CN113692487A

CN113692487A - High-pressure fuel pump

Info

Publication number: CN113692487A
Application number: CN202080028729.3A
Authority: CN
Inventors: 田村真悟; 山田裕之; 小仓清隆
Original assignee: Hitachi Astemo Ltd
Current assignee: Hitachi Astemo Ltd
Priority date: 2019-04-18
Filing date: 2020-02-07
Publication date: 2021-11-23
Anticipated expiration: 2040-02-07
Also published as: JPWO2020213234A1; JP7169438B2; DE112020001266T5; WO2020213234A1; CN113692487B

Abstract

The invention aims to suppress the reduction of the durability and the oil sealing performance of a suction valve mechanism by stabilizing the operation of the suction valve. Therefore, the high-pressure fuel pump (100) of the present invention includes an electromagnetic suction valve mechanism having a suction valve (30), the suction valve (30) including: a rod portion (30B); a valve body portion (30A) formed integrally with the stem portion (30B); a1 st guide section (31B) that guides the outer peripheral section (30B1) of the rod section (30B); and a2 nd guide part (34B1) that guides the outer periphery of the valve body part (30A).

Description

High-pressure fuel pump

Technical Field

The present invention relates to a high-pressure fuel pump including a suction valve mechanism.

Background

As a background art in this field, a high-pressure fuel supply pump described in japanese patent application laid-open No. 2017-96216 (patent document 1) is known. The high-pressure fuel supply pump of patent document 1 includes an electromagnetically-driven intake valve mechanism, and the following structure is described in paragraph 0018-0021 of patent document 1. The electromagnetically driven type suction valve mechanism includes a plunger rod that is electromagnetically driven. A valve is provided at the front end of the plunger rod, the valve being opposed to a valve seat formed in the valve housing. A plunger rod biasing spring is provided at the other end of the plunger rod, and biases the plunger rod in a direction (valve opening direction) in which the valve is separated from the valve seat. A valve stopper is fixed to the outer periphery of the valve housing on the front end side.

The valve stopper is a member that restricts the movement of the valve 203 in the valve opening direction. A valve biasing spring is disposed between the valve and the valve stopper, and the valve is biased in a direction away from the valve stopper (valve closing direction) by the valve biasing spring. The front ends of the valve and the plunger rod are urged in opposite directions by the respective springs, but since the plunger rod urging spring is formed of a strong spring, the plunger rod presses the valve in a direction away from the valve seat against the force of the valve urging spring, and as a result, the valve is pressed against the valve stopper.

The plunger rod and the valve are not fixed and the front end of the plunger rod is dimensioned in such a way that it can exit from the valve (paragraph 0045). The valve stopper has a protruding portion at a center portion, the protruding portion including a cylindrical surface portion protruding toward the bottomed cylindrical portion side of the valve, the cylindrical surface portion functioning as a guide portion that guides a stroke of the valve in the axial direction (paragraph 0047).

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2017-96216

Disclosure of Invention

Problems to be solved by the invention

The high-pressure fuel supply pump of patent document 1 is configured such that the plunger rod and the valve of the electromagnetic drive type suction valve mechanism are not fixed, and the valve is guided to the axial stroke by the cylindrical surface portion of the protruding portion provided on the valve stopper. In this case, it is necessary to increase the axial length of the cylindrical surface portion in order to stabilize the operation of the valve in the axial direction, but if the axial length of the cylindrical surface portion is increased, the size of the suction valve mechanism increases. In other words, if the axial length of the cylindrical surface portion is shortened, the straight movement of the valve in the axial direction becomes unstable, and the valve abuts against the valve seat in a state where the valve is inclined. In this case, the valve seat portion of the valve (suction valve) or the valve seat (suction valve seat) is worn sharply, and the durability of the suction valve mechanism is reduced, leading to early reduction in oil-tight performance.

The invention aims to suppress the reduction of the durability and the oil sealing performance of a suction valve mechanism by stabilizing the operation of the suction valve.

Means for solving the problems

In order to solve the above problems, a high-pressure fuel pump according to the present invention,

comprising an electromagnetic suction valve mechanism having a suction valve,

the suction valve includes:

a rod portion;

a valve body portion integrally formed with the stem portion;

a1 st guide portion that guides an outer peripheral portion of the rod portion; and

and a2 nd guide portion that guides an outer periphery of the valve body portion.

Effects of the invention

According to the present invention, by stabilizing the operation of the suction valve, it is possible to suppress a decrease in the durability or oil sealing performance of the suction valve mechanism. Other structures, operations, and effects of the present invention will be described in detail in the following examples.

Drawings

Fig. 1 is an overall configuration diagram of an engine system to which the high-pressure fuel pump of the present invention is applied.

Fig. 2 is a cross-sectional view showing a vertical cross section (a cross section parallel to the axial direction of the plunger) of the high-pressure fuel pump as a premise of applying the present invention.

Fig. 3 is a sectional view showing a horizontal section (a section orthogonal to the axial direction of the plunger) of the high-pressure fuel pump of fig. 2 as viewed from above.

Fig. 4 is a cross-sectional view showing a vertical cross-section (a cross-section parallel to the axial direction of the plunger) of the high-pressure fuel pump of fig. 2, as viewed from a direction different from that of fig. 2.

Fig. 5 is an enlarged cross-sectional view of the electromagnetic suction valve mechanism of fig. 2.

Fig. 6 is a diagram for explaining the operation of the suction valve.

Fig. 7 is a diagram showing an example of a modification of the structure of the valve body portion and the guide portion for guiding the valve body portion.

Fig. 8 is a diagram showing an example of a modification of the structure of the valve body portion and the guide portion for guiding the valve body portion.

Detailed Description

Hereinafter, examples of the present invention will be described.

Fig. 1 is an overall configuration diagram of an engine system to which a high-pressure fuel pump 100 of the present invention is applied. The portion surrounded by the broken line indicates the main body of the high-pressure fuel pump 100 (see fig. 2), and the mechanism and the components shown in the broken line indicate that they are integrally assembled to the pump body 1. Fig. 1 is a diagram schematically showing an operation of an engine system.

In the following description, the vertical direction will be sometimes specified, but the vertical direction is based on the vertical direction in fig. 2 and 4, and does not necessarily coincide with the vertical direction in the case where high-pressure fuel pump 100 is mounted on the engine. In the following description, the axial direction is defined by the central axis 2A (see fig. 2) of the plunger 2, and the axial direction is parallel to the central axis 2A of the plunger 2 and coincides with the longitudinal direction of the plunger 2.

The fuel of the fuel tank 20 is drawn by a feed pump 21 based on a signal from an engine control unit 27 (hereinafter referred to as ECU). The fuel is pressurized to an appropriate supply pressure and delivered to the low-pressure fuel suction port 10a of the high-pressure fuel pump 100 through the suction pipe 28. The low-pressure fuel suction port 10a is formed by a suction joint 51 (see fig. 3 and 4).

The fuel having passed through 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 buffer (damper) chambers (10b, 10c) in which the pressure pulsation reducing mechanism 9 is disposed.

The fuel that has flowed into the electromagnetic intake valve mechanism 300 flows into the compression chamber 11 through an intake port (intake passage) that is opened and closed by the intake valve 30. The plunger 2 is powered by a cam mechanism 93 (see fig. 2 and 4) of the engine to reciprocate. By the reciprocating motion of the plunger 2, fuel is sucked into the compression chamber 11 from the suction port opened and closed by the suction valve 30 in the downward stroke of the plunger 2. The fuel drawn into the pressurizing chamber 11 is pressurized in the ascending stroke. The pressurized fuel is pressure-fed to the common rail 23 to which the pressure sensor 26 is attached via the discharge valve mechanism 8.

The injector 24 connected to the common rail 23 injects fuel to the engine based on a signal from the ECU 27. The high-pressure fuel pump of 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 100 controls the electromagnetic intake valve mechanism 300 by a signal sent from the ECU27 to discharge a desired fuel flow rate through the fuel discharge port 12.

Fig. 2 is a cross-sectional view showing a vertical cross section (a cross section parallel to the axial direction of the plunger 2) of the high-pressure fuel pump 100 as a premise of applying the present invention. Fig. 3 is a sectional view showing a horizontal section (a section orthogonal to the axial direction of the plunger 2) of the high-pressure fuel pump 100 of fig. 2 as viewed from above. Fig. 4 is a cross-sectional view showing a vertical cross-section (a cross-section parallel to the axial direction of the plunger 2) of the high-pressure fuel pump 100 of fig. 2, as viewed from a direction different from that of fig. 2.

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. That is, the plunger 2 reciprocates inside the cylinder 6 to change the volume of the pressurizing chamber 11. The pump body 1 is provided with 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 the discharge passage. The cylinder 6 is press-fitted into the pump body 1 on the outer peripheral side thereof.

A tappet 92 that converts a rotational motion of a cam 93 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 via a retainer (retainer)15 by a plunger biasing spring 4. This allows the plunger 2 to reciprocate up and down in accordance with the rotational movement of the cam 93.

A suction joint 51 is attached to a side surface portion of the pump body 1 of the high-pressure fuel pump 100. The suction joint 51 is connected to a low-pressure pipe for supplying the fuel from the fuel tank 20 to the high-pressure fuel pump 100, and the fuel is supplied from the suction joint 51 to the inside of the high-pressure fuel pump 100. The suction filter 52 prevents foreign matter present between the fuel tank 20 and the low-pressure fuel suction port 10a from being absorbed into the interior of the high-pressure fuel pump 100 due to the flow of fuel.

The fuel having passed through the low-pressure fuel suction port 10a passes through a low-pressure fuel suction passage provided in the pump body 1 so as to extend in the vertical direction, and then flows toward the pressure pulsation reducing mechanism 9. The pressure pulsation reducing mechanism 9 is disposed in the

buffer chambers

10b and 10c between the buffer cover 14 and the upper end surface of the pump body 1.

The fuel having passed through the

buffer chambers

10b and 10c then reaches the suction port 31b of the electromagnetic suction valve mechanism 300 through the low-pressure fuel suction passage 10d formed in the pump body 1 to extend in the vertical direction. The suction port 31b is formed in the suction valve seat member 31 forming the suction valve seat 31 a.

The electromagnetic suction valve mechanism 300 is provided with a terminal 46 a. The terminal 46a is integrally molded with the connector 46, and an unmolded end portion is connectable to the engine control unit 27 side.

The electromagnetic intake valve mechanism 300 will be described in detail with reference to fig. 3.

In the intake stroke state, the volume of the compression chamber 11 increases, and the fuel pressure in the compression chamber 11 decreases. In this stroke, if the fuel pressure in the compression chamber 11 is lower than the pressure in the suction port 31b, the suction valve 30 is opened. When the suction valve 30 is in the maximum lifted state, the suction valve 30 contacts the stopper 32. When the suction valve 30 is lifted up, the suction port between the suction valve seat 31a and the suction valve 30 is opened, and the electromagnetic suction valve mechanism 300 is opened. The fuel flows into the pressurizing chamber 11 through a suction port between the suction valve seat 31a and the suction valve 30 via a hole (fuel passage) formed in the pump body 1 in the lateral direction (horizontal direction).

After the end of the intake stroke, the plunger 2 is transferred to the upward movement and to the upward stroke. Here, the electromagnetic coil 43 is maintained in a non-energized state, and does not exert a magnetic biasing force. The armature biasing spring 40 biases the armature (anchor)36 in the right direction (valve opening direction) in the figure, and biases the suction valve 30 in the valve opening direction via the armature 36. The armature biasing spring 40 sets the biasing force so as to have a sufficient biasing force necessary to maintain the intake valve 30 open in a state where the electromagnetic coil 43 is not energized. The volume of the compression chamber 11 decreases with the upward movement of the plunger 2, but in this state, the fuel once sucked into the compression chamber 11 returns to the suction passage 10d through the suction port of the suction valve 30 in the open state again, so the pressure in the compression chamber 11 does not increase. This stroke is referred to as a return stroke.

In this state, when a control signal from ECU27 is applied to solenoid valve mechanism 300, current flows through electromagnetic coil 43 via terminal 46 (see fig. 2). Thereby, a magnetic attractive force acts between the core 39 and the armature 36, and the core 39 and the armature 36 come into contact on a magnetic attractive surface. The magnetic attractive force biases the armature 36 against the biasing force of the armature biasing spring 40, and moves the armature 36 in a direction 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 generated when the fuel flows 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 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 the high-pressure fuel is supplied to the common rail 23. This stroke is referred to as a discharge stroke.

That is, the ascending stroke from the lower start point to the upper start point of the plunger 2 is constituted by the return stroke and the discharge stroke. Then, by controlling the timing of energization to the coil 43 of the electromagnetic intake valve mechanism 300, the amount of the discharged high-pressure fuel can be controlled.

As shown in fig. 3, 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 welded at the contact portion 8e, and block a flow path through which the fuel flows 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. When the fuel pressure in the pressurizing chamber 11 becomes higher than the fuel pressure in the discharge valve chamber 12a, the discharge valve 8b is opened against the discharge valve spring 8 c. The fuel discharge port 12 is formed in the discharge joint 60, and the discharge joint 60 is welded and fixed to the pump body 1 by a welded portion 60 a.

Next, the relief valve mechanism 200 will be described with reference to fig. 2.

The relief valve mechanism 200 is composed of a relief valve body 201, a relief valve 202, a relief valve holder 203, a relief spring 204, and a spring stopper 205. The relief valve 202 receives the load of the relief spring 204 via the relief valve holder 203, is pressed by the seat portion of the relief valve body 201, and cooperates with the seat portion to shut off fuel.

If the pressure at the fuel discharge port 12 becomes abnormally high due to a failure of the electromagnetic intake valve mechanism 300 of the high-pressure fuel pump 100 or the like and becomes larger than the set pressure of the relief valve mechanism 200, the abnormally high-pressure fuel overflows to the buffer chamber 10c, which is the low-pressure side, via the relief passage 213. In the present embodiment, the relief destination of the relief valve mechanism 200 is set as the cushion chamber 10c, but it may be configured to relief to the compression chamber 11.

The electromagnetic intake valve mechanism 300 will be described in more detail with reference to fig. 5. Fig. 5 is an enlarged cross-sectional view of the electromagnetic suction valve mechanism 300 of fig. 2.

The suction valve 30 is constituted by a valve body portion 30A, a rod portion 30B, and a guided portion (convex portion) 30C. In the present embodiment, the guided portion 30C is regarded as a part of the valve body portion 30A, and the guided portion 30C is formed in the valve body portion 30A. The valve body 30A has an outer diameter Φ 30A larger than that of the stem portion 30B, the valve body 30A forms a larger diameter portion with respect to the stem portion 30B, and the stem portion 30B forms a smaller diameter portion with respect to the valve body 30A.

The rod portion 30B has a rod shape (circular rod shape or cylindrical shape) with a circular cross section. The valve body portion 30A is formed in a disc shape or a cylindrical shape having a thickness dimension D30A in the axial direction (longitudinal direction) of the stem portion 30B smaller than the outermost diameter Φ 30A. The stem portion 30B is integrally formed with the valve body portion 30A in an axial direction so as to be orthogonal to the end face 30A1 of the valve body portion 30A. The rod portion 30B and the valve body portion 30A may be integrally formed, or a member in which a member constituting the rod portion 30B and a member constituting the valve body portion 30A are joined to each other.

The end surface 30A1 of the valve body portion 30A constitutes a seat portion facing the seat portion 31a formed in the intake seat member 31, and is used as a fuel seal portion. Therefore, the seat portion 30A1 of the valve body portion 30A is finished to have a high surface accuracy of the surface (i.e., a small surface roughness).

The outer cylindrical surface (outer circumferential surface) 30B1 of the stem portion 30B constitutes a guided portion (1 st guided portion) that guides the movement of the stem portion 30B in the axial direction (longitudinal direction) by a guide portion (1 st guide portion) 31B formed in the suction valve seat member 31. The guide portion 31B is formed on an inner cylindrical surface (inner circumferential surface) of the suction valve seat member 31. The outer peripheral surface 30B1 of the stem portion 30B and the inner peripheral surface 31B of the suction valve seat member 31 are finished to have high surface accuracy (i.e., small surface roughness). This can prevent the rod portion 30B from being fixed to the inner cylindrical portion of the guide portion 31B or from being worn when sliding on the guide portion 31B.

A convex portion 30C is formed on a surface (end surface) 30A2 of the valve body portion 30A on the opposite side of the seat portion 30A 1. The valve stopper 34 is provided on the end surface 30A2 of the valve body 30A and the projection 30C side. The valve stopper 34 surrounds the valve body 30A with a side wall (peripheral wall) 34A2 of the large-diameter recess 34A, and constitutes a valve body case that houses the valve body 30A. The valve stopper 34 has a stepped recess portion having at least 2 layers as viewed from the side of the intake valve seat member 31 so as to house the valve body portion 30A and the convex portion 30C.

The bottom surface (opening side recess bottom surface) 34A1 of the large diameter recess (opening side recess) 34A of the valve stopper 34 abuts against the end surface 30A2 of the valve body 30A, and constitutes a stopper portion (stopper surface) that restricts the valve body 30A from moving in the valve opening direction. A bottom surface (a rear recess bottom surface) 34B2 of the small-diameter recess (a rear recess) 34B of the valve stopper 34 constitutes a spring seat of the suction valve biasing spring 33.

The suction valve biasing spring 33 is disposed between the small-diameter recess bottom surface 34B2 and the end surface 30C1 of the convex portion 30C, and biases the entire suction valve 30 in the valve closing direction through the valve body portion 30A. The suction valve urging spring 33 is in direct contact with the bottom surface 34B2 of the valve stopper 34. The bottom surface 34B2 of the valve stopper 34 is orthogonal to the center axis LA of the guide portion 31B formed in the suction valve seat member 31, and prevents the suction valve biasing spring 33 from being attached obliquely.

The valve stopper 34 has 1 or more opening portions (notched portions) 34D for constituting the fuel flow path. The opening (cutout) 34D constituting the fuel flow path provided in the valve stopper 34 may have a hole shape or a groove shape.

The inner diameter of the small-diameter recess 34B of the valve stopper 34 is slightly larger than the outer diameter Φ 30C of the protrusion 30C, and the outer peripheral surface (guided portion) 30C2 of the protrusion 30C slides on the inner cylindrical portion (inner peripheral surface) 34B1 of the small-diameter recess 34B. That is, the outer peripheral surface 30C2 of the convex portion 30C constitutes a guided portion (No. 2 guided portion), and the inner peripheral surface 34B1 constitutes a guide portion (guide surface) that guides the guided portion 30C 2. In this way, in the intake valve 30, the guided portion 30C2 of the convex portion 30C provided at the one end is guided by the guide portion (the 2 nd guide portion) 34B1 of the valve stopper 34 to move in the axial direction.

The suction valve 30 is supported at both ends of the stem portion 30B and the convex portion 30C by a guide portion 31B formed on the suction valve seat member 31 and a guide portion 34B1 formed on the valve stopper 34, respectively, and the radial movement and the tilt range are restricted. The guide portion 31B formed on the suction valve seat member 31 and the guide portion 34B1 formed on the valve stopper 34 are provided with clearances with respect to the guided portion 30B1 of the rod portion 30B and the guided portion 30C2 of the protrusion 30C, respectively, and the suction valve 30 can slide with respect to the guide portion 31B and the guide portion 34B1 in an environment where sliding resistance is small.

The suction seat member 31 is provided with a fuel seal portion 31a orthogonal to the center axis LA of the guide portion 31B, and the surface accuracy of the surface is made small.

The valve stopper 34 will be explained again. The valve stopper 34 has a stopper surface 34a1 and a surface 34E in surface contact with the intake valve seat member 31, the valve body 30A including the convex portion 30C is housed between these surfaces 34a1, 34E, and the distance between the stopper surface 34a1 and the surface 34E is defined as Δ L. If only the thickness of the valve body portion 30A except for the convex portion 30C is set to t30A, the value g1 (see fig. 6) of Δ L-t30A can be adjusted to the stroke length of the intake valve 30. The suction valve 30 is provided with a tapered portion 34a3 on the valve stopper 34 side, and the suction valve 30 is prevented from sticking to the valve stopper 34 by reducing the contact area between the valve stopper 34 and the valve body portion 30A. In addition, the fuel passage area is increased by providing the tapered portion 34a 3. Further, by providing the tapered portion 34a3, the fluid resistance at the time of valve opening is reduced, and the valve opening operation is stabilized.

The suction valve seat member 31 is press-fitted or inserted into an inner cylindrical portion 1H2 (see fig. 3) provided in the pump body 1. The valve stopper 34 is press-fitted or inserted into an inner cylindrical portion 1H1 provided in the pump body 1. The inner cylindrical portions 1H1 and 1H2 provided in the pump body 1 are made coaxially, and the better the coaxial accuracy, the more the coaxial accuracy of the suction valve 30 with the guide portion 31B and the guide portion 34B1 can be improved.

The smaller the axial length of the guide portion 31B of the suction valve seat member 31 is, the smaller the sliding area with the suction valve 30 can be suppressed. Further, the smaller the axial length of the guide portion 34B1 of the valve stopper 34, the smaller the sliding area with the intake valve 30 can be suppressed. Further, by making the convex portion 30C spherical, when the suction valve 30 and the valve seat portion 31a are closed, the suction valve 30 can be inclined in accordance with a relative positional shift after assembly of the components of the suction valve 30 and the valve seat portion 31a, and abrasion caused by contact of one end of the suction valve 30 and an increase in contact surface pressure between the corner portion of the guide portion 31B of the suction valve seat member 31 and the rod portion 30B can be suppressed.

Fig. 6 is a diagram for explaining the operation of the suction valve 30. Fig. 6 (a) shows a state when the valve is opened. Fig. 6 (B) shows a state in the middle of the transition from the valve-opened state to the valve-closed state. Fig. 6 (C) shows a state when the valve is closed.

In the state of fig. 6 (a), a gap G1 between the valve seat portion 30A1 and the valve seat portion 31a of the valve body portion 30A is G1, and a gap G3 between the end face 36A of the armature 36 and the end face 39A of the core 39 is G2. In this case, g2 is greater than g1(g2 > g 1). The end 30B2 of the rod portion abuts the end face 36B of the armature 36, and the gap G2 between the end 30B2 and the end face 36B is 0(G2 is 0).

In the state of fig. 6B, the gap G1 between the valve seat portion 30A1 and the valve seat portion 31a of the valve body portion 30A is 0(G1 is 0), and the gap G3 between the end face 36A of the armature 36 and the end face 39A of the core 39 is G3. In this case, g3 is the size obtained by subtracting g1 from g2 (g3 — g2-g 1). The end 30B2 of the rod portion abuts the end face 36B of the armature 36, and the gap G2 between the end 30B2 and the end face 36B is 0(G2 is 0).

In the state of fig. 6C, the gap G1 between the valve seat portion 30A1 and the valve seat portion 31a of the valve body portion 30A is 0(G1 is 0), and the gap G3 between the end face 36A of the armature 36 and the end face 39A of the core 39 is also 0(G3 is 0). In this case, the end 30B2 of the rod portion is separated from the end face 36B of the armature 36 in the direction along the central axis LA, a gap is generated between the end 30B2 of the rod portion and the end face 36B of the armature 36, and the gap G2 between the end 30B2 and the end face 36B becomes G3.

A modification of the structure of the valve body 30A and the guide portion for guiding the valve body 30A will be described. Fig. 7 and 8 are diagrams showing an example of a modification of the structure of the valve element 30A and the guide portion for guiding the valve element 30A.

In fig. 7, the outermost peripheral portion (outer peripheral surface having the largest outer diameter) of the valve body portion 30A is defined as a guided portion 30C2 without providing the convex portion 31C. In this case, 30C2 is not the outer peripheral surface of the convex portion 31C.

In this example, the suction valve seat member 31 constitutes both the 1 st guide portion 31B and the 2 nd guide portion 34B 1. For example, the suction valve seat member 31 may constitute a part of the side wall (peripheral wall) 34a2 of the valve stopper 34. In this case, the 1 st guided portion 31B1 is also formed in the rod portion 31B, and the 2 nd guided portion 30C2 is formed in the valve body portion 30A. In this example, the coaxiality of the 1 st guide part 31B and the 2 nd guide part 34B1 is also maintained. As long as the coaxiality of the 1 st guide part 31B and the 2 nd guide part 34B1 is maintained, the 1 st guide part 31B does not need to be provided in the suction valve seat member 31, and another member constituting the 1 st guide part 31B may be provided.

In fig. 8, in fig. 7, the 1 st guide portion 31B formed in the suction valve seat member 31 is provided in the valve stopper (valve housing) 34, similarly to the embodiment of fig. 5. In this case, the 2 nd guided portion 30C2 is configured in the same manner as in fig. 7.

In the example illustrated in fig. 7 or 8, the pump body 1 may be formed with a2 nd guide portion 34B1 provided in the intake valve seat member 31 or the valve stopper (valve housing) 34. In this case, by forming the valve stopper 34 directly in the shape of the pump body 1, it is not necessary to prepare another member for the valve stopper 34 and assemble the valve stopper to the pump body 1. This can improve the efficiency of the assembly work and reduce the material cost.

The features of the high-pressure fuel pump 100 of the present embodiment are described below, for example.

(1) Including an electromagnetic suction valve mechanism 300 having a suction valve 30, the suction valve 30 includes: a rod portion 30B; a valve body portion 30A formed integrally with the stem portion 30B; a1 st guide portion 31B that guides the outer peripheral portion 30B1 of the lever portion 30B; and a2 nd guide portion 34B1 that guides the outer periphery of the valve body portion 30A.

(2) In (1), the 2 nd guide portion 34B1 guides the outer periphery of the convex portion 30C formed on the tip end side of the valve body portion 30A.

(3) In (1), the 1 st guide portion 31B is configured coaxially with the 2 nd guide portion 34B 1.

(4) In (3), the suction seat member 31 on which the valve body portion 30A is seated is provided, and the 1 st guide portion 31B is constituted by the suction seat member 31.

(5) In (4), the valve body housing portion 34 formed of a member different from the suction valve seat member 31 is included, and the 2 nd guide portion 34B1 is constituted by the valve body housing portion 34.

(6) In (2), the outer diameter φ 30C of the projection 30C is smaller than the outermost diameter φ 30A of the valve body portion 30A.

(7) In (3), the 2 nd guide portion 34B1 is formed in the pump body 1 for mounting the electromagnetic suction valve mechanism 300.

(8) In (1), the electromagnetic intake valve mechanism 300 includes the armature 36 and the core 39 that generate magnetic attraction force with each other, and the armature 36 abuts on the rod portion 30B when the valve is opened, and the armature 39 is separated from the rod portion 30B when the valve is closed, so that a gap g3 is generated between the abutment portions 36B and 30B2 of the armature 36 and the rod portion 30B when the valve is opened.

(9) The intake valve 30 is fixed so that a valve body portion 30A and a rod portion 30B extending from the valve body portion 30A to the armature 36 side always integrally operate, the valve body portion 30A abuts against the intake valve seat member 31 to seal fuel, and the intake valve 30 includes a1 st guide portion 31B that guides an outer peripheral portion 30B1 of the rod portion 30B and a2 nd guide portion 34B1 that guides an outer periphery of the valve body portion 30A.

In the embodiment of the present invention, the valve body portion 30A and the rod portion 30B are integrally configured, and both end portions of the valve seat portion 30A1 of the intake valve 30 are supported, whereby the inclination of the intake valve 30 when opening and closing the intake valve 30 can be limited to be small. Thus, the corner portion of the suction valve 30 or the suction valve seat 30a1 is in contact with the seat portion 31a of the suction valve seat member 31, and the possibility of damaging the seat portion 31a and reducing the oil-tight performance can be suppressed low.

According to the present invention, the inclination of the suction valve 30 in the electromagnetic suction valve mechanism 300 is reduced, so that the reduction of the oil-tight performance can be suppressed, and the high-pressure fuel pump 100 which can reduce the cost by reducing the number of components can be provided.

Description of the reference numerals

30 … suction valve, 30a … valve body portion, 30B … stem portion, outer peripheral portion of 30B1 … stem

portion

30B, 30C … convex portion, 31 … suction valve seat member, 31B … 1 st guide portion, 34 … valve stopper (valve body case portion), 34B1 … 2 nd guide portion, 36 … armature, 39 … magnetic core, 100 … high-pressure fuel pump, 300 … electromagnetic suction valve mechanism.

Claims

1. A high-pressure fuel pump characterized in that:

comprising an electromagnetic suction valve mechanism having a suction valve,

the suction valve includes:

a rod portion;

a valve body portion integrally formed with the stem portion;

2. The high-pressure fuel pump of claim 1, wherein:

the 2 nd guide portion guides an outer periphery of a convex portion formed on a tip end side of the valve body portion.

3. The high-pressure fuel pump of claim 1, wherein:

the 1 st guide portion and the 2 nd guide portion are coaxially formed.

4. The high-pressure fuel pump of claim 3, wherein:

the high-pressure fuel pump includes a suction valve seat member on which the valve body portion is seated,

the 1 st guide part is formed of the suction valve seat member.

5. The high-pressure fuel pump of claim 4, wherein:

the high-pressure fuel pump includes a valve body housing portion formed of a member different from the suction valve seat member,

the 2 nd guide portion is constituted by the valve body housing portion.

6. The high-pressure fuel pump of claim 2, wherein:

the convex portion has an outer diameter smaller than an outermost diameter of the valve body portion.

7. The high-pressure fuel pump of claim 3, wherein:

the 2 nd guide portion is formed in a pump body for mounting the electromagnetic suction valve mechanism.

8. The high-pressure fuel pump of claim 1, wherein:

the electromagnetic suction valve mechanism includes an armature and a core that generate a magnetic attraction force with each other,

the armature abuts the rod portion when the valve is opened, and the armature is separated from the rod portion when the valve is closed, thereby generating a gap between the armature and the rod portion.

9. A high-pressure fuel pump characterized in that:

comprises an electromagnetic suction valve mechanism which is provided with an armature, a magnetic core, a suction valve and a suction valve seat component,

the suction valve is fixed so that a valve body portion that seals fuel by coming into contact with the suction valve seat member and a rod portion extending from the valve body portion to the armature side always integrally operate,

the suction valve includes: