WO2020090371A1

WO2020090371A1 - Fuel pump

Info

Publication number: WO2020090371A1
Application number: PCT/JP2019/039577
Authority: WO
Inventors: 雅史根本; 悟史臼井; 斉藤　淳治
Original assignee: 日立オートモティブシステムズ株式会社
Priority date: 2018-10-31
Filing date: 2019-10-08
Publication date: 2020-05-07
Also published as: JPWO2020090371A1; JP7110384B2

Abstract

According to the present invention, a magnetic circuit of a solenoid valve is made compact and has a structure that efficiently generates a magnetic force, and both miniaturization and low costs thereof are achieved. To this end, a fuel pump according to the present invention comprises: a fixed core that suctions a movable core through a magnetic suction force generated by conducting a coil; a spring member that is disposed in a recess part formed in the inner diameter side of the fixed core and biases a rod driven by the movable core; and a magnetic member that is disposed on the outer peripheral side of the coil and forms a magnetic circuit, wherein an axial outer spring end surface of the spring member is disposed axially outward of an axial outer end surface of the magnetic member.

Description

Fuel pump

The present invention relates to vehicle parts, and more particularly to a fuel pump that supplies high pressure fuel to an engine.

In a direct injection engine that directly injects fuel into a combustion chamber of an engine (internal combustion engine) of an automobile or the like, a high-pressure fuel supply pump for increasing the pressure of fuel is widely used. As a conventional technique of this high-pressure fuel supply pump, for example, there is one disclosed in Japanese Unexamined Patent Application Publication No. 2018-087548 (Patent Document 1). In Patent Document 1, "High-pressure provided with an intake valve mechanism 300 having an intake valve 30 for opening and closing a flow path on the upstream side of the pressurizing chamber 11 and an electromagnetic coil 43 for controlling the opening and closing of the intake valve 30. In the fuel supply pump, a groove 39c formed in the intake valve mechanism 300, and a fixing member (annular member 47) for fixing the yoke (second yoke 44) constituting the magnetic circuit by being inserted and fixed in the groove 39c. Was disclosed. ”(See summary).

JP, 2008-087548, A

The fuel pump is installed in a narrow space inside the engine, so it is desirable to be as small as possible. The suction valve mechanism 300 is a mechanism that is inserted into the pump body from the outside in the radial direction, and is a mechanism that projects outward in the radial direction of the pump body. Therefore, an object of the present invention is to shorten the length of the electromagnetic suction valve mechanism, particularly in the axial direction, and to reduce the size of the fuel pump.

In order to solve the above-mentioned problems, the fuel pump of the present invention is arranged in a fixed core that attracts a movable core by a magnetic attraction force generated by energizing a coil, and a recess formed on the inner diameter side of the fixed core. A spring member for urging the rod driven by the movable core, and a magnetic member arranged on the outer peripheral side of the coil to form a magnetic circuit, and the axially outer spring end surface of the spring member is The magnetic member is arranged axially outside of the axially outer end surface.

According to the present invention having such a configuration, it is possible to shorten the length of the electromagnetic suction valve mechanism, particularly in the axial direction, and to downsize the fuel pump. The configuration, action, and effect of the present invention other than those described above will be described in detail in the following embodiments.

The block diagram of the engine system to which the fuel pump was applied is shown. It is a longitudinal cross-sectional view of a fuel pump. It is a horizontal direction sectional view seen from the upper part of a fuel pump. FIG. 3 is a vertical cross-sectional view of the fuel pump seen from a different direction from FIG. 2. It is an axial sectional view for explaining electromagnetic suction valve mechanism 3 of an example of the present invention. It is the drawing which expanded the electromagnetic suction valve mechanism 3 of the Example of this invention. It is the drawing which decomposed | disassembled and showed the main components of the electromagnetic suction valve mechanism 3 of the Example of this invention.

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

First, an embodiment of the present invention will be described in detail with reference to FIGS. The configuration and operation of the system will be described using the overall configuration diagram of the engine system shown in FIG. The part surrounded by the broken line shows the main body of the high-pressure fuel supply pump (hereinafter referred to as the fuel pump), and the mechanism and parts shown in the broken line are integrated with the body 1 (may be called the pump body). Indicates that it is installed.

The fuel in the fuel tank 103 is pumped up from the fuel tank 103 by the feed pump 102 based on a signal from the engine control unit 101 (hereinafter referred to as ECU). This fuel is pressurized to an appropriate feed pressure and sent to the low-pressure fuel intake port 10a of the fuel pump through the fuel pipe 104.

The fuel that has flowed in from the low-pressure fuel intake port 10a of the intake pipe 5 (not shown in FIG. 1) reaches the intake port 3k of the electromagnetic intake valve mechanism 3, which is a variable capacity mechanism, via the pressure pulsation reducing mechanism 9 and the intake passage 10d. ..

The fuel flowing into the electromagnetic suction valve mechanism 3 passes through the suction valve 3b, flows through the suction passage 1a formed in the body 1, and then flows into the pressurizing chamber 11. Power for reciprocating motion is applied to the plunger 2 by the cam mechanism 91 of the engine. Due to the reciprocating motion of the plunger 2, fuel is sucked from the suction valve 3b during the downward stroke of the plunger 2 and pressurized during the upward stroke. When the pressure in the pressurizing chamber 11 exceeds the set value, the discharge valve mechanism 8 opens and high-pressure fuel is pressure-fed to the common rail 106 on which the pressure sensor 105 is mounted. Then, based on the signal from the ECU 101, the injector 107 injects fuel into the engine. The present embodiment is a fuel pump applied to a so-called direct injection engine system in which the injector 107 injects fuel directly into the cylinder of the engine. The fuel pump discharges a desired fuel flow rate of the supplied fuel in response to a signal from the ECU 101 to the electromagnetic suction valve mechanism 3.

FIG. 2 is a vertical cross-sectional view of the fuel pump of this embodiment as seen in a vertical cross section, and FIG. 3 is a horizontal cross-sectional view of the fuel pump as seen from above. FIG. 4 is a vertical cross-sectional view of the fuel pump as viewed in a vertical direction different from that of FIG. The fuel pump of this embodiment uses a mounting flange 1e (FIG. 3) provided on the body 1 to be in close contact with a fuel pump mounting portion 90 (FIGS. 2 and 4) of an engine (internal combustion engine) and fixed with a plurality of bolts (not shown). To be done.

As shown in FIGS. 2 and 4, an O-ring 93 is fitted into the body 1 for a seal between the fuel pump mounting portion 90 and the body 1 to prevent engine 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 body 1 is attached to the body 1. Further, an electromagnetic suction valve mechanism 3 for supplying fuel to the pressurizing chamber 11 and a discharge valve mechanism 8 for discharging fuel from the pressurizing chamber 11 to the discharge passage are provided.

The cylinder 6 is press-fitted with the body 1 on the outer peripheral side. Further, by deforming the body 1 to the inner peripheral side (inward in the radial direction), the fixing portion 6a of the cylinder 6 is pressed upward in the drawing, and the fuel pressurized in the pressurizing chamber 11 at the upper end surface of the cylinder 6 is released. Sealed to prevent leakage to the low pressure side. That is, the pressurizing chamber 11 is composed of the body 1, the electromagnetic suction valve mechanism 3, the plunger 2, the cylinder 6, and the discharge valve mechanism 8.

At the lower end of the plunger 2, there is provided a tappet 92 that converts the rotational movement of a cam 91 attached to the camshaft of the engine into vertical movement and transmits it to the plunger 2. The plunger 2 is pressed against the tappet 92 by the spring 18 via the retainer 15. This allows the plunger 2 to reciprocate up and down with the rotational movement of the cam 91.

The plunger seal 13 held at the lower end of the inner circumference of the seal holder 7 is installed in a slidable contact with the outer circumference of the plunger 2 at the lower part of the cylinder 6 in the figure. As a result, when the plunger 2 slides, the fuel in the sub chamber 7a is sealed and prevented from flowing into the engine. At the same time, it prevents lubricating oil (including engine oil) that lubricates sliding parts in the engine from flowing into the body 1.

The relief valve mechanism 4 shown in FIGS. 2 and 3 includes a seat member 4e, a relief valve 4d, a relief valve holder 4c, a relief spring 4b, and a spring support member 4a. The spring support member 4a also functions as a relief body that contains the relief spring 4b and forms a relief valve chamber. The spring support member 4a (relief body) of the relief valve mechanism 4 is press-fitted and fixed in the lateral hole formed in the body 1. One end of the relief spring 4b is in contact with the spring support member 4a and the other end is in contact with the relief valve holder 4c. The relief valve 4d shuts off the fuel by the urging force of the relief spring 4b acting via the relief valve holder 4c and being pressed against the relief valve seat (seat member 4e). The valve opening pressure of the relief valve 4d is determined by the urging force of the relief spring 4b. In the present embodiment, the relief valve mechanism 4 communicates with the pressurizing chamber 11 via the relief passage, but is not limited to this, and communicates with the low pressure passage (the low pressure fuel chamber 10 or the suction passage 10d, etc.). It may be done. The relief valve mechanism 4 is a valve configured to operate when a problem occurs in the common rail 106 or a member ahead of the common rail 106 and the common rail 106 becomes abnormally high in pressure.

That is, the relief valve mechanism 4 is configured to open the relief valve 4d against the biasing force of the relief spring 4b when the differential pressure between the upstream side and the downstream side of the relief valve 4d exceeds the set pressure. It It has a role of opening the valve when the pressure in the common rail 106 or a member beyond it becomes high and returning the fuel to the pressurizing chamber 11 or the low pressure passage (the low pressure fuel chamber 10 or the suction passage 10d). 2 and 3 show a structure in which the relief valve mechanism 4 returns to the pressurizing chamber 11 when the valve is opened. Therefore, it is necessary to maintain the valve closed state at a predetermined pressure or less, and a very strong relief spring 4b is provided to counter the high pressure.

As shown in FIGS. 3 and 4, a suction pipe 5 is attached to the side surface of the body 1. The intake pipe 5 is connected to a low-pressure pipe 104 that supplies fuel from a fuel tank 103 of the vehicle, and the fuel is supplied from here to the inside of the fuel pump. The suction filter 17 in the suction passage 5a at the tip of the suction pipe 5 prevents foreign matter existing between the fuel tank 103 and the low-pressure fuel suction port 10a from being absorbed into the fuel pump by the flow of fuel. The fuel that has passed through the low-pressure fuel intake port 10a reaches the intake port 3k of the electromagnetic intake valve mechanism 3 via the pressure pulsation reducing mechanism 9 and the low-pressure fuel flow path 10d (see FIG. 2).

When the plunger 2 moves in the direction of the cam 91 due to the rotation of the cam 91, the volume of the pressurizing chamber 11 increases and the fuel pressure in the pressurizing chamber 11 decreases. In the intake stroke, the electromagnetic coil 3g is in the non-energized state, and the rod urging spring 3 urges the rod 3i in the valve opening direction (rightward in FIGS. 3 and 4), so that the tip of the rod 3i moves the movable core. Energize 3h. In this process, when the fuel pressure in the pressurizing chamber 11 becomes lower than the pressure in the suction port 3k, and the biasing force of the rod biasing spring 3 becomes larger than the differential pressure across the suction valve 3b, the suction valve 3b becomes The valve is opened from the seat portion 3a. As a result, the fuel flows into the pressurizing chamber 11 through the opening 3f of the intake valve 3b. The rod 3i urged by the rod urging spring 3 collides with the stopper 3n and its operation in the valve opening direction is restricted.

After the plunger 2 finishes the inhalation stroke, the plunger 2 starts to move up and moves to the upstroke. Here, the electromagnetic coil 3g remains in the non-energized state, and the magnetic biasing force does not act. The rod urging spring 3m is set so as to have a urging force necessary and sufficient for keeping the intake valve 3b open in the non-energized state. The volume of the pressurizing chamber 11 decreases with the compressive movement of the plunger 2. In this state, the fuel once sucked into the pressurizing chamber 11 is sucked again through the opening 3f of the intake valve 3b in the valve open state. Since it is returned to the passage 10d, the pressure in the pressurizing chamber does not rise. This process is called a return process.

In this state, when a control signal from the engine control unit 101 (hereinafter referred to as ECU) is applied to the electromagnetic suction valve mechanism 3, a current flows through the electromagnetic coil 3g via the terminal 16. When a current flows through the electromagnetic coil 3g, a magnetic attraction force acts between the fixed core 3e (magnetic core) and the movable core 3h, and the fixed core 3e and the movable core 3h come into contact with each other on the magnetic attraction surface. The magnetic attraction force overcomes the urging force of the rod urging spring 3m to urge the movable core 3h, and the movable core 3h engages with the rod protrusion 3j to move the rod 3i in the direction away from the suction valve 3b.

Therefore, the suction valve 3b is closed by the urging force of the suction valve urging spring 3l and the fluid force of the fuel flowing into the suction passage 10d. After the valve is closed, the fuel pressure in the pressurizing chamber 11 rises with the ascending movement of the plunger 2, and when the pressure becomes equal to or higher than the pressure of the fuel discharge port 12a, the high pressure fuel is discharged through the discharge valve mechanism 8 to the common rail 106. Supplied. This process is called a discharge process. The discharge joint 12 is inserted into the lateral hole of the body 1, and the fuel discharge port 12a is formed by the internal space of the discharge joint 12. The discharge joint 12 is fixed to the lateral hole of the body 1 by welding at the welded portion 12b.

That is, the ascending stroke from the lower start point to the upper start point of the plunger 2 consists of the return stroke and the discharge stroke. Then, by controlling the timing of energizing the coil 3g of the electromagnetic suction valve mechanism 3, the amount of high-pressure fuel discharged can be controlled. If the timing of energizing the electromagnetic coil 3g is advanced, the proportion of the return stroke during the ascending stroke is small and the proportion of the discharge stroke is large. That is, less fuel is returned to the suction passage 10d, and more fuel is discharged under high pressure. On the other hand, if the timing of energization is delayed, the proportion of the return stroke is large and the proportion of the discharge stroke is small during the rising stroke. That is, much fuel is returned to the suction passage 10d, and less fuel is discharged under high pressure. The timing of energizing the electromagnetic coil 3g is controlled by a command from the ECU 101.

By controlling the energization timing to the electromagnetic coil 3g as described above, the amount of fuel discharged at high pressure can be controlled to the amount required by the engine. The discharge valve mechanism 8 on the outlet side of the pressurizing chamber 11 of the body 1 includes a discharge valve seat 8a, a discharge valve 8b that contacts and separates from the discharge valve seat 8a, and a discharge valve spring that biases the discharge valve 8b toward the discharge valve seat 8a. 8c and a discharge valve stopper 8d that determines the stroke (movement distance) of the discharge valve 8b. The discharge valve stopper 8d is press-fitted into a plug 8e that blocks the leakage of fuel to the outside. The plug 8e is joined by welding at the welded portion 8f. A discharge valve chamber 8g is formed on the secondary side of the discharge valve 8b, and the discharge valve chamber 8g communicates with the fuel discharge port 12a through a lateral hole formed in the body 1 in the horizontal direction.

When there is no fuel pressure difference between the pressurizing chamber 11 and the discharge valve chamber 8g, the discharge valve 8b is pressed against the discharge valve seat 8a by the urging force of the discharge valve spring 8c and is in the closed state. Only when the fuel pressure in the pressurizing chamber 11 becomes higher than the fuel pressure in the discharge valve chamber 8g, the discharge valve 8b opens against the biasing force of the discharge valve spring 8c. When the discharge valve 8b is opened, the high-pressure fuel in the pressurizing chamber 11 is discharged to the common rail 106 (see FIG. 1) via the discharge valve chamber 8g and the fuel discharge port 12a. With the configuration as described above, the discharge valve mechanism 8 functions as a check valve that limits the flow direction of fuel.

The low pressure fuel chamber 10 is provided with a pressure pulsation reducing mechanism 9 for reducing the pressure pulsation generated in the fuel pump from spreading to the fuel pipe 104. When the fuel once flowing into the pressurizing chamber 11 is returned to the suction passage 10d through the suction valve body 3b which is in the open state again for the capacity control, the fuel returned to the suction passage 10d causes the fuel to flow into the low pressure fuel chamber 10. Pressure pulsation 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-shaped metal plates are bonded together at their outer periphery and an inert gas such as argon is injected into the inside. Therefore, the pressure pulsation is absorbed and reduced as the metal damper expands and contracts.

The plunger 2 has a large diameter portion 2a and a small diameter portion 2b, and the volume of the sub chamber 7a increases or decreases due to the reciprocating motion of the plunger. The sub chamber 7a communicates with the low pressure fuel chamber 10 through the fuel passage 10e. When the plunger 2 descends, the fuel flows from the sub chamber 7a to the low pressure fuel chamber 10, and when the plunger 2 rises, the fuel flows from the low pressure fuel chamber 10 to the sub chamber 7a. As a result, the fuel flow rate into and out of the pump during the suction stroke or the return stroke of the pump can be reduced, and the pressure pulsation generated inside the fuel pump can be reduced.

Hereinafter, the fuel pump of the present embodiment will be specifically described with reference to FIGS. 5 is an axial sectional view of the electromagnetic suction valve mechanism 3 of the present embodiment, FIG. 6 is an enlarged view of the electromagnetic suction valve mechanism 3, and FIG. 7 is an exploded view of main parts of the electromagnetic suction valve mechanism 3. It is the drawing shown. As shown in FIG. 5, the fuel pump of this embodiment includes a bobbin 3p arranged radially outside the fixed core 3e or the movable core 3h, around which a coil 3g is wound, and the terminal member 16 corresponds to the cutout 3ra. The bobbin 3p is connected to the bobbin 3p. Specifically, the fuel pump includes a cup-shaped yoke 3q arranged on the outside in the radial direction of the coil 3g and the cover member 3r, and the terminal member 16 includes a bobbin on the inside in the radial direction of the cylindrical side surface portion of the yoke 3q. It is connected to 3p. The cover member 3r is biased inward in the axial direction by the disc spring 3s, and the C ring 3t is fitted in the groove formed in the small diameter portion 3ea of the fixed core 3e, so that the disc spring 3s is maintained in the biased state. So that the disc spring 3s is held.

As shown in FIG. 7, the bobbin 3p has a protruding portion 3pa arranged from the radially inner side to the radially outer side with respect to the cylindrical side surface of the yoke 3q, and the terminal member 16 is fixed by the protruding portion 3pa. The bobbin 3p and the protrusion 3pa are integrally formed of a non-conductive material such as resin mold or plastic. A hole 3qc is formed on the bottom surface of the yoke 3q, and the inner peripheral portion of the hole 3qc is press-fitted into the outer peripheral portion of the anchor guide portion 3u. The inner peripheral portion of the anchor guide portion 3u guides the outer peripheral portion of the anchor 3h. The inner peripheral portion of the anchor guide portion 3u is press-fitted into the outer peripheral portion of the small diameter portion of the seat member 3v on the axially opposite side to the anchor 3h. The seat member 3v forms the seat portion 3a shown in FIGS. 2 and 3, and also has an elongated hole formed at the center in the radial direction, and the rod 3i is guided by the inner peripheral portion of the elongated hole.

Also, the coil 3g is connected to the terminal member 16 on the outside in the radial direction of the yoke 3q. Specifically, the terminal member 16 fixes the wire by sandwiching and crimping the wire from the coil 3g at the wire connecting portion 16a. That is, the wire from the coil 3g is welded to the terminal member 16 at the wire connecting portion 16a. The wire from the coil 3g is not shown in FIG. The bobbin 3p has a protrusion 3pb or a groove (not shown) formed along the axial direction of the coil 3g (the left-right direction in FIG. 5), and the wire of the coil 3g contacts the protrusion 3pb or the groove. In this state, it is desirable that the terminal member 16 be wound. Further, the bobbin 3p is formed with a notch 3pc for disposing the coil 3g wound around the bobbin 3p on the axially outer side of the coil 3g, and the bobbin 3p has the axially inner side of the notch 3pc (rightward in FIG. 5). The coil 3g arranged axially outside (to the left in FIG. 5) is formed toward the protrusion 3pb or the groove located radially outside.

Here, as shown in FIGS. 5 and 6, the fuel pump of the present embodiment is arranged on the outer peripheral side of the fixed core 3e that attracts the movable core by the magnetic attraction force generated by energizing the coil 3g, and on the outer peripheral side of the coil 3g. And a magnetic member (cover member 3r) forming a magnetic circuit. The magnetic member is arranged outside the fixed core 3e in the axial direction. Further, the spring member 3m is arranged in the recessed portion 3ec formed on the inner diameter side of the fixed core 3e, and urges the rod 3i driven by the movable core 3h. The axially outer spring end surface 3ma of the spring member 3m is arranged axially outer (left side in FIG. 5) than the axially outer end surface (axial outer cover end surface 3rc) of the magnetic member. Further, it is desirable that the bottom surface 3ed of the recessed portion 3ec of the fixed core 3e is arranged axially outside of the axially outer end surface (axial outer cover end surface 3rc) of the magnetic member.

Here, the above-mentioned magnetic member is the cover member 3r arranged on the axially outer side of the fixed core 3e, and the axially outer cover end surface of the cover member 3r and the axially outer end surface of the magnetic member are the same surface. .. In the present embodiment, the fixed core 3e is based on Fe and has C 0.18 wt%, Mo, Si, Al 12 wt% or less, Cu 2 wt%, Ni 4 wt%, Cr 9 to 20 wt%, Ti 0.5 wt% or less. And a ferrite-based magnetic material containing other impurity elements, the hardness of which is adjusted to about Hmv 350 to 450.

In FIGS. 5 and 6, the fixed core 3e and the magnetic member (cover member 3r) are formed as separate members, but the present invention is not limited to this, and they may be an integral member. That is, in this case, the large diameter portion 3ea and the cover member 3r are formed as an integral member, and the axially outer end surface of the integrated large diameter portion is referred to as the axial outer cover end surface 3rc of the cover member 3r. Show. As a result, the position of the spring member 3m can be moved outward in the axial direction as compared with the conventional case. Therefore, since the axial length of the fixed core 3e can be shortened, the cost can be reduced.

In FIGS. 5 and 6, the fixed core 3e and the cover member 3r are separate members, but the cover member 3r is also a magnetic member. The axially outer cover end surface 3rc of the cover member 3r and the axially outer end surface of the fixed core 3e are flush with each other. Thereby, the space of the hole formed in the central portion of the cover member 3r can be effectively used, and the axial length of the fixed core 3e can be shortened. Further, since the cover member 3r approaches the coil 3g, the magnetic circuit can be downsized, and as a result, the efficiency of the magnetic circuit can be improved.

FIG. 6 is an enlarged view of the electromagnetic suction valve mechanism 3. The fixed core 3e has a large diameter portion 3ea and a small diameter portion 3eb, and the cover member 3r is arranged radially outside the small diameter portion 3eb and axially outside the large diameter portion 3ea. The small diameter portion 3eb of the fixed core 3e has a length L1 from the axial outer cover end surface 3rc of the cover member 3r to the axial outer small diameter end surface 3ee of the small diameter portion 3eb from the axial inner cover end surface 3rd of the cover member 3r to the large diameter portion. The length L2 up to the axially inner large-diameter end face 3ef of 3ea is equal to or more than the length L2. Further, in the small diameter portion 3eb of the fixed core 3e, the length L3 from the axially outer yoke end surface 3qa of the yoke 3q to the axially outer small diameter end surface 3ee of the small diameter portion 3eb is set from the axial outer cover end surface 3rc of the cover member 3r to the yoke 3q. It is configured to be larger than the length L4 up to the axially outer yoke end surface 3qa. That is, by securing the length of L3, it is possible to secure the strength for withstanding the load received from the spring member 3m.

The terminal member 16 for power supply is electrically connected to the coil 3g and is arranged inside the connector 17. The fixed core 3e is configured such that the axially outer small-diameter end surface 3ee of the small-diameter portion 3eb is arranged axially outside with respect to the axially outer connector end surface 17b of the connector 17. The terminal member 16 is arranged inside the connector 17 and along the direction (vertical direction in FIG. 6) intersecting the axial direction of the coil 3g (horizontal direction in FIG. 6) and electrically connected to the coil 3g. Connected to. Further, the spring member 3m is arranged radially inward of the cover member 3r, and the axially outer spring end surface 3ma of the spring member 3m is axially outward with respect to the connecting portion (wire connecting portion 16a) between the terminal member and the coil 3g. Arranged to be arranged. Thereby, the length of L3 can be secured, and the strength for withstanding the load received from the spring member 3m can be secured.

Further, as shown in FIG. 7, the yoke 3q is formed in a cylindrical shape, and a notch 3qb extending inward in the axial direction is formed from a part of the axially outer end surface 3qa of the yoke 3q in the circumferential direction. Further, the terminal member 16 is formed so as to pass from the radially inner side of the yoke 3q through the notch 3qb to the radially outer side of the yoke 3q. Since this allows the terminal member 16 to be projected in the radial direction, the length in the axial direction can be made shorter than that in which the terminal member 16 is projected in the axial direction, so that it does not become an obstacle when installing the fuel pump. Can be Further, the connector 17 is formed such that the radial length L5 is larger than the axial length L6, and the radial length L6 is substantially constant in the entire region of the connector 17 in the longitudinal direction (radial direction). It is desirable to be formed as follows.

According to the configuration of the present embodiment described above, it is possible to improve the attractive force with which the movable core 3h is magnetically attracted when the coil 3g is energized, and the electromagnetic suction valve mechanism 3 can be downsized. .. That is, according to the present embodiment, the magnetic circuit can be efficiently formed, so that the required magnetic attraction force can be generated even if the energization current is reduced, and the power consumption can be reduced.

1 Body 2 Plunger 3 Electromagnetic Suction Valve Mechanism 4 Relief Valve Mechanism 5 Suction Pipe 5a Suction Pipe Mounting Site 6 Cylinder 7 Seal Holder 8 Discharge Valve Mechanism 9 Pressure Pulsation Reduction Mechanism 10a Low Pressure Fuel Suction Port 11 Pressurization Chamber 12 Discharge Joint 13 Plunger Seal

Claims

A fixed core that attracts the movable core by a magnetic attraction force generated by energizing the coil,
A spring member arranged in a recess formed on the inner diameter side of the fixed core and biasing the rod driven by the movable core;
A magnetic member arranged on the outer peripheral side of the coil to form a magnetic circuit,
A fuel pump in which an axially outer spring end surface of the spring member is arranged axially outer than an axially outer end surface of the magnetic member.
A fixed core that attracts the movable core by a magnetic attraction force generated by energizing the coil,
A spring member arranged in a recess formed on the inner diameter side of the fixed core and biasing the rod driven by the movable core;
A magnetic member arranged on the outer peripheral side of the coil to form a magnetic circuit,
A fuel pump in which the bottom surface of the recess of the fixed core is arranged axially outside of the axially outer end surface of the magnetic member.
The high-pressure fuel pump according to claim 1 or 2,
The magnetic member is a cover member arranged on the outer side in the axial direction of the fixed core,
A fuel pump in which an axially outer cover end surface of the cover member and an axially outer end surface of the magnetic member are flush with each other.
The fuel pump according to claim 3,
The fixed core has a large diameter portion and a small diameter portion,
In the fuel pump, the cover member is arranged radially outside the small diameter portion and axially outside the large diameter portion.
The fuel pump according to claim 4,
The small diameter portion of the fixed core has a length from an axially outer cover end surface of the cover member to an axially outer small diameter end surface of the small diameter portion to an axially inner cover end surface of the cover member in the axial direction of the large diameter portion. A fuel pump configured to have a length equal to or greater than the length up to the inner large-diameter end surface.
The fuel pump according to claim 4,
The small diameter portion of the fixed core has a length from the axially outer yoke end surface of the yoke to the axially outer small diameter end surface of the small diameter portion to the axial outer yoke end of the yoke from the axial outer cover end surface of the cover member. A fuel pump configured to be larger than the length to the end face.
The fuel pump according to claim 4,
A terminal member for power supply, which is electrically connected to the coil and is arranged inside the connector,
The fixed core is a fuel pump configured such that an axially outer small-diameter end surface of the small-diameter portion is arranged axially outside with respect to an axially outer connector end surface of the connector.
The fuel pump according to claim 3,
A terminal member that is disposed inside the connector and that is disposed along a direction that intersects the axial direction of the coil, and that is electrically connected to the coil,
The spring member is arranged radially inside the cover member,
A fuel pump arranged such that an axially outer spring end surface of the spring member is arranged axially outside with respect to a connection portion between the terminal member and the coil.
The fuel pump according to claim 8,
The yoke is formed in a cylindrical shape, and a notch extending inward in the axial direction is formed from a part of the axially outer end surface of the yoke in the circumferential direction,
The fuel pump is formed such that the terminal member passes through the notch from a radial inner side of the yoke and extends radially outward of the yoke.
The fuel pump according to claim 8,
The fuel pump is formed such that the radial length of the connector is larger than the axial length of the connector, and the radial length of the connector is substantially constant over the entire longitudinal region of the connector. ..