JP2019019728A - High-pressure fuel pump - Google Patents

Abstract

To provide a high-pressure fuel pump on which a suction valve is mounted for reducing noise while maintaining strength reliability.SOLUTION: The high-pressure fuel pump comprises: a suction valve which opens/closes a channel; a seat part where the suction valve is seated; a stopper part which regulates movements of the suction valve toward an opposite side of the seat part in valve opening; and a rod which is configured separately from the suction valve and energizes the suction valve towards the stopper part. In the high-pressure fuel pump, the suction valve is formed from a central portion; and an outer peripheral portion which is formed radially outside of the central portion from a downstream face of the central portion to an upstream side and of which the axial thickness is reduced with respect to the central portion.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a high-pressure fuel pump that supplies fuel to an internal combustion engine at a high pressure.

  As a conventional technique of the present invention, there is a technique described in Patent Document 1. In Patent Document 1, a high-pressure pump capable of reducing the weight of a suction valve that opens and closes a supply passage for supplying fuel to a pressurizing chamber is provided. For this purpose, the intake valve 40 closes the supply passage 100 by sitting on the valve seat 34, and opens the supply passage 100 by separating from 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 contact 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 the suction valve 40 is urged toward the valve seat 34 side. 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 moving distance A when the suction valve 40 is fully closed and fully opened. Restrict movement. Accordingly, it is disclosed that the outer diameter of the suction valve 40 can be reduced and the axial thickness thereof can be reduced (see summary).

JP 2012-154295 A

  Patent Document 1 describes that the suction valve can be reduced in weight by reducing the outer diameter of the suction valve and reducing its axial thickness. 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 lowered, and there is a concern that fatigue failure may occur. On the other hand, if it is attempted to ensure strength reliability, the axial thickness increases, 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 an intake valve that reduces noise while maintaining strength reliability.

  In order to solve the above problems, a high-pressure fuel pump according to the present invention includes a suction valve that opens and closes a flow path, a seat portion on which the suction valve is seated, and a movement toward the opposite side of the seat portion of the suction valve when the valve is opened. A high-pressure fuel pump comprising: a stopper portion that restricts the intake valve; and a rod that is configured separately from the intake valve and biases the intake valve toward the stopper portion. The outer peripheral portion is formed on the radially outer side of the central portion from the downstream surface of the central portion toward the upstream and has an axial thickness that 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 intake valve while maintaining strength reliability. Other configurations, operations, and effects of the present invention will be described in detail in the following examples.

It is a figure showing the whole high-pressure fuel pump system composition to which the example 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 which shows the cross section of the electromagnetic suction valve mechanism 50 which concerns on Example 1 of this invention. Length R ₁ -R _0, is a diagram for describing a case where concentrated load F acts on the end of Hari cantilevered width X.theta. It is a figure explaining considering the case where the fuel pressure p acts on the edge part of the cantilever of length R- _R0 and width x (theta). 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. Of these, 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. Therefore, the overall configuration will be described first with reference to FIG. 2, and then each embodiment of the intake valve structure will be described.

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

  The high-pressure fuel pump 300 incorporates a plurality of components and mechanisms integrally 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 pressurizing 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 is provided in the discharge passage 12, and a relief valve mechanism 30 is provided in the relief passage 15. The pressurizing chamber 11 in the body 1 is changed in volume by the plunger 2 that moves up and down by the rotation of the cam 7 of the internal combustion engine, so that the pump operation is possible. The electromagnetic intake valve mechanism 50 is an adjustment valve that determines the amount of fuel to be pressurized. The discharge valve 8 is a check valve that restricts the direction of fuel flow. The relief valve mechanism 30 functions as a safety valve that opens 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 guided to the high pressure fuel pump 300 and passes through the electromagnetic suction valve mechanism 50 in the suction passage 9, the pressurizing chamber 11, and the discharge valve 8 in the discharge passage 12. The pressure is increased and 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, 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 the pressure sensor 56, and the signal is sent to the engine control unit (ECU) 40. The injectors 54 are mounted in accordance with the number of cylinders of the engine, and inject fuel with a signal from an engine control unit (ECU) 40. An engine control unit (ECU) 40 controls an electromagnetic intake valve mechanism 50 in the high-pressure fuel pump.

  Although the present invention relates to the improvement of the electromagnetic intake valve mechanism 50 of FIG. 1, the functions of each part 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 below the pressurizing chamber 11 is slidably inserted into the cylinder 120, and the retainer 3 is attached to the lower end. The urging force of the plunger return spring 4 acts on the retainer 3 in the downward direction in FIG. The tappet 6 reciprocates in the vertical direction in FIG. 1 by the rotation of the cam 7 of the internal combustion engine. Since the plunger 2 is displaced following the tappet 6, this changes the volume of the pressurizing chamber 11 and enables the pump operation.

  Next, the configuration of the electromagnetic intake 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. However, the movable portion 503 is driven in the valve closing direction (left direction in FIG. 1) by an anchor that forms a magnetic attraction surface that is attracted to the magnetic core. It may be formed from two members of a rod.

  Although FIG. 1 shows an engine system using a normally open type electromagnetic intake valve mechanism 50, the present invention is not limited to this. That is, the present invention can be applied even when a normally closed electromagnetic intake valve mechanism is provided.

  An electromagnetic intake valve mechanism that is opened when the electromagnetic coil 500 is OFF and closed when the electromagnetic coil 500 is ON is referred to as a normally open electromagnetic intake valve mechanism. The urging force of the anchor spring 502 acts on the suction valve 501 in the valve opening direction via the movable portion 503, while the urging force of the valve body spring 504 acts on the suction valve 501 in 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, that is, when no power is supplied, the suction valve 501 overcomes the biasing force of the valve body spring 504 by the mover 503 biased by the anchor spring 502, and the suction valve 501 is in the open state. It has become. Note that this is the same even if a system using an electromagnetic valve system called a normally closed system in which the operation is reversed, that is, when the electromagnetic coil 500 is OFF (non-energized), the suction valve 501 is closed. It is possible to implement the present invention.

  Next, the operation of the high pressure fuel pump and the flow rate 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 pressurizing chamber 11 increases, and the fuel pressure therein decreases. When the fuel pressure in the pressurizing chamber 11 becomes lower than the fuel pressure in the suction passage 9 and the biasing force due to the differential pressure exceeds the biasing force of the valve body spring 504, the suction valve 501 moves in the valve opening direction. Is sucked into the pressurizing 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 is opened against the suction valve 501 in addition to the biasing force due to the differential pressure. Will take direction. This process is called an inhalation stroke.

  After that, after the plunger 2 reaches BDC (Bottom Dead Center), it starts to move upward again. At this time, the electromagnetic coil 500 is in an OFF state. Then, since the biasing force of the anchor spring 502 acts on the suction valve 501 via the movable portion 503, the open state of the suction valve 501 is maintained by the movable portion 503 even if the plunger 2 moves upward. In this case, since the pressure in the pressurizing chamber 11 is in a low pressure state substantially equal to that of the suction passage 9, the discharge valve 8 cannot be opened. And is 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-layer metal diaphragm that reduces 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 attractive force, and this magnetic attractive force overcomes the biasing force of the anchor spring 502, and the movable portion 503 moves 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 differential pressure of the return fuel. Immediately after the intake valve 501 is closed, the fuel pressure in the pressurizing chamber 11 rises as the plunger 2 rises. As a result, the discharge valve 8 is automatically opened, and the fuel is pumped 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 from the pump can be controlled. That is, if the timing at which the electromagnetic coil 500 is turned on is advanced, the discharge flow rate can be increased, and conversely, the discharge flow rate can be reduced by decreasing the timing. The relief valve mechanism 30 includes a relief valve 151 seated on the relief valve seat 150 and a relief spring 155 that urges the relief valve 151 in the valve closing direction. When the common rail 53 becomes abnormally high in pressure due to a failure of the fuel injection valve 54 or the like and exceeds the set pressure, the relief valve mechanism 30 opens, and the abnormally high pressure fuel passes through the relief r passage 15 and passes through the pressurizing chamber 11. Function to return to.

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

  Here, Embodiment 1 of the present invention will be described with reference to FIG. The high-pressure fuel pump of this embodiment includes a suction valve 501 that opens and closes a flow path, a seat portion 505 on which the suction valve 501 is seated, and a stopper that restricts the movement of the suction valve 501 toward the opposite side of the seat portion 501 when the valve is opened. And a rod that is configured separately from the suction valve 501 and urges the suction valve 501 toward the stopper portion 506. The suction valve 501 includes a central portion 509 and an outer peripheral portion 511 that is formed on the radially outer side of the central portion 509 from the downstream surface of the central portion 509 toward the upstream and has a smaller axial thickness than the central portion 509. Formed with.

  That is, the electromagnetic suction valve mechanism 50 includes 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 the valve is closed, and a stopper portion that holds the suction valve 501 when the valve is opened. 506, a rod part 507 configured separately from the suction valve 501 and biasing the suction valve 501, and a valve body spring 504 biasing the suction valve 501 toward the rod part 507. As shown in FIG. 2, the central portion 509 is preferably configured such that the axial thickness becomes thinner as it goes radially outward. The intake valve 501 is configured such that the plate thickness (axial thickness) decreases toward the outermost peripheral portion 510, and a curved surface portion 511 that is recessed upstream is formed. One end of the valve body spring 504 is in contact with the spring contact portion 512 on the inner diameter side of the central portion 509 of the suction valve 501, thereby urging 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 surface with the same inclination as the central portion 509.

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

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

Further, as shown in the sectional view of the electromagnetic suction valve mechanism 50 in FIG. 3, the axial thickness t of the suction valve 501 is as follows 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). 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 on the radially outer side with respect to the guide portion.

At this time, in this embodiment, the relationship is satisfied so that the axial thickness t (x) of the suction valve 501 satisfies the following (Equation 1). R ₁ is the radius to the stopper contact portion 513, and t ₀ is the axial thickness of the root portion 514.

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 as shown in FIG. 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 as (Equation 4). By arranging (Equation 4) by (Equation 3), the bending stress σ (x) can be expressed by (Equation 5). As shown in the enlarged view A of FIG. 1, when the thickness t is constant, the stress σ (x) is maximized at the root (x = R ₁ −R ₀ ). The stress σ _{s at the} root portion can be expressed by (Equation 6). The thickness t (x) where the relationship between σ (x) and σ _s always satisfies σ (x) ≦ σ _s is as shown in (Equation 1). Thereby, the stress applied from the outermost peripheral portion 510 to the root portion 514 of the suction valve 501 applied when the suction valve 501 and the stopper portion 506 are in contact with each other 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 satisfy the above-described (Equation 2). As shown in FIG. 5, a case is considered in which the fuel pressure p acts on the end of a cantilever beam 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). By arranging (Equation 7) by (Equation 3), the bending stress σ (x) can be expressed by (Equation 8). As shown in the enlarged view A of FIG. 1, when the thickness t is constant, the stress σ (x) is maximized at the root (x = R ₁ −R ₀ ). The stress σ _{ss at the} 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). Thereby, when fuel pressure is applied to the entire downstream surface of the suction valve, the stress from the outermost peripheral portion 510 to the root portion 514 of the suction valve 501 can be made equal to or less than the stress applied to the root portion 514. Therefore, damage to the suction valve 501 can be prevented.

  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 sectional view of the electromagnetic suction valve mechanism 50 in FIG. 6, the suction valve 501 has a spring contact portion 512 with a 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 includes 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 of the valve body spring 504 (the left-right direction in FIG. 6). It is formed flat in the vertical direction of FIG.

  Thereby, since the valve body spring 504 and the spring contact part 512 contact uniformly, the urging | biasing force which the suction valve 501 receives from the valve body spring 504 can be stabilized. Therefore, it is possible to prevent the intake valve 501 from being violated and to provide a highly reliable electromagnetic intake valve mechanism 50.

  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 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. In other words, the downstream surface of the central portion 509 includes a stopper contact portion 513 with the stopper portion 506, and the stopper contact portion 513 is formed flat in a direction orthogonal to the valve body spring 504.

  When the contact portion 513 with the stopper portion 506 is flat, the suction valve 501 does not contact the valve portion 501 locally with respect to the stopper portion 506, and wear of the suction valve 501 can be prevented.

  Embodiment 4 of the present invention will be described with reference to FIG. Since the basic configuration is the same as that of the first or fourth embodiment, only different points will be described here. As shown in the 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.

  If the outermost peripheral portion 510 of the suction valve 501 has a sharp shape, the outermost peripheral portion 510 cannot be fixed when the suction valve 501 is manufactured by lathe processing, and workability is deteriorated. With the above configuration, this is suppressed and the processing of the intake valve 501 is facilitated.

  Embodiment 5 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 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. The center part 509 and the root part 514 of the center part 509 are provided.

  In the present embodiment, a curved surface portion 511 is formed so that the axial thickness decreases from the outermost peripheral portion 510 toward the stopper contact portion 513 and is recessed upstream, and the central portion root portion from the stopper contact portion 513 is formed. The thickness in the axial direction is constant over 514.

  That is, in the present embodiment, the central portion 509 of the suction valve 501 is configured as a flat plate having a constant axial thickness. Specifically, the suction valve 501 has a curved outer peripheral portion 511 formed from the stopper contact portion 513 with the stopper portion 506 toward the outermost peripheral portion 510, and is axially directed radially inward from the stopper contact portion 513. A central portion 509 having a constant thickness is formed. And as above-mentioned, it forms so that the downstream surface of the outer peripheral part 511 may have a curved surface part dented in an upstream.

  As a result, 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 intake valve 501, it is desirable that the axial thickness of the intake 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. Since the basic configuration is the same as that of the first embodiment or the fifth embodiment, only different points will be described here. As shown in the sectional view of the electromagnetic suction valve mechanism 50 in FIG. 10, it is desirable that the outermost peripheral portion 510 of the suction valve 501 has a curved surface or a certain thickness.

  If the outermost peripheral portion 510 of the suction valve 501 has a sharp shape, it cannot be fixed when the suction valve 501 is manufactured by lathe processing, and the processing becomes difficult. With the above configuration, this is suppressed and the processing of the intake valve 501 is facilitated.

  The present invention is not limited to high-pressure fuel pumps for internal combustion engines, and can be widely used for 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 part 504: Valve body spring 505: Seat part 506: Stopper part 507: Rod portion 508: Valve body upstream portion 509: Center 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: Pressurization chamber 12: Discharge passage 15: Relief passage 53: Common rail 54: Injector 56 : Pressure sensor

Claims (11)

A suction valve that opens and closes the flow path, a seat portion on which the suction valve is seated, a stopper portion that restricts movement of the suction valve toward the side opposite to the seat portion when the valve is opened, and a separate structure from the suction valve A high-pressure fuel pump comprising: a rod that urges the suction valve toward the stopper portion;
The intake valve is formed of a central portion and an outer peripheral portion that is formed radially outward of the central portion from the downstream surface of the central portion toward the upstream and has an axial thickness that is thinner than the central portion. High pressure fuel pump. The high-pressure fuel pump according to claim 1,
The central portion is a high pressure fuel pump having a flat plate shape with a constant axial thickness. The high-pressure fuel pump according to claim 1,
The central portion is a high-pressure fuel pump configured such that the axial thickness becomes thinner as it goes radially outward. The high-pressure fuel pump according to claim 1,
The high-pressure fuel pump is configured such that the outer peripheral portion is formed to be connected to the central portion, and a downstream surface of the outer peripheral portion has a curved surface portion that is recessed upstream. The high-pressure fuel pump according to claim 1,
A high-pressure fuel pump configured such that all of the outer peripheral portion is located upstream with respect to all of the downstream surface of the central portion. The high-pressure fuel pump according to claim 1,
A high-pressure fuel pump configured such that a downstream surface of the central portion collides with a stopper portion that restricts movement of the intake valve in a valve opening direction. The high-pressure fuel pump according to claim 1,
The high-pressure fuel pump in which 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. The high-pressure fuel pump according to claim 1,
A 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 perpendicular to the valve body spring. The high-pressure fuel pump according to claim 4,
The curved surface portion is a high-pressure fuel pump formed on an outermost peripheral portion of the intake valve. 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 from the stopper contact portion toward the radially inner side. High pressure fuel pump. The high-pressure fuel pump according to claim 10,
A high-pressure fuel pump formed so that a downstream surface of the outer peripheral portion has a curved surface portion recessed on the upstream side.

Images