuel once flowing into the compression chamber 11 is returned to the intake passage 10d by the capacity control through the intake valve 30 (intake valve body) in the valve-opened state again, pressure pulsation occurs in the low-pressure fuel chamber 10 due to the fuel returned to the intake passage 10 d. However, the metal damper 9 provided in the low pressure fuel chamber 10 is formed by a metal diaphragm damper in which 2 pieces of disk-shaped metal plates in the form of a corrugated plate are bonded to each other on the outer periphery thereof and an inert gas such as argon is injected into the inside thereof, and the pressure pulsation is absorbed and reduced by the expansion and contraction of the metal damper.

The plunger 2 has a large diameter portion 2a and a small diameter portion 2b, and the volume of the sub-chamber 7a is increased or decreased by the reciprocating motion of the plunger 2. The sub-chamber 7a communicates with the low-pressure fuel chamber 10 through a fuel passage 10e (refer to fig. 3). When the plunger 2 is lowered, fuel flows from the sub-chamber 7a to the low pressure fuel chamber 10, and when the plunger 2 is raised, fuel flows from the low pressure fuel chamber 10 to the sub-chamber 7 a.

This reduces the flow rate of fuel into and out of the pump in the intake stroke or the return stroke of the pump, and has a function of reducing pressure pulsation generated inside the high-pressure fuel pump.

In recent years, high-pressure fuel pumps have been increasing in the pressure of discharged fuel (20MPa or more) and increasing in the flow rate. As a result of diligent studies by the present inventors, it has been found that, in this case, a large force is also applied to the intake valve 30 shown in fig. 1, 2, and 4 in a direction other than the intake valve axial direction (the left-right direction in fig. 1, 2, and 4). However, in the case of the suction valve structure shown in fig. 1, 2, and 4, if the suction valve 30 is tilted by a force in the radial direction or if it is deflected in the radial direction, the movement cannot be controlled. This causes a problem that the sealing of the suction valve 30 is not performed, and the flow rate is reduced or the flow rate control performance is deteriorated. Further, the suction valve 30 contacts the suction valve seat portion 31a obliquely, which may cause abrasion of the suction valve seat portion 31a, thereby causing a problem of deterioration of sealing performance.

Therefore, an embodiment of the present invention will be described with reference to fig. 6. The valve mechanism of the present embodiment includes: a spring member 33 having a mounting collar portion 33a and a movable portion 33b, and fixed by a spring support portion 32a on the side opposite to the mounting collar portion 33 a; and a valve body (suction valve 30) urged by a side of the spring member 33 on which the collar portion 33a is mounted. Further, the valve body (suction valve 30) is formed with a convex portion 30b that protrudes toward one side of the spring support portion 32a and is positioned radially inward of the spring member 33. As shown in fig. 6, in a cross-sectional view of the spring member 30 taken through the center in the radial direction and cut in the axial direction of the spring member, the tip end portions 30c of the convex portions 30b are located on the spring support portion 32a side with respect to the coil cross-section on both sides in the radial direction of at least the first turn of the movable portion 33b adjacent to the mounting collar portion 33 a.

The movable portion 33b may be referred to as an effective ring portion, and the movable portion 33b is a portion that actually operates as a spring. Since the movable portion 33b has a gap, even when a large force is applied in the radial direction of the valve body (suction valve 30), the valve body itself is tilted or swung through the gap of the movable portion. Therefore, in the present embodiment, as described above, the distal end portion 30c of the convex portion 30b is positioned on the spring support portion 32a side with respect to the coil cross section on both sides in the radial direction of at least the first turn of the movable portion 33b (effective coil portion). Furthermore, the ends of the coil cross-section on both radial sides of the first turn are indicated in fig. 6 by dashed lines. This, in turn, suppresses the movement of the valve body itself, such as tilting or yawing, even when a large force is applied in the radial direction of the valve body (suction valve 30). Therefore, the above-described problems of the flow rate reduction or the deterioration of the flow rate control performance can be solved. Further, since the valve body (the suction valve 30) can be prevented from obliquely contacting the suction valve seat portion 31a, the problem of the deterioration of the sealing performance can be solved.

As shown in fig. 7, the valve mechanism of the present embodiment is preferably configured to include a valve seat (suction valve seat portion 31a) that seals by seating a valve body (suction valve 30), and in a cross-sectional view cut along the axial direction of the spring member in a state where the valve body (suction valve 30) is seated on the valve seat (suction valve seat portion 31a), the tip end portion 30c of the convex portion 30b is located on the side of the spring support portion 32a in comparison with the coil cross-sections on both sides in the radial direction of at least the first turn of the movable portion 33 b. Further, if the tip end portion 30c of the convex portion 30b is positioned on the side of the spring support portion 32a with respect to the coil cross section on both sides in the radial direction of at least the second turn of the movable portion 33b, the play in the radial direction can be further suppressed.

As shown in fig. 8, the valve mechanism of the present embodiment is preferably provided with a stopper 32 that restricts movement of the valve body (suction valve 30) in the direction opposite to the valve seat (suction valve seat portion 31a), and the tip end portion 30c of the convex portion 30b is preferably located on the side of the spring support portion 32a with respect to a position half the entire length of the spring member 33 in a cross-sectional view cut along the axial direction of the spring member in a state where the valve body (suction valve 30) and the stopper 32 are in contact.

Fig. 8 is a view cut in a cross section of a convex portion of the stopper 32 with which the valve body (suction valve 30) can be seen, and fig. 6 is a view cut in a cross section of a convex portion of the stopper 32 with which the valve body (suction valve 30) cannot be seen. Therefore, fig. 6 and 8 show the same state. Further, it is preferable that the stopper 32 has a cylindrical holding portion 32c for holding the spring member 33 on the radially inner side. Further, the stopper 32 is preferably configured to hold the spring member 33 by the inner peripheral surface of the holding portion 32c, and to have a fixing portion 32d for fixing the stopper 32 on the radially outer side of the inner peripheral surface. In the present embodiment, the stopper 32 is formed by press working, and therefore can be configured at low cost.

It is preferable that the convex portion 30b of the valve body (suction valve 30) is formed in a cylindrical shape. As shown in fig. 6, the valve body (suction valve 30) is formed of a cylindrical portion 30d having a relatively low height and a cylindrical protruding portion 30b having a height greater than that of the cylindrical portion 30 d. The electromagnetic intake valve mechanism 300 of the present embodiment further includes: the valve mechanism described above; a valve rod 35 which is configured separately from the valve body (suction valve 30) and biases the valve body (suction valve 30) in a valve opening direction; an armature 36 that drives the valve rod 35 in a valve closing direction; and an electromagnetic coil 43 that generates an electromagnetic attraction force that drives the armature 36 in the valve closing direction.

The high-pressure fuel pump of the present embodiment includes: the valve mechanism described above; a valve rod 35 which is configured separately from the valve body and biases the valve body in a valve opening direction; an armature 36 that drives the valve rod 35 in a valve closing direction; an electromagnetic coil 43 that generates an electromagnetic attraction force that drives the armature 36 in the valve closing direction; a pressurizing chamber 11 located on the downstream side of the valve body (intake valve 30) and pressurizing the fuel; and a plunger 2 that increases and decreases the volume of the pressurizing chamber 11.

The present invention includes various modifications, and is not limited to the embodiments described above.

For example, the above-described embodiments are for describing the present invention in detail so as to be easily understood, and are not necessarily limited to having all the configurations. Further, addition, deletion, and replacement of another configuration may be performed on a part of the configuration of the embodiment.

Description of the symbols

1 Pump body

2 plunger piston

11 pressurization chamber

30 suction valve

30b convex part

30c tip part

30d cylindrical part

31a suction valve seat part

32 stop

32a spring support

32c holding part

33 spring member

33a mounting and positioning ring part

33b movable part

35 valve rod

36 armature

43 electromagnetic coil.

Claims

1. A valve mechanism is characterized by comprising:

a spring member having a mounting collar portion and a movable portion and fixed by a spring support portion on the side opposite to the mounting collar portion;

a valve body biased by one side of the mounting land portion of the spring member;

a valve seat that seals by seating the valve element; and

a stopper that restricts movement of the spool in a direction opposite to the valve seat, the spool having a convex portion formed thereon that protrudes toward one side of the spring support portion and is located radially inward of the spring member,

the stopper has an inner surface disposed opposite to an outer surface of the convex portion of the valve body,

the inner surface of the stopper is formed of a plurality of inner surface portions having different diameters, and an inner surface portion having a largest diameter is located on a side opposite to the spring support portion,

in a cross-sectional view cut in an axial direction of the spring member through a radial center of the spring member, in a state where the valve body is seated on the valve seat, a tip end portion of the convex portion is positioned on a side of the spring support portion with respect to a coil cross-section on a side close to the spring support portion of both sides in a radial direction of a second turn of the movable portion farthest from the mounting positioning ring portion, and in a state where the valve body is in contact with the stopper, the tip end portion of the convex portion is positioned on a side of the spring support portion with respect to an inner side surface portion having a largest diameter among the inner side surfaces of the stopper.

2. The valve mechanism according to claim 1, comprising:

the protruding portion is configured such that, in a cross-sectional view cut along an axial direction of the spring member in a state where the valve element is in contact with the stopper, a tip end portion of the protruding portion is located on a side of the spring support portion with respect to a position of a half of an entire length of the spring member.

3. The valve mechanism according to claim 1, comprising:

the stopper is configured to have a cylindrical holding portion that holds the spring member radially inward.

4. The valve mechanism of claim 3,

the stopper is configured to hold the spring member by an inner peripheral surface of the holding portion, and a fixing portion for fixing the stopper is provided radially outside the inner peripheral surface.

5. A valve mechanism according to claim 3 or 4,

the stopper is formed by press working.

6. The valve mechanism of claim 1,

the convex portion is formed in a cylindrical shape.

7. The valve mechanism of claim 1,

the valve body is formed of a cylindrical portion and the cylindrical protruding portion having a height greater than that of the cylindrical portion.

8. An electromagnetic suction valve mechanism comprising:

the valve mechanism according to any one of claims 1 to 6;

a valve rod which is configured to be different from the valve body, and which applies force to the valve body in a valve opening direction;

an armature that drives the valve rod in a valve closing direction; and

a coil that generates an electromagnetic attraction force that drives the armature in the valve closing direction.

9. A high-pressure fuel pump is characterized by comprising:

the valve mechanism according to any one of claims 1 to 7;

an armature that drives the valve rod in a valve closing direction;

a coil that generates an electromagnetic attraction force that drives the armature in the valve closing direction;

a pressurizing chamber located on a downstream side of the valve body and configured to pressurize fuel; and

and a plunger that increases or decreases the volume of the pressurizing chamber.