WO2019012969A1

WO2019012969A1 - Solenoid intake valve, and high-pressure fuel pump provided therewith

Info

Publication number: WO2019012969A1
Application number: PCT/JP2018/023944
Authority: WO
Inventors: 雄太笹生; 早谷　政彦; 康久内山; 菅波　正幸; 棟方　明広; 雅史根本; 壮嗣秋山
Original assignee: 日立オートモティブシステムズ株式会社
Priority date: 2017-07-14
Filing date: 2018-06-25
Publication date: 2019-01-17
Also published as: CN110809670A; CN110809670B; JPWO2019012969A1; DE112018003099T5; JP6754902B2

Abstract

The purpose of the present invention is to provide a solenoid intake valve which improves assembly by avoiding increasing the press fitting load in the case in which a solenoid valve mechanism 300 is inserted and fixed in a hole formed in a pump body 1, and to provide a high-pressure fuel pump. This solenoid valve mechanism is provided with a valve body that opens and closes a flow path, a movable core, and a magnetic core that attracts the movable core, is inserted and fixed in an insertion hole, and is provided with: a press-fitting part which is formed on the outer peripheral portion on the distal end in the insertion direction and which is press-fitted into a small-diameter insertion hole; a clearance-fitting part which, disposed towards the entrance in the insertion direction with respect to the press-fitting part, is formed on an outer peripheral portion having an outer diameter larger than that of the press fitting part, and which is arranged having a prescribed clearance from a large-diameter insertion hole having a larger diameter than that of the small-diameter insertion hole; and a welded part which, disposed towards the entrance in the insertion direction with respect to the clearance-fitting part, is welded to the member in which the insertion hole is formed.<u/> <u/>

Description

Electromagnetic suction valve and high pressure fuel pump provided with the same

The present invention relates to a solenoid intake valve applied to an internal combustion engine, and a high pressure fuel pump provided with the same.

As a prior art of the high pressure fuel pump of this invention, there exists a thing of patent document 1. FIG. In paragraphs 0013 and 0014 of this patent document 1, “the fuel that has passed through the suction joint 51 from the low pressure fuel suction port 10a is a pressure pulsation reduction mechanism 9 and an electromagnetic valve mechanism 300 that constitutes a capacity variable mechanism via the suction passage 10d. The fuel that has flowed into the solenoid valve mechanism 300 passes through the suction valve 30 and flows into the pressurizing chamber 11. "

JP, 2017-82717, A

Although the solenoid valve mechanism 300 is illustrated in FIG. 2 and FIG. 3 of the above Patent Document 1, by what method the solenoid valve mechanism 300 is fixed to the hole formed in the pump body 1 Not clear. Therefore, in the present invention, when the electromagnetic valve mechanism 300 is inserted into the hole formed in the pump body 1 and fixed, the increase in the press-fit load is suppressed to improve the assemblability, or the high-pressure fuel Intended to provide a pump.

In order to solve the above-mentioned problems, the present invention comprises a valve body for opening and closing a flow path, a movable core, and a magnetic core for attracting the movable core, and an electromagnetic valve inserted and fixed in an insertion hole. In the mechanism, a press-fit portion formed on the distal end side in the insertion direction and press-fit into the small-diameter insertion hole, and an outer circumferential portion having an outer diameter larger than the press-fit portion at the inlet side of the insertion direction than the press-fit portion. A clearance fitting portion which is formed with a predetermined clearance between the large diameter insertion hole having a larger diameter than the small diameter insertion hole, and the insertion on the inlet side of the clearance fitting portion in the insertion direction, And a weld welded to the member in which the hole is to be formed.

According to the present invention, it is possible to provide a solenoid valve mechanism or a high pressure fuel pump capable of improving assemblability by suppressing an increase in press-fit load when inserting and fixing in a hole formed in the pump body 1. Is possible. Other configurations, operations and effects of the present invention will be described in detail in the following embodiments.

The block diagram of the engine system to which the high pressure fuel pump of a present Example was applied is shown. It is a longitudinal cross-sectional view of the high pressure fuel pump of the Example of a present Example. It is the horizontal direction sectional view seen from the upper direction of the high pressure fuel pump of the Example of a present Example. It is the longitudinal cross-sectional view seen from the direction different from FIG. 1 of the high pressure fuel pump of the Example of a present Example. It is an enlarged longitudinal cross-sectional view of the solenoid valve mechanism of the high pressure fuel pump of a present Example, and the state which a solenoid valve mechanism is in the valve opening state is shown. It is a figure explaining the detail of the assembling method of the solenoid valve mechanism of a present Example. It is a schematic diagram of the welding part (joining part) of the solenoid valve mechanism of a present Example. It is a schematic diagram of the welding part (joining part) of the solenoid valve mechanism of a present Example by the structure different from FIG.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

The present embodiment relates to the structure of an electromagnetic suction valve mechanism that improves the assemblability of a high pressure fuel pump (high pressure fuel supply pump), particularly the electromagnetic suction valve mechanism.
FIG. 1 shows the overall configuration of the engine system. The portion surrounded by a broken line shows the main body of a high pressure fuel supply pump (hereinafter referred to as a high pressure fuel pump), and the mechanism / parts shown in the broken line are integrated into the pump body 1 Show. FIG. 1 is a diagram schematically showing the operation of the engine system, and the detailed configuration is different from the configuration of the high pressure fuel pump of FIG. FIG. 2 shows a longitudinal sectional view of the high pressure fuel pump of the present embodiment, and FIG. 3 is a horizontal sectional view of the high pressure fuel pump as viewed from above. FIG. 4 is a longitudinal sectional view of the high pressure fuel pump as viewed in a direction different from that of FIG. FIG. 5 is an enlarged view of the solenoid valve mechanism 300.

The fuel of the fuel tank 20 is pumped up by a feed pump 21 based on a signal from an engine control unit 27 (hereinafter referred to as an ECU). The fuel is pressurized to an appropriate feed pressure and sent through the suction pipe 28 to the low pressure fuel inlet 10a of the high pressure fuel pump.

The fuel that has passed through the suction joint 51 from the low pressure fuel suction port 10a reaches the suction port 31b of the solenoid valve mechanism 300 that constitutes the capacity variable mechanism through the damper chamber (10b, 10c) in which the pressure pulsation reduction mechanism 9 is disposed. . Specifically, the solenoid valve mechanism 300 constitutes a solenoid suction valve mechanism.

The fuel flowing into the solenoid valve mechanism 300 passes through the suction port opened and closed by the suction valve 30 and flows into the pressure chamber 11. A power to reciprocate the plunger 2 is given by the cam mechanism 93 of the engine. The reciprocating motion of the plunger 2 sucks the fuel from the suction valve 30 during the downward stroke of the plunger 2 and the fuel is pressurized during the upward stroke. The pressurized fuel is pressure-fed through the discharge valve mechanism 8 to the common rail 23 on which the pressure sensor 26 is mounted. Then, the injector 24 injects fuel to the engine based on the signal from the ECU 27. This embodiment is a high pressure fuel pump applied to 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 the desired fuel flow rate of the supplied fuel in response to a signal from the ECU 27 to the solenoid valve mechanism 300.

As shown in FIGS. 2 and 3, the high pressure fuel pump of the present embodiment is closely fixed to the high pressure fuel pump mounting portion 90 of the internal combustion engine. Specifically, as shown in FIG. 3, screw holes 1b are formed in a mounting flange 1a provided on the pump body 1, and a plurality of bolts (not shown) are inserted into the screw holes 1b. Thus, the mounting flange 1a is in close contact with and fixed to the high pressure fuel pump mounting portion 90 of the internal combustion engine. An O-ring 61 is fitted into the pump body 1 for sealing between the high pressure fuel pump mounting portion 90 and the pump body 1 to prevent engine oil from leaking outside.

As shown in FIGS. 2 and 4, a cylinder 6 is attached to the pump body 1 to guide the reciprocating movement of the plunger 2 and to form a pressure chamber 11 together with the pump body 1. That is, the plunger 2 reciprocates inside the cylinder to change the volume of the pressure chamber. A solenoid valve mechanism 300 for supplying fuel to the pressure chamber 11 and a discharge valve mechanism 8 for discharging fuel from the pressure chamber 11 to the discharge passage are provided.

The cylinder 6 is press-fit with the pump body 1 at its outer peripheral side. The pump body 1 is formed with an insertion hole for inserting the cylinder 6 from the lower side, and an inner peripheral convex portion deformed to the inner peripheral side to be in contact with the lower surface of the fixing portion 6a of the cylinder 6 at the lower end of the insertion hole Be done. The upper surface of the inner peripheral convex portion of the pump body 1 presses the fixing portion 6a of the cylinder 6 upward in the figure, 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. ing.

At the lower end of the plunger 2 is provided a tappet 92 which converts the rotational movement of the cam 93 attached to the camshaft of the internal combustion engine into vertical movement and transmits it to the plunger 2. The plunger 2 is crimped to the tappet 92 by a spring 4 through a retainer 15. As a result, the plunger 2 can be reciprocated up and down 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 installed in a state where the plunger seal 13 slidably contacts the outer periphery of the plunger 2 at the lower portion in the drawing of the cylinder 6. Thus, when the plunger 2 slides, the fuel in the sub chamber 7a is sealed to prevent the fuel from flowing into the internal combustion engine. At the same time, lubricating oil (including engine oil) for lubricating sliding parts in the internal combustion engine is prevented from flowing into the inside of the pump body 1.

As shown in FIGS. 3 and 4, a suction joint 51 is attached to the side surface of the pump body 1 of the high pressure fuel pump. The suction joint 51 is connected to a low pressure pipe that supplies fuel from the fuel tank 20 of the vehicle, and the fuel is supplied from here to the inside of the high pressure fuel pump. The suction filter 52 has a function of preventing foreign matter present between the fuel tank 20 and the low pressure fuel suction port 10a from being absorbed by the flow of fuel into the high pressure fuel pump.

The fuel that has passed through the low pressure fuel suction port 10a travels to the pressure pulsation reducing mechanism 9 through the low pressure fuel suction passage vertically connected to the pump body 1 shown in FIG. The pressure pulsation reducing mechanism 9 is disposed in the damper chamber (10b, 10c) between the damper cover 14 and the upper end surface of the pump body 1, and is supported from the lower side by a holding member 9a disposed on the upper end surface of the pump body 1. Ru. Specifically, the pressure pulsation reducing mechanism 9 is a metal damper configured by overlapping two metal diaphragms. A gas of 0.3 MPa to 0.6 MPa is enclosed inside the pressure pulsation reducing mechanism 9, and the outer peripheral edge portion is fixed by welding. Therefore, the outer peripheral edge portion is thin and configured to be thicker toward the inner peripheral side.

And as shown in FIG. 2, the convex part for fixing the outer-periphery edge part of the pressure pulsation reduction mechanism 9 from lower side is formed in the upper surface of the holding member 9a. On the other hand, on the lower surface of the damper cover 14, a convex portion for fixing the outer peripheral edge portion of the pressure pulsation reducing mechanism 9 from the upper side is formed. These convex portions are formed in a circular shape, and the pressure pulsation reducing mechanism 9 is fixed by being pinched by these convex portions. The damper cover 14 is pressed into and fixed to the outer edge of the pump body 1, but at this time, the holding member 9 a is elastically deformed to support the pressure pulsation reducing mechanism 9. Thus, damper chambers (10b, 10c) communicating with the low pressure fuel suction port 10a and the low pressure fuel suction passage are formed on the upper and lower surfaces of the pressure pulsation reducing mechanism 9, respectively. Although not shown in the figure, the holding member 9a is formed with a passage connecting the upper side and the lower side of the pressure pulsation reducing mechanism 9, whereby the damper chamber (10b, 10c) is a pressure pulsation reducing mechanism It is formed on the upper and lower surfaces of the reference numeral 9.

The fuel having passed through the damper chamber (10b, 10c) then reaches the suction port 31b of the solenoid valve mechanism 300 via the low pressure fuel suction passage 10d formed in vertical communication with the pump body. The suction port 31 b is formed in communication with the suction valve seat member 31 forming the suction valve seat 31 a in the vertical direction.

The solenoid valve mechanism 300 will be described in detail based on FIG. The coil portion includes a first yoke 42, an electromagnetic coil 43, a second yoke 44, a bobbin 45, a terminal 46, and a connector 47. A coil 43 in which a copper wire is wound around the bobbin 45 a plurality of times is disposed so as to be surrounded by the first yoke 42 and the second yoke 44, and molded and fixed integrally with a connector which is a resin member. The opposite ends of each of the two terminals 46 are electrically connected to both ends of the copper wire of the coil. Similarly, the terminal 46 is molded integrally with the connector, and the other end is connectable to the engine control unit side.

In the coil portion, the hole at the center of the first yoke 42 is press-fitted and fixed to the outer core 38. At that time, the inner diameter side of the second yoke 44 is configured to be in contact with the fixed core 39 or to be in close proximity to a slight clearance.

Both the first yoke 42 and the second yoke 44 are magnetic stainless steel materials in consideration of corrosion resistance in order to form a magnetic circuit, and the bobbin 45 and connector 47 use high strength heat resistant resin in consideration of strength characteristics and heat resistance characteristics. . The coil 43 is made of copper, and the terminal 46 is made of brass plated with metal.

Thus, when a magnetic circuit is formed by the outer core 38, the first yoke 42, the second yoke 44, the fixed core 39, and the anchor portion 36 and a current is applied to the coil, magnetic attraction is generated between the fixed core 39 and the anchor portion 36. Forces are generated and forces are drawn together. In the outer core 38, almost all of the magnetic flux passes between the fixed core 39 and the anchor portion 36 by making the axial direction portion where the fixed core 39 and the anchor portion 36 mutually generate magnetic attraction force as thin as possible. The magnetic attraction can be obtained efficiently.

The solenoid mechanism comprises a rod 35 which is a movable part, an anchor 36, a rod guide 37 which is a fixed part, an outer core 38, a fixed core 39, a rod biasing spring 40 and an anchor biasing spring 41.

The rod 35, which is a movable portion, and the anchor portion 36 are configured as separate members. The rod 35 is axially slidably held on the inner peripheral side of the rod guide 37, and the inner peripheral side of the anchor portion 36 is slidably held on the outer peripheral side of the rod 35. That is, both the rod 35 and the anchor portion 36 are axially slidable in a range that is geometrically restricted.

The anchor portion 36 has one or more through holes 36a penetrating in the axial direction of the component in order to move freely freely axially in the fuel, thereby eliminating the restriction of movement due to the pressure difference before and after the anchor portion as much as possible. .

The rod guide 37 is radially inserted into the inner peripheral side of the hole into which the suction valve of the pump body 1 is inserted, and is axially butted against one end of the suction valve seat. The pump body 1 is disposed so as to be sandwiched between the outer core 38 welded and fixed to the insertion hole of the pump body 1 and the pump body 1. Similar to the anchor portion 36, the rod guide 37 is also provided with a through hole 37a penetrating in the axial direction, and the pressure of the fuel chamber on the anchor portion side moves the anchor portion so that the anchor portion can move freely freely. It is configured not to disturb.

The outer core 38 has a thin-walled cylindrical shape on the opposite side of the portion to be welded to the pump body 1 and is fixed by welding so that the fixed core 39 is inserted on the inner peripheral side. A rod biasing spring 40 is disposed on the inner peripheral side of the fixed core 39 with the small diameter portion as a guide, the rod 35 contacts the suction valve 30, and the suction valve 30 is pulled away from the suction valve seat portion 31a, Apply biasing force in the valve opening direction.

The anchor biasing spring 41 is configured to apply a biasing force to the anchor 36 in the direction of the rod collar 35a while inserting the forward end into the cylindrical central bearing 37b provided on the center side of the rod guide 37 and maintaining the same axis. And The moving amount 36 e of the anchor portion 36 is set larger than the moving amount 30 e of the suction valve 30. This is to ensure that the suction valve 30 closes.

As shown in FIG. 3, the discharge valve mechanism 8 is provided at the outlet of the pressure chamber 11. The discharge valve mechanism 8 comprises a discharge valve seat 8a, a discharge valve 8b contacting and separating with the discharge valve seat 8a, and a discharge valve 8b. The discharge valve spring 8c is biased toward the seat 8a, and the discharge valve stopper 8d determines the stroke (moving distance) of the discharge valve 8b. The discharge valve stopper 8d and the pump body 1 are joined by welding at the contact portion 8e to block the fuel from the outside.

In the state where there is no fuel pressure difference between the pressurizing chamber 11 and the discharge valve chamber 12a, the discharge valve 8b is crimped to the discharge valve seat 8a by the biasing force of the discharge valve spring 8c and is in a closed state. Only when the fuel pressure in the pressure chamber 11 becomes higher than the fuel pressure in the discharge valve chamber 12a, the discharge valve 8b opens against the discharge valve spring 8c. The high pressure fuel in the pressure chamber 11 is discharged to the common rail 23 through the discharge valve chamber 12 a, the fuel discharge passage 12 b, and the fuel discharge port 12. When the discharge valve 8 b is opened, the discharge valve 8 b contacts the discharge valve stopper 8 d and the stroke is limited. Therefore, the stroke of the discharge valve 8b is appropriately determined by the discharge valve stopper 8d. As a result, the stroke is too large, and it is possible to prevent the fuel discharged to a high pressure into the discharge valve chamber 12a from flowing back into the pressure chamber 11 again due to the delay of closing the discharge valve 8b. Can be suppressed. Further, when the discharge valve 8b repeats opening and closing motions, 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. By doing as described above, the discharge valve mechanism 8 serves as a check valve that restricts the flow direction of the fuel.

As described above, the pressurizing chamber 11 is configured by the pump body 1, the solenoid valve mechanism 300, the plunger 2, the cylinder 6, and the discharge valve mechanism 8.

FIG. 5 shows a detailed configuration of the solenoid valve mechanism 300. As shown in FIG. When the plunger 2 moves in the direction of the cam 93 and is in the suction stroke state by the rotation of the cam 93, the volume of the pressurizing chamber 11 increases and the fuel pressure in the pressurizing chamber 11 decreases. When the fuel pressure in the pressure chamber 11 becomes lower than the pressure of the suction port 31b in this stroke, the suction valve 30 is opened. 30e indicates the maximum opening degree, and at this time, the suction valve 30 contacts the stopper 32. Opening of the suction valve 30 opens the opening 31 c formed in the seat member 31. The fuel passes through the opening 31 c and flows into the pressurizing chamber 11 through the hole 1 c formed in the pump body 1 in the lateral direction. The hole 1 c also constitutes a part of the pressure chamber 11.

After the plunger 2 completes the suction stroke, the plunger 2 turns upward and shifts to the upward stroke. Here, the electromagnetic coil 43 remains in the non-energized state, and the magnetic bias does not act. The rod biasing spring 40 biases the rod convex portion 35a which is convex on the outer diameter side of the rod 35, and is set to have a biasing force necessary and sufficient to open the suction valve 30 in the non-energized state. There is. The volume of the pressure chamber 11 decreases with the upward movement of the plunger 2. In this state, the fuel once sucked into the pressure chamber 11 is again sucked through the opening 30a of the suction valve 30 in the open state. Since the flow is returned to the passage 10d, the pressure in the pressure chamber does not rise. This process is called a return process.

In this state, when a control signal from the engine control unit 27 (hereinafter referred to as an ECU) is applied to the solenoid valve mechanism 300, a current flows in the solenoid coil 43 through the terminal 46. A magnetic attraction force acts between the magnetic core 39 and the anchor 36, and the magnetic core 39 and the anchor 36 contact on the magnetic attraction surface S. The magnetic attraction force overcomes the biasing force of the rod biasing spring 40 to bias the anchor 36, and the anchor 36 engages with the rod projection 35a to move the rod 35 away from the suction valve 30.

At this time, the suction valve 30 is closed by the biasing force of the suction valve biasing spring 33 and the fluid force caused by the fuel flowing into the suction passage 10d. After the valve is closed, the fuel pressure in the pressure chamber 11 rises with the upward movement of the plunger 2, and when the pressure in the fuel outlet 12 becomes higher than that, the high pressure fuel is discharged through the discharge valve mechanism 8 to the common rail 23. Supplied. This stroke is called a discharge stroke.

That is, the upward stroke from the lower start point to the upper start point of the plunger 2 consists of a return stroke and a discharge stroke. Then, by controlling the energization timing of the coil 43 of the solenoid valve mechanism 300, it is possible to control the amount of high pressure fuel to be discharged. If the timing for energizing the electromagnetic coil 43 is advanced, the proportion of the return stroke during the compression stroke is small, and the proportion of the discharge stroke is large. That is, the amount of fuel returned to the suction passage 10d is small, and the amount of fuel discharged at high pressure is large. On the other hand, if the timing of energizing is delayed, the proportion of the return stroke during the compression stroke is large, and the proportion of the discharge stroke is small. That is, the amount of fuel returned to the suction passage 10d is large, and the amount of fuel discharged at high pressure is small. The energization timing of the electromagnetic coil 43 is controlled by a command from the ECU 27. As described above, by controlling the energization timing of the electromagnetic coil 43, the amount of high-pressure discharged fuel can be controlled to the amount required by the internal combustion engine.

A pressure pulsation reducing mechanism 9 is provided in the low pressure damper chamber (10b, 10c) for reducing the pressure pulsation generated in the high pressure fuel pump from spreading to the fuel pipe 28. In the case where the fuel that has once flowed into the pressurizing chamber 11 is returned to the suction passage 10d through the suction valve 30 that is in the open state again for volume control, pressure pulsation is generated in the low pressure fuel chamber 10 by the fuel returned to the suction passage 10d. Occurs. However, the pressure pulsation reducing mechanism 9 provided in the low pressure fuel chamber 10 is formed by a metal diaphragm damper in which two corrugated disc-like metal plates are laminated at their outer periphery and an inert gas such as argon is injected therein. 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 movement of the plunger. The sub chamber 7a is in communication with the damper chamber (10b, 10c) by the fuel passage 10e. When the plunger 2 is lowered, a flow of fuel is generated from the auxiliary chamber 7a to the damper chamber (10b, 10c), and when raised, from the damper chamber (10b, 10c) to the auxiliary chamber 7a.

As a result, the flow rate of fuel into and out of the pump in the suction stroke or return stroke of the pump can be reduced, and the pressure pulsation generated inside the high pressure fuel pump can be reduced.

Next, the relief valve mechanism 200 shown in FIGS. 2 and 3 will be described.
The relief valve mechanism 200 includes a relief body 201, a relief valve 202, a relief valve holder 203, a relief spring 204, and a spring stopper 205. The relief body 201 is provided with a tapered seat portion. The load of the relief spring 204 is loaded through the valve holder 203, and the valve 202 is pressed against the seat portion of the relief body 201 and cooperates with the seat portion to shut off the fuel. The valve opening pressure of the relief valve 202 is determined by the load of the relief spring 204. The spring stopper 205 is press-fitted and fixed to the relief body 201, and is a mechanism that adjusts the load of the relief spring 204 depending on the position of the press-fitting.

Here, when the fuel in the pressure chamber 11 is pressurized and the discharge valve 8b is opened, the high pressure fuel in the pressure chamber 11 passes through the discharge valve chamber 12a and the fuel discharge passage 12b, and from the fuel discharge port 12 It is discharged. The fuel discharge port 12 is formed in a discharge joint 60, and the discharge joint 60 is welded and fixed to the pump body 1 at a welding portion 61 to secure a fuel passage.
When the pressure of the fuel discharge port 12 becomes abnormally high pressure due to a failure of the electromagnetic suction valve 300 of the high pressure fuel pump, etc. and becomes larger than the set pressure of the relief valve mechanism 200, the abnormally high pressure fuel is on the low pressure side via the relief passage 213 The damper chamber 10c is relieved.

Hereinafter, the detailed configuration of the solenoid valve mechanism 300 of the present embodiment will be described with reference to FIG. 5 and FIG. In this embodiment, it is an object of the present invention to provide a high pressure fuel pump provided with a solenoid valve mechanism 300 for achieving a high flow rate and a large flow rate, wherein the assemblability is improved by suppressing the occurrence of assembly defects.

The solenoid valve mechanism 300 is housed in the housing hole 100 provided in the pump body 1 in a three-stage configuration. In the suction valve sheet member 31 of the solenoid valve mechanism 300, a first outer peripheral portion 301 is formed on the tip end side in the insertion direction, and a second outer peripheral portion 302 is formed on the inlet side in the insertion direction than the first outer peripheral portion 301 and on the outer diameter side. Here, the inner peripheral portion of the outer core 38 is press-fit and fixed to the outer peripheral portion of the rod guide 37 of the suction valve sheet member 31 to be integrated. In addition, a third outer peripheral portion 303 is formed on the outer core 38 further to the entrance side in the insertion direction than the second outer peripheral portion 302. Similarly, the housing hole 100 has a first inner peripheral portion 101 on the tip end side of the electromagnetic valve mechanism 300 in the insertion direction, an inlet side on the insertion direction than the first inner peripheral portion 101, and a second inner peripheral portion 102 on the outer diameter side. A third inner circumferential portion 103 is provided further in the insertion direction inlet side than the circumferential portion 102.

In the present embodiment, the first outer peripheral portion 301 of the solenoid valve mechanism 300 is press-fit into the first inner peripheral portion 101. In addition, the second outer peripheral portion 302 is fitted with a gap on the second inner peripheral portion 102. In addition, the third outer peripheral portion 303 is gap-fitted to the third inner peripheral portion 103 and then fixed by welding.

As described above, the solenoid valve mechanism 300 according to the present embodiment includes the valve body (intake valve 30) for opening and closing the flow path, the movable core (anchor portion 36), and the magnetic core (spinned for attracting the movable core (anchor portion 36) And a core 39), and inserted and fixed to the insertion hole (receiving hole 100). And the solenoid valve mechanism 300 is formed in the outer peripheral part at the front end side of an insertion direction, and has a press-fit part (1st outer peripheral part 301) press-fit with respect to a small diameter insertion hole (1st inner peripheral part 101). Further, the electromagnetic valve mechanism 300 has an outer peripheral portion (second outer peripheral portion 302) having an outer diameter larger than that of the press-in portion (first outer peripheral portion 301) on the inlet side in the insertion direction than the press-in portion (first outer peripheral portion 301). A clearance fitting portion (having a predetermined gap with the large diameter insertion hole (second inner circumferential portion 102) having a larger diameter than the small diameter insertion hole (first inner circumferential portion 101) It has a second outer peripheral portion 302). Furthermore, the electromagnetic valve mechanism 300 is welded to a member (pump body 1) in which the insertion hole (housing hole 100) is formed on the inlet side in the insertion direction than the gap fitting portion (second outer peripheral portion 302) Part (third outer peripheral part 303).

Here, it is assumed that all of the first outer peripheral portion 301, the second outer peripheral portion 302, and the third outer peripheral portion 303 of the solenoid valve mechanism 300 are fixed to the pump body 1 by press fitting. As described above, when the press-fit portion is three-tiered, the axial center of the first-stage press-fit member is eccentric to the axial centers of the second and third stages. As a result, the inventors of the present invention have found that there is a problem that the press-in interference in the second and third stages is increased, and a press-in failure occurs. On the other hand, according to the configuration of the above-described embodiment, such problems can be solved, the occurrence of assembly defects can be suppressed, and the assemblability can be improved.

A gap formed by the second outer peripheral portion 302 and the second inner peripheral portion 102 and a gap formed by the third outer peripheral portion 303 and the third inner peripheral portion 103 are the first outer peripheral portion 301 and the first inner peripheral portion. Even when eccentric with respect to the central axis of the portion 101, the gap is set to be 0 or more. With such a configuration, contact between the second outer peripheral portion 302 and the second inner peripheral portion 102 and between the third outer peripheral portion 303 and the third inner peripheral portion 103 can be suppressed, and the solenoid valve mechanism 300 It is possible to improve the assemblability without the occurrence of galling when press-fitting into the housing hole 100.

The first outer peripheral portion 301 of the suction valve sheet member 31 is formed in parallel to the insertion direction up to the second outer peripheral portion 302, and forms a fuel passage 10f with the second inner peripheral portion 102. The fuel passage 10f is formed in the entire circumferential direction.

That is, in the present embodiment, the outer peripheral portion (first outer peripheral portion 301) where the press-fit portion (first outer peripheral portion 301) is formed is formed in parallel with the insertion direction until it reaches the clearance fitting portion (second outer peripheral portion 302). On the outer peripheral side of the outer peripheral portion (first outer peripheral portion 301), the insertion direction front end portion of the clearance fitting portion (second outer peripheral portion 302) and the insertion direction front end portion 102a of the large diameter insertion hole (second inner peripheral portion 102) And a flow passage (fuel passage 10f) is formed therebetween. The outer diameter of the clearance fitting portion (second outer peripheral portion 302) is larger than the outer diameter of the press-fit portion (first outer peripheral portion 301) by 0.1 mm or more. Further, the flow passage (the fuel passage 10f) is formed in the entire circumferential direction on the outer peripheral side of the outer peripheral portion (first outer peripheral portion 301) where the press-fit portion (first outer peripheral portion 301) is formed. This makes it possible to secure the fuel passage.

The first outer peripheral portion 301 and the second outer peripheral portion 302 are formed on the suction valve sheet member 31 and are formed of the same member. That is, the press-fit portion (first outer peripheral portion 301) and the gap fitting portion (second outer peripheral portion 302) are integrally configured by the same member. The outer core 38 having the third outer peripheral portion 303 to be fixed by welding is a separate member from the suction valve seat member 31. The outer peripheral portion 31c of the suction valve seat member 31 is press-fit into the inner peripheral portion 38a of the outer core 38 Be done. That is, the same member (the suction valve sheet member 31) described above and the welding member (the outer core 38) in which the welding portion (the third outer peripheral portion 303) is formed are configured separately. A press-fit portion which is press-fit to the outer peripheral portion 31c of the same member (suction valve sheet member 31) is formed on the inner peripheral portion 38a of the welding member (outer core 38).

The outer peripheral portion 31 c of the sheet member 31 is located on the inner diameter side of the first outer peripheral portion 301. A press-fit portion (inner circumferential portion 38a) pressed into the outer circumferential portion of the same member (suction valve sheet member 31) by the inner circumferential portion 38a of the welding member (outer core 38) has a small diameter insertion hole (first inner circumferential portion). It is located radially inward of a press-fit portion (first outer circumferential portion 301) which is press-fit into the portion 101). Since the suction valve seat member 31 and the outer core 38 are separate structures, the stroke adjustment member 50 of the rod 35 can be inserted between the suction valve seat member 31 and the outer core 38. Therefore, the stroke variation of the rod 35 can be reduced, and the product quality can be ensured.

The third outer peripheral portion 303 of the suction valve sheet member 31 and the third inner peripheral portion 103 of the accommodation hole 100 are welded by laser irradiation from the insertion direction side of the electromagnetic valve mechanism 300. The welded portion (third outer peripheral portion 303) is formed by laser irradiation along the insertion direction with respect to the large diameter insertion hole (second inner peripheral portion 102). At this time, the spatter by laser welding intrudes into the inside of the pump body 1, but is accommodated in the space 104 of the accommodation hole 100. That is, in the electromagnetic valve mechanism 300, the sputter capture hole 104 is formed between the gap fitting portion (second outer peripheral portion 302) and the welding portion (third outer peripheral portion 303) in the insertion direction.

The gap between the second outer peripheral portion 302 and the large diameter insertion hole (second inner peripheral portion 102) is set to be smaller than the stroke amount (30e) of the suction valve 30 or the stroke amount (not shown) of the discharge valve 8b There is. That is, the solenoid valve mechanism 300 of the present embodiment includes the rod 35 for urging the valve body (intake valve 30) in the valve opening direction, and the same member (intake valve seat member 31) A seat portion on which the seat 30 is seated is formed, and a guide portion 37 for guiding the outer peripheral portion of the rod 35 is formed. Then, the above-described predetermined gap is configured to be smaller than the maximum lift amount of the valve body (the suction valve 30). Further, the high pressure fuel pump of the present embodiment is provided with the solenoid valve mechanism 300 and the discharge valve mechanism 8, and the above-described predetermined gap is configured to be smaller than the maximum lift amount of the discharge valve 8 b of the discharge valve mechanism 8. . Thereby, the influence on the high pressure fuel pump operation can be suppressed.

FIG. 7 shows a schematic view of the third outer peripheral portion 303 of the outer core 38 and the third inner peripheral portion 303 of the pump body 1. As described above, the gap C is formed between the third outer peripheral portion 303, which is a welded portion, and the third inner peripheral portion 303. When welding, the outer core 38 and the molten metal of the pump body 1 flow into the gap C, but if the volume of the gap C can not be satisfied, there is a possibility that the weld portion 138 may cause a weld dent d. The theoretical welding length L is calculated by the overlapping length of the third outer peripheral portion 303 and the third inner peripheral portion 103, but the actual welding length La is a value obtained by subtracting the welding depth d from the welding length L Become. Therefore, the overlapping length of the third outer peripheral portion 303 and the third inner peripheral portion 103 may be set so that the welding length satisfying the necessary strength is the actual welding length La.

FIG. 8 shows a structure for welding with a laser with a configuration different from that of FIG. As shown in FIG. 8, a step D may be provided on the welding laser irradiation side of the third outer peripheral portion 303 of the outer core 38 and the third inner peripheral portion 303 of the pump body 1. Since the molten metal of the volume of the corner portion 103c of the outer core 38 can be made to flow into the gap C at the time of welding, it is possible to prevent the occurrence of the welding dent d in the welding portion 138. Therefore, it is possible to consider the theoretical welding length L as the actual welding length La.

According to the above-described invention, it is possible to supply a high-pressure fuel pump with improved assemblability by suppressing occurrence of assembly failure of the solenoid valve mechanism in the solenoid valve mechanism achieving high speed and large flow rate.

DESCRIPTION OF SYMBOLS 1 ... pump body, 2 ... plunger, 8 ... discharge valve mechanism, 9 ... pressure pulsation reduction mechanism, 11 ... pressurization chamber, 12 ... fuel discharge port, 30 ... valve body (intake valve), 31 ... suction valve sheet member, 31c: outer periphery of suction valve seat member 36: movable core (anchor portion) 38: welding member (outer core) 39: magnetic core (fixed core 39) 100: insertion hole (housing hole) 101: small diameter Insertion hole (first inner circumferential portion) 102: second inner circumferential portion 103: third inner

circumferential portion

103, 300 electromagnetic valve mechanism 301: press-fit portion (first outer circumferential portion) 302: clearance fitting portion Second outer peripheral portion), 303 ... welded portion (third outer peripheral portion)

Claims

An electromagnetic valve mechanism comprising a valve body for opening and closing a flow path, a movable core, and a magnetic core for attracting the movable core, wherein the electromagnetic valve mechanism is inserted and fixed to the insertion hole,
A press-fit portion which is formed on the outer periphery at the tip end side in the insertion direction and which is press-fit into the small diameter insertion hole
It is formed on the inlet side in the insertion direction than the press-fit portion, and is formed on the outer peripheral portion having a larger outer diameter than the press-fit portion, and has a predetermined gap between it and the large diameter insertion hole having a larger diameter than the small diameter insertion hole. A clearance fit portion to be disposed,
An electromagnetic valve mechanism comprising a welded portion welded to a member in which the insertion hole is formed on the inlet side in the insertion direction than the gap fitting portion;
In the solenoid valve mechanism according to claim 1,
An outer peripheral portion on which the press-fit portion is formed is formed in parallel with the insertion direction until the gap fitting portion is reached,
An electromagnetic valve mechanism in which a flow passage is formed on the outer peripheral side of the outer peripheral portion between the insertion direction distal end portion of the clearance fitting portion and the insertion direction inlet portion of the large diameter insertion hole.
In the solenoid valve mechanism according to claim 1,
An electromagnetic valve mechanism in which the press-fit portion and the clearance fit portion are integrally formed of the same member.
In the solenoid valve mechanism according to claim 3,
The same member and the welding member in which the welding portion is formed are formed as separate members, and a press-fit portion is formed on the inner peripheral portion of the welding member to be pressed into the outer peripheral portion of the same member. Solenoid valve mechanism.
In the solenoid valve mechanism according to claim 4,
An electromagnetic valve mechanism in which a press-fit portion pressed into the outer peripheral portion of the same member at an inner peripheral portion of the welding member is located radially inward of a press-fit portion pressed into the small diameter insertion hole.
In the solenoid valve mechanism according to claim 1,
The electromagnetic valve mechanism formed by the laser irradiation of the said welding part along the insertion direction with respect to the said large diameter insertion hole.
In the solenoid valve mechanism according to claim 1,
An electromagnetic valve mechanism in which a spatter capture hole is formed between the clearance fitting portion and the welding portion in the insertion direction.
In the solenoid valve mechanism according to claim 2,
The solenoid valve mechanism formed in the whole circumferential direction on the outer peripheral side of the outer peripheral portion where the press-fit portion is formed.
In the solenoid valve mechanism according to claim 3,
A rod for biasing the valve body in a valve opening direction;
An electromagnetic valve mechanism in which a seat portion on which the valve body is seated is formed on the same member, and a guide portion for guiding an outer peripheral portion of the rod is formed.
In the solenoid valve mechanism according to claim 1,
The electromagnetic valve mechanism in which the outer diameter of the said clearance gap fitting part was formed 0.1 mm or more in diameter large with respect to the outer diameter of the said press-fit part.
The electromagnetic valve mechanism according to claim 1, wherein the predetermined gap is smaller than a maximum lift amount of the valve body.
A high-pressure fuel pump comprising the solenoid valve mechanism according to claim 1 and a discharge valve mechanism,
The high pressure fuel pump, wherein the predetermined gap is smaller than the maximum lift amount of the discharge valve of the discharge valve mechanism.