WO2019012976A1

WO2019012976A1 - High-pressure fuel pump

Info

Publication number: WO2019012976A1
Application number: PCT/JP2018/024091
Authority: WO
Inventors: 幸平松下; 谷江　尚史; 康雄溝渕; 徳尾　健一郎
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: 2018-06-26
Publication date: 2019-01-17
Also published as: JP6855343B2; JP2019019728A

Abstract

Provided is a high-pressure fuel pump having mounted therein a suction valve having reduced noise achieved while the reliability of strength is maintained. This high-pressure fuel pump is provided with: a suction valve for opening and closing a flow passage; a seat on which the suction valve sits; a stopper which, at the time of valve opening, prevents the suction valve from moving away from the seat; and a rod formed as a separate body from the suction valve and biasing the suction valve toward the stopper. The suction valve comprises a center section and an outer peripheral section which is formed radially outside the center section so as to extend upstream from the downstream surface of the center section, and which has an axial thickness smaller than that of the center section.

Description

High pressure fuel pump

The present invention relates to a high pressure fuel pump for supplying fuel to an internal combustion engine at high pressure.

As a prior art of this invention, there exists a technique of patent document 1. FIG. This patent document provides a high pressure pump capable of reducing the weight of a suction valve for opening and closing a supply passage for supplying fuel to a pressurizing chamber. For this purpose, the suction valve 40 closes the supply passage 100 by being seated on the valve seat 34 and opens the supply passage 100 by leaving the valve seat 34. A stopper 50 is provided on the pressure chamber side of the suction valve 40 to limit movement of the suction valve 40 to the pressure chamber side. The needle 60 configured separately from the suction valve 40 can abut on the end face of the suction valve 40 on the valve seat 34 side. The first spring 21 is accommodated in the accommodation chamber 52 provided in the stopper 50, and urges the suction valve 40 toward the valve seat 34. The guide portion 41 extending from the end face on the stopper 50 side of the suction valve 40 is formed such that the axial length B is longer than the movement distance A between the fully closed and fully opened suction valve 40. Restrict movement. It is disclosed that this makes it possible to reduce the outer diameter of the suction valve 40 and reduce the axial thickness thereof (see the summary).

JP 2012-154295 A

Patent Document 1 describes that the weight of the suction valve can be reduced by reducing the outer diameter of the suction valve and reducing the thickness in the axial direction. However, in this structure, if the thickness is made too thin for the purpose of weight reduction, the strength reliability of the valve body is reduced, and there is a concern that fatigue failure may occur. On the other hand, in order to secure strength reliability, the axial thickness may be increased, and the noise reduction effect may not be sufficiently obtained.

An object of the present invention is to provide a high-pressure fuel pump equipped with a suction valve that reduces noise while maintaining strength reliability.

In order to solve the above problems, the high-pressure fuel pump according to the present invention includes a suction valve for opening and closing a flow path, a seat portion on which the suction valve is seated, and a movement of the suction valve toward the opposite side of the seat portion when opened. A high pressure fuel pump comprising a stopper portion for restricting the pressure, and a rod which is formed separately from the suction valve and which biases the suction valve toward the stopper portion, the suction valve includes a central portion, and The radial outer side of the central portion is formed from the downstream surface of the central portion toward the upstream, and is formed with an outer peripheral portion whose axial thickness is thinner than the central portion.

According to the configuration of the present invention, it is possible to realize a high pressure fuel pump equipped with a low noise suction valve while maintaining strength reliability. Other configurations, operations and effects of the present invention will be described in detail in the following embodiments.

FIG. 1 is a diagram showing an overall configuration of a high pressure fuel pump system to which an embodiment of the present invention is applied. It is a figure which shows the cross section of the electromagnetic suction valve mechanism 50 with which the Example of this invention is applied. It is a figure showing the section of electromagnetic induction valve mechanism 50 concerning Example 1 of the present invention. It is a figure explaining the case where concentration load F acts on the end of cantilever with length R ₁ -R ₀ and width xθ. It is a figure explaining about the case where the fuel pressure p acts on the end of the cantilever of length R-R ₀ and width xθ. It is a figure which shows the cross section of the electromagnetic suction valve mechanism 50 which concerns on Example 2 of this invention. It is a figure which shows the cross section of the electromagnetic suction valve mechanism 50 which concerns on Example 3 of this invention. It is a figure which shows the cross section of the electromagnetic suction valve mechanism 50 which concerns on Example 4 of this invention. It is a figure which shows the cross section of the electromagnetic suction valve mechanism 50 which concerns on Example 5 of this invention. It is a figure which shows the cross section of the electromagnetic suction valve mechanism 50 which concerns on Example 6 of this invention.

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

Example 1 will be described with reference to FIGS. 1 and 2. Among them, FIG. 1 shows the overall configuration of a high pressure fuel pump system to which the embodiments of the present invention (Embodiments 1 to 6) are applied. For this reason, first, the entire configuration will be described using FIG. 2, and then each embodiment of the suction valve structure will be described.

The high-pressure fuel pump system shown in FIG. 1 can be roughly divided into a fuel tank 101 on the left side, a high-pressure fuel pump 300 on the center side, a fuel injection system 200 (common rail 53, injector 54, etc.) on the right side. 40, an internal combustion engine 400 (not shown) below the center of the drawing (below the high pressure fuel pump 1).

The high pressure fuel pump 300 integrally incorporates a plurality of parts and mechanisms in the body 1 and is attached to the cylinder head 20 of the internal combustion engine 400. In the body 1, a suction passage 9, a pressure chamber 11, a discharge passage 12, and a relief passage 15 are formed. An electromagnetic suction valve mechanism 5 is provided in the suction passage 9, a discharge valve 8 in the discharge passage 12, and a relief valve mechanism 30 in the relief passage 15. Further, the volume of the pressure chamber 11 in the body 1 is changed by the plunger 2 moved up and down by the rotation of the cam 7 of the internal combustion engine, and the pump operation becomes possible. The electromagnetic suction valve mechanism 50 is a control valve that determines the amount of fuel to be pressurized. The discharge valve 8 is a check valve that restricts the flow direction of the fuel. The relief valve mechanism 30 functions as a safety valve that opens the inside of the common rail 53 when the pressure in the common rail 53 exceeds a predetermined pressure.

In the high pressure fuel pump system of FIG. 1, the fuel from the fuel tank 101 is introduced to the high pressure fuel pump 300 and passes through the electromagnetic suction valve mechanism 50 of the suction passage 9, the pressure chamber 11 and the discharge valve 8 of the discharge passage 12. Is supplied to the fuel injection system 200. The high pressure fuel pump is connected to the common rail 53 of the fuel injection system 200, and the pressurized fuel is pumped, and the high pressure fuel is injected from the injector 54 into the combustion chamber of the internal combustion engine. The pressure in the common rail 53 is measured by a pressure sensor 56, and the signal is sent to an engine control unit (ECU) 40. The injectors 54 are mounted in accordance with the number of cylinders of the engine, and inject fuel in response to a signal from the engine control unit (ECU) 40. The engine control unit (ECU) 40 also controls an electromagnetic suction valve mechanism 50 in the high pressure fuel pump.

Although the present invention relates to the improvement of the electromagnetic suction valve mechanism 50 of FIG. 1, each function of the high pressure fuel pump will be described in more detail.

First, the connection relationship with the internal combustion engine for operating the pump by the pressurizing chamber 11 will be described. The plunger 2 at the lower part of the pressure chamber 11 is slidably inserted into the cylinder 120, and a retainer 3 is attached to the lower end. The biasing force of the plunger return spring 4 acts on the retainer 3 downward in FIG. The tappet 6 reciprocates in the vertical direction of FIG. 1 by the rotation of the cam 7 of the internal combustion engine. The plunger 2 is displaced following the tappet 6, whereby the volume of the pressure chamber 11 changes and the pump operation becomes possible.

Next, the configuration of the electromagnetic suction valve mechanism 50 will be described. The electromagnetic suction valve mechanism 50 is held in a hole formed in the body 1 by press-fitting and welding. The electromagnetic suction valve mechanism 50 is provided with an electromagnetic coil 500, a mover 503, an anchor spring 502, and a valve body spring 504. In FIG. 1, the movable portion 503 is formed of one member, but the movable portion 503 is driven in the valve closing direction (left direction in FIG. 1) by the anchor forming the magnetic attraction surface attracted to the magnetic core and the anchor. It may be formed from two parts of the rod.

FIG. 1 shows an engine system using a normally open type electromagnetic suction valve mechanism 50, but the present invention is not limited thereto. That is, the present invention is also applicable to the case where a normally closed electromagnetic suction valve mechanism is provided.

The electromagnetic intake valve mechanism which is in the valve open state when the electromagnetic coil 500 is off and the valve closed state when the electromagnetic coil 500 is on is referred to as a normally open type electromagnetic intake valve mechanism. The biasing force of the anchor spring 502 acts on the suction valve 501 in the valve opening direction via the movable portion 503, while the biasing force of the valve body spring 504 acts on the valve closing direction. Here, the biasing force of the anchor spring 502 is larger than the biasing force of the valve body spring 504. Therefore, when the electromagnetic coil 500 is OFF, ie, when no current is supplied, the suction valve 501 overcomes the biasing force of the valve spring 504 by the mover 503 biased by the anchor spring 502, so the suction valve 501 is opened. It has become. The same applies to a system using an electromagnetic valve system called a normally closed system in which the suction valve 501 is closed when the operation is reversed, that is, when the electromagnetic coil 500 is OFF (no current). It is possible to practice the present invention.

Next, the operation of the high pressure fuel pump and the flow control method will be described. First, when the plunger 2 is displaced downward in FIG. 1 due to the rotation of the cam 7 of the internal combustion engine, the volume of the pressure chamber 11 increases and the fuel pressure therein decreases. Then, when the fuel pressure in the pressure chamber 11 becomes lower than the fuel pressure in the suction passage 9 and the biasing force by the differential pressure exceeds the biasing force of the valve spring 504, the suction valve 501 moves in the valve opening direction. Is sucked into the pressure chamber 11. If the electromagnetic coil 500 is turned off before the plunger 2 reaches TDC (Top Dead Center), the biasing force of the anchor spring 502 opens the suction valve 501 in addition to the biasing force due to the differential pressure. It will take you in the direction. This process is called a suction stroke.

Thereafter, the plunger 2 starts moving upward again after reaching the BDC (Bottom Dead Center). At this time, the electromagnetic coil 500 is in the OFF state. Then, since the biasing force of the anchor spring 502 acts on the suction valve 501 via the movable portion 503, the movable portion 503 maintains the open state of the suction valve 501 even if the plunger 2 moves upward. In this case, since the pressure in the pressure chamber 11 is in a low pressure state substantially equal to that of the suction passage 9, the discharge valve 8 can not be opened, and the fuel corresponding to the volume reduction of the pressure chamber 11 is the suction valve 501. , And returned to the damper chamber 51 side. This process is called a return process. In the damper chamber 51, a metal damper composed of a two-piece metal diaphragm for reducing pulsation of fuel pressure is disposed.

When the electromagnetic coil 500 is energized in the return step, the mover 503 is attracted to the magnetic core 5 by the magnetic attraction force, and the magnetic attraction force overcomes the biasing force of the anchor spring 502 to move the movable portion 503 in the valve closing direction. . Then, the valve body 501 is closed by the biasing force of the valve body spring 504 and the fluid pressure difference of the return fuel. Immediately after the suction valve 501 is closed, the fuel pressure in the pressure chamber 11 rises with the rise of the plunger 2. Thus, the discharge valve 8 is automatically opened, and the fuel is pressure fed to the common rail 53.

As described above, by adjusting the timing at which the electromagnetic coil 500 of the electromagnetic suction valve mechanism 50 is turned on, the flow rate discharged by the pump can be controlled. That is, the discharge flow rate can be increased by shortening the timing at which the electromagnetic coil 500 is turned on, and the discharge flow rate can be reduced by delaying the timing. The relief valve mechanism 30 includes a relief valve 151 seated on the relief valve seat 150 and a relief spring 155 biasing the relief valve 151 in the valve closing direction. When the common rail 53 abnormally rises to a high pressure due to a failure of the fuel injection valve 54 or the like and the set pressure is exceeded, the relief valve mechanism 30 opens and the abnormally high pressure fuel passes through the relief r passage 15 to the pressurizing chamber 11. Function to return to.

An enlarged view A of the lower drawing of FIG. 1 shows an enlarged sectional view of the suction valve although the shape is different from the suction valve 501 shown in the upper drawing of FIG. In the enlarged view A of the lower side of FIG. 1, the electromagnetic suction valve mechanism 50 includes a suction valve 501, a valve body spring 504 for biasing the suction valve 501 in a valve closing direction, a seat portion 505 on which the suction valve 501 is seated, and the suction valve 501. A stopper portion 506 for restricting the movement in the valve opening direction and a rod portion 507 for urging the suction valve 501 in the valve opening direction are provided. The stopper member forming the stopper portion 506 is press-fitted to the inner peripheral surface of the sheet member forming the sheet portion 505.

A first embodiment of the present invention will now be described with reference to FIG. The high-pressure fuel pump of this embodiment includes a suction valve 501 for opening and closing a flow path, a seat portion 505 on which the suction valve 501 is seated, and a stopper for regulating the movement of the suction valve 501 toward the opposite side to the seat portion 501 when opening. And a rod configured separately from the suction valve 501 and urging the suction valve 501 toward the stopper portion 506. The suction valve 501 has a central portion 509, an outer peripheral portion 511 which is formed radially outward of the central portion 509 from the downstream surface of the central portion 509 toward the upstream and has a thinner axial thickness than the central portion 509. It is formed by

That is, the electromagnetic suction valve mechanism 50 has a suction valve 501 that opens and closes the flow path at the valve body upstream portion 508, a seat portion 505 that holds the suction valve 501 when closing the valve, and a stopper portion that holds the suction valve 501 when opening the valve. And a rod 507 configured separately from the suction valve 501 to bias the suction valve 501, and a valve spring 504 biasing the suction valve 501 toward the rod 507. Further, as shown in FIG. 2, it is desirable that the central portion 509 is configured to become thinner as the axial thickness goes radially outward. The suction valve 501 is configured such that the plate thickness (axial direction thickness) becomes thinner toward the outermost peripheral portion 510, and a curved surface portion 511 recessed on the upstream side is formed. One end of the valve body spring 504 contacts the spring contact portion 512 on the inner diameter side of the central portion 509 of the suction valve 501 to bias the suction valve 501 in the valve closing direction. In the present embodiment, the spring contact portion 512 is configured to be formed on the same plane at the same inclination as the central portion 509.

Further, as shown in FIG. 2, it is desirable that the outer peripheral portion 511 is formed to be connected to the central portion 509, and the downstream surface of the outer peripheral portion 511 is configured to have a curved surface portion recessed on the upstream side. In addition, it is desirable that all of the outer peripheral portion 511 be configured to be located upstream with respect to all of the downstream surfaces of the central portion 509. Furthermore, it is desirable that the downstream surface of the central portion 509 be configured to collide with the stopper portion 506 that restricts the movement of the suction valve 501 in the valve opening direction. Furthermore, it is desirable that the curved surface portion of the downstream surface of the outer peripheral portion 511 be formed on the outermost peripheral portion of the suction valve 501.

As described above, if the axial thickness of the suction valve 501 becomes thinner toward the outermost peripheral portion 510 and the curved surface portion 511 recessed on the upstream side is formed, the mass of the suction valve 501 becomes lighter. Noise can be reduced.

Further, as shown in the cross-sectional view of the electromagnetic suction valve mechanism 50 in FIG. 3, the axial thickness t of the suction valve 501 extends from the outermost peripheral portion 510 (radius R) to the root portion 514 (radius R ₀ ) of the central portion 509 It is formed so as to be equal to or greater than the axial thickness indicated by (Equation 1) and (Equation 2) of In the present embodiment, the suction valve 501 has the largest axial thickness at the radial center and has a guide portion guided by the inner peripheral portion of the valve body spring 504. That is, the central portion 509 is formed radially outward with respect to the guide portion.

At this time, in the present embodiment, the axial thickness t (x) of the suction valve 501 is set to satisfy the following (Equation 1). R ₁ is a radius to the stopper contact portion 513, and t ₀ is an axial thickness of the root portion 514.

As shown in FIG. 4, consider the case where a concentrated load F acts on the end of a cantilever having a length R ₁ -R ₀ and a width xθ. The moment M (x) acting on each cross section of the beam can be expressed as (Equation 3), and the bending stress σ (x) can be expressed by (Equation 4). If (equation 4) is arranged by (equation 3), bending stress σ (x) can be expressed by (equation 5). As shown in the enlarged view A of FIG. 1, when the plate thickness t is constant, the stress σ (x) is maximized at the root portion (x = R ₁ −R ₀ ). The stress σ _s of this root portion can be expressed by (Equation 6). The plate thickness t (x) where the relationship between σ (x) and σ _s always satisfies σ (x) ≦ σ _s is as shown in (Equation 1). Accordingly, the stress applied from the outermost periphery 510 to the root portion 514 of the suction valve 501, which is applied when the suction valve 501 and the stopper portion 506 contact, can be made equal to or less than the stress applied to the root portion 514.

It is desirable that the axial thickness t (x) of the suction valve 501 be set to satisfy the above (Equation 2). As shown in FIG. 5, it is assumed that the fuel pressure p acts on the end of a cantilever having a length R-R ₀ and a width xθ. The moment M (x) acting on each cross section of the beam can be expressed by (Equation 7), and the bending stress σ (x) can be expressed by (Equation 3). If the equation (7) is rearranged by the equation (3), the bending stress σ (x) can be expressed by the equation (8). As shown in the enlarged view A of FIG. 1, when the plate thickness t is constant, the stress σ (x) is maximized at the root portion (x = R ₁ −R ₀ ). The stress σ _ss of this root portion can be expressed by (Equation 9). The thickness t (x) where the relationship between σ (x) and σ _ss always satisfies σ (x) ≦ σ _s is as shown in (Equation 1). Thus, when fuel pressure is applied to the entire surface on the downstream side of the suction valve, the stress from the outermost periphery 510 to the root 514 of the suction valve 501 can be made equal to or less than the stress applied to the root 514. Therefore, damage to the suction valve 501 can be prevented.

Second Embodiment A second embodiment of the present invention will be described with reference to FIG. Since the basic configuration is the same as that of the first embodiment, only different points will be described here. As shown in the cross-sectional view of the electromagnetic suction valve mechanism 50 of FIG. 6, the suction valve 501 has a spring contact portion 512 with the valve body spring 504 on the inner diameter side of the central portion 509. Here, in the present embodiment, the downstream surface of the central portion 509 is provided with a spring contact portion 512 with the valve body spring 504, and the spring contact portion 512 is a direction orthogonal to the axial direction (left and right direction in FIG. 6) of the valve body spring 504. It is formed flat (in the vertical direction in FIG. 6).

Thereby, since the valve body spring 504 and the spring contact part 512 contact uniformly, the biasing force which the suction valve 501 receives from the valve body spring 504 can be stabilized. Therefore, it is possible to suppress the asymmetry of the suction valve 501 and provide the electromagnetic suction valve mechanism 50 with high reliability.

A third embodiment of the present invention will be described with reference to FIG. Since the basic configuration is the same as that of the first embodiment, only different points will be described here. As shown in the cross-sectional view of the electromagnetic suction valve mechanism 50 in FIG. 7, the suction valve 501 is configured such that the stopper contact portion 513 with the stopper portion 506 is a flat portion. That is, the downstream surface of the central portion 509 includes the stopper contact portion 513 with the stopper portion 506, and the stopper contact portion 513 is formed flat in the direction orthogonal to the valve body spring 504.

In the suction valve 501, when the contact portion 513 with the stopper portion 506 is flat, the valve body 501 does not locally contact the stopper portion 506, and the wear of the suction valve 501 can be prevented.

Fourth Embodiment A fourth embodiment of the present invention will be described with reference to FIG. Since the basic configuration is the same as that of the first embodiment or the fourth embodiment, only different points will be described here. As shown in the cross-sectional view of the electromagnetic suction valve mechanism 50 in FIG. 8, it is desirable that the outermost peripheral portion 510 of the suction valve 501 has a curved surface or a certain thickness.

When the outermost peripheral portion 510 of the suction valve 501 has a sharp shape, the outermost peripheral portion 510 can not be fixed when manufacturing the suction valve 501 by lathe processing, and the workability is reduced. According to the above configuration, this is suppressed, and the processing of the suction valve 501 is facilitated.

A fifth embodiment of the present invention will be described with reference to FIG. Since the basic configuration is the same as that of the first embodiment, only different points will be described here. As shown in the sectional view of FIG. 9, the electromagnetic suction valve mechanism 50 includes a suction valve 501, a valve body spring 504, a seat portion 505, a stopper portion 506, a rod portion 507, an outermost peripheral portion 510, a stopper contact portion 513, and a suction valve 501. And a root portion 514 of the central portion 509.

In this embodiment, a curved surface portion 511 which is configured such that the thickness in the axial direction decreases from the outermost peripheral portion 510 toward the stopper contact portion 513 and is recessed on the upstream side is formed, and the central portion root portion from the stopper contact portion 513 The axial thickness is made constant over 514.

That is, in the present embodiment, the central portion 509 of the suction valve 501 is formed in a flat plate shape having a constant axial thickness. Specifically, in the suction valve 501, a curved outer peripheral portion 511 is formed from the stopper contact portion 513 with the stopper portion 506 toward the outermost peripheral portion 510, and the radial direction inward from the stopper contact portion 513 is in the axial direction A central portion 509 having a constant thickness is formed. Then, as described above, the downstream surface of the outer peripheral portion 511 is formed to have a curved surface portion recessed toward the upstream side.

Thereby, wear due to contact between the stopper portion 506 and the suction valve 501 can be prevented. However, in order to prevent damage to the suction valve 501, it is desirable that the axial thickness of the suction valve 501 be configured to satisfy the relationship shown in (Equation 1) and (Equation 2) shown in the first embodiment.

A sixth embodiment of the present invention will be described with reference to FIG. The basic configuration is the same as that of the first embodiment or the fifth embodiment, so only the difference will be described here. As shown in the cross-sectional view of the electromagnetic suction valve mechanism 50 of FIG. 10, it is desirable that the outermost peripheral portion 510 of the suction valve 501 has a curved surface or a constant thickness.

If the outermost periphery 510 of the suction valve 501 has a sharp shape, it can not be fixed when manufacturing the suction valve 501 by lathe processing, which makes processing difficult. According to the above configuration, this is suppressed, and the processing of the suction valve 501 is facilitated.

The present invention is widely applicable not only to high pressure fuel pumps for internal combustion engines but also to various high pressure pumps.

1: body 2: plunger 3: retainer 4: return spring 5: magnetic core 50: electromagnetic suction valve mechanism 501: suction valve 502: anchor spring 503: movable portion 504: valve body spring 505: seat portion 506: stopper portion 507: Rod portion 508: valve body upstream portion 509: central portion 510: outermost peripheral portion 511: outer peripheral portion (curved surface portion) 512: valve body spring contact portion 513: stopper contact portion 514: root portion 6: tappet 7: cam 8: discharge Valve 9: suction passage 11: pressure chamber 12: discharge passage 15: relief passage 53: common rail 54: injector 56: pressure sensor

Claims

A suction valve that opens and closes a flow path, a seat portion on which the suction valve is seated, a stopper portion that regulates movement of the suction valve toward the side opposite to the seat portion at the time of valve opening, and a separate body from the suction valve A high pressure fuel pump including a rod for urging the suction valve toward the stopper portion;
The suction valve is formed of a central portion, and an outer peripheral portion which is formed radially outward of the central portion from the downstream surface of the central portion toward the upstream and thinner in axial direction with respect to the central portion High pressure fuel pump.
In the high pressure fuel pump according to claim 1,
The high-pressure fuel pump may have a flat plate shape with a constant axial thickness at the central portion.
In the high pressure fuel pump according to claim 1,
The high-pressure fuel pump is configured such that the central portion becomes thinner toward the radial outside in the axial direction.
In the high pressure fuel pump according to claim 1,
The high-pressure fuel pump is configured such that the outer peripheral portion is connected to the central portion, and the downstream surface of the outer peripheral portion has a curved surface portion recessed toward the upstream side.
In the high pressure fuel pump according to claim 1,
The high-pressure fuel pump, wherein all of the outer peripheral portions are positioned upstream with respect to all of the downstream surfaces of the central portion.
In the high pressure fuel pump according to claim 1,
The high-pressure fuel pump is configured such that a downstream surface of the central portion collides with a stopper portion that restricts the movement of the suction valve in the valve opening direction.
In the high pressure fuel pump according to claim 1,
The downstream surface of the central portion includes a spring contact portion with the valve body spring, and the spring contact portion is formed flat in a direction orthogonal to the valve body spring.
In the high pressure fuel pump according to claim 1,
The downstream surface of the central portion includes a stopper contact portion with the stopper portion, and the stopper contact portion is formed flat in a direction orthogonal to the valve body spring.
In the high pressure fuel pump according to claim 4,
The high-pressure fuel pump wherein the curved surface portion is formed at the outermost periphery of the suction valve.
In the high pressure fuel pump according to claim 2,
The suction valve has the outer peripheral portion formed from the stopper contact portion with the stopper portion toward the outermost peripheral portion, and the central portion having a constant axial thickness in the radial direction from the stopper contact portion. High pressure fuel pump.
The high pressure fuel pump according to claim 10,
The high pressure fuel pump, wherein the downstream surface of the outer peripheral portion is formed to have a curved surface portion recessed toward the upstream side.