JP2023093776A - Valve mechanism and high-pressure fuel supply pump having the same - Google Patents

Abstract

To provide a valve mechanism which is easy to manufacture while suppressing an inclination and eccentricity of a valve body, and also suppressing the lowering of the responsiveness of the valve body, and a high-pressure fuel supply pump having the same.SOLUTION: A suction valve mechanism 300 comprises a suction valve 30 which can be seated on a valve seat part 31b, and can be separated therefrom, and a suction valve stopper 32 for regulating the movement of the suction valve 30 to a valve-opening direction. The suction valve 30 has a valve main body part 71 which is seated on the valve seat part 31b, and a cylindrical guided part 72 extending toward the suction valve stopper 32 side from a position at the inside of a radial direction rather than the valve seat part 31b of the valve main body part 71. The suction valve stopper 32 has a stopper main body part 81 for regulating the movement of the suction valve 30 to the valve-opening direction by abutting on a tip part 72C of the guided part 72, and a cylindrical part 82 as a guide part extending toward the valve seat part 31b side from the stopper main body part 81, and guiding the movement of the suction valve 30 in a contact/separation direction with respect to the valve seat part 31b by a slide of the guided part 72.SELECTED DRAWING: Figure 4

Description

TECHNICAL FIELD The present invention relates to a valve mechanism and a high pressure fuel supply pump including the same, and more particularly to a valve mechanism in which movement of a valve body in a valve opening direction is restricted by a stopper and a high pressure fuel supply pump including the same.

In recent years, efforts have been made to increase output and reduce exhaust emissions in internal combustion engines, and global expansion is underway. Among internal combustion engines, a direct-injection engine that injects fuel directly into a combustion chamber uses a high-pressure pump for increasing the pressure of the fuel. Among high-pressure pumps that are widely used in the market today, there is a piston-type pump equipped with an electromagnetic intake valve mechanism. As this electromagnetic suction valve mechanism, there is known one that has a suction valve that passively opens and closes with respect to the movement of the fluid, and an electromagnetic actuator that engages with the suction valve to regulate the operation of the suction valve (for example, See Patent Document 1).

The high-pressure pump disclosed in Patent Document 1 includes an intake valve that can be seated on and removed from a valve seat formed in an introduction passage, and a stopper that limits the movement (lift) of the intake valve in the valve opening direction. The suction valve has a valve body that abuts on the valve seat, and a cylindrical first guide portion that extends in the movement direction of the valve body. The stopper has a cylindrical second guide portion that slides on the first guide portion of the intake valve, and a contact portion that contacts the valve body. The intake valve is guided to move in the opening/closing direction by the first guide portion slidingly contacting the second guide portion of the stopper. Further, the intake valve is limited in movement (lift) in the valve opening direction by contacting the contact portion of the stopper with the surface of the valve body opposite to the valve seat.

Further, in the high-pressure pump disclosed in Patent Literature 1, a space (valve chamber) is formed inside by the tubular first guide portion of the suction valve and the tubular second guide portion of the stopper. A groove extending in the radial direction is provided in either the abutment portion of the stopper or the valve body, and an orifice is provided in either the first guide portion of the suction valve or the second guide portion of the stopper. ing. When the intake valve shifts from an open state in which the intake valve contacts the stopper to a closed state, the fuel in the pump chamber flows from the groove of the stopper into the valve chamber through the gap between the first guide portion and the second guide portion and the orifice. do.

JP 2014-114722 A

In the high-pressure pump disclosed in Patent Document 1, the movement of the suction valve in the opening/closing direction is guided by sliding the cylindrical first guide portion of the suction valve against the cylindrical second guide portion of the stopper. As a result, tilting and eccentricity of the intake valve are suppressed. Further, by providing a radially extending groove in the abutment portion of the stopper or in the valve body, a flow path connecting the pump chamber and the valve chamber is ensured when the intake valve is opened. This suppresses a decrease in responsiveness of the opening/closing operation of the intake valve.

By the way, it is an important issue to manufacture high-pressure pumps with a simple configuration at a low cost at present, when the global development of products is progressing. A suction valve and a stopper as described in Patent Document 1 are basically components of an axially symmetrical structure. In the case of parts such as the suction valve and the stopper described in Patent Document 1, in the case of a part having radial grooves in an axially symmetrical structure, the man-hours for cutting tend to increase, which is disadvantageous in terms of manufacturing cost. I have concerns.

In the case of a component of an axially symmetrical structure, it can be manufactured by machining the workpiece only with a lathe. To briefly explain the process of this part machining, for example, a workpiece is fixed to the chuck of a lathe, and a tool (bite) is applied to the rotated workpiece while moving it along the axis of rotation for cutting. . Therefore, cutting is relatively easy, and the number of processing steps can be reduced.

On the other hand, in the case of a component having radial and axial grooves in an axially symmetrical structure, it is necessary to perform additional machining using an end mill of a milling machine after cutting the workpiece using a lathe. That is, after machining the work by the lathe, it is necessary to remove the work from the chuck of the lathe and then fix it to the table of the milling machine. Next, a groove is formed by cutting the workpiece with a tool such as an end mill that rotates. In this way, in the case of a component having radial and axial grooves in an axially symmetrical structure, the number of man-hours for cutting is increased, which is troublesome.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and an object of the present invention is to provide a valve that is easy to manufacture while maintaining suppression of inclination and eccentricity of the valve body and suppression of deterioration in responsiveness of the valve body. It is to provide a mechanism and a high-pressure fuel supply pump equipped with the same.

The present application includes a plurality of means for solving the above problems. One example is a valve body that can be seated and separated from a valve seat, and a valve on the opposite side of the valve seat with respect to the valve body. and a valve stopper for restricting the movement of the valve body in the valve opening direction, the valve body having a valve body portion seated on the valve seat and a diameter larger than the valve seat in the valve body portion. and a cylindrical guided portion extending toward the valve stopper side from a position on the inner side of the direction, and the valve stopper abuts on the tip portion of the guided portion to move the valve body in the valve opening direction. and a stopper portion that extends from the stopper portion toward the valve seat side, and guides the movement of the valve body in a direction toward or away from the valve seat by sliding the guided portion. It is characterized by having a guide part for doing.

According to the present invention, eccentricity and inclination of the valve body can be suppressed by sliding the guided portion against the guide portion and guiding the movement of the valve body. Furthermore, since the structure restricts the movement of the valve body in the valve-opening direction not by the contact between the valve main body and the valve stopper, but by the contact between the tip of the guided portion of the valve body and the valve stopper, the valve body And, without forming grooves in the structure of the valve stopper in the radial direction and the axial direction of the structure, the fluid can flow in and out of the inner space of the cylindrical guided part during the opening and closing operation of the valve body. A flow path can be secured. Therefore, it is possible to easily manufacture the parts while maintaining the suppression of the inclination and eccentricity of the valve body and the suppression of the response deterioration of the valve body.
Problems, configurations, and effects other than those described above will be clarified by the following description of the embodiments.

1 is a configuration diagram showing a fuel supply system for an internal combustion engine including a high-pressure fuel supply pump according to an embodiment of the invention; FIG. BRIEF DESCRIPTION OF THE DRAWINGS It is a longitudinal cross-sectional view which shows the high pressure fuel supply pump which concerns on the 1st Embodiment of this invention. FIG. 3 is a cross-sectional view of the high-pressure fuel supply pump according to the first embodiment of the present invention shown in FIG. 2, viewed from the line III-III. FIG. 3 is a cross-sectional view showing an enlarged state of a portion of the intake valve mechanism according to the first embodiment of the present invention shown in FIG. 2, showing the valve open state of the intake valve mechanism. FIG. 5 is a cross-sectional view showing the intake valve mechanism according to the first embodiment of the present invention shown in FIG. 4 in an open state; 5 is a perspective view showing an intake valve stopper forming part of the intake valve mechanism according to the first embodiment of the present invention shown in FIG. 4; FIG. FIG. 5 is a cross-sectional view showing an enlarged state of a portion of the intake valve mechanism according to the modification of the first embodiment of the present invention; FIG. 7 is a cross-sectional view showing an enlarged state of a portion of the intake valve mechanism according to the second embodiment of the present invention;

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of a suction valve mechanism and a high-pressure supply fuel pump provided with the same according to the present invention will be described below with reference to the drawings. First, the configuration of a fuel supply system for an internal combustion engine including a high-pressure fuel supply pump according to an embodiment of the present invention will be described with reference to FIG. FIG. 1 is a configuration diagram showing a fuel supply system for an internal combustion engine including a high-pressure fuel supply pump according to an embodiment of the invention.

In FIG. 1, the portion surrounded by broken lines indicates the pump body, which is the main body of the high-pressure fuel supply pump. Mechanisms and parts shown within this dashed line indicate that they are incorporated in the pump body. FIG. 1 is a diagram schematically showing the configuration of the fuel supply system, and the configuration of the high-pressure fuel supply pump shown in FIG. 1 is different from the configuration shown in FIG. 2 and subsequent figures to be described later.

In FIG. 1, a fuel supply system for an internal combustion engine includes, for example, a fuel tank 101 that stores fuel, a feed pump 102 that pumps up and delivers the fuel in the fuel tank 101, and pressurizes the fuel delivered from the feed pump 102. and a plurality of injectors 103 for injecting the high-pressure fuel pressure-fed from the high-pressure fuel supply pump 1 . The high-pressure fuel supply pump 1 is connected to a feed pump 102 via an intake pipe 104 and connected to an injector 103 via a common rail 105 . The injectors 103 are attached to the common rail 105 according to the number of cylinders of the engine. A pressure sensor 106 for detecting the pressure of the fuel discharged from the high-pressure fuel supply pump 1 is attached to the common rail 105 . This system is a so-called direct injection engine system that directly injects fuel into the cylinders of the engine.

The high-pressure fuel supply pump 1 includes a pump body 1a having a pressurization chamber 3 for pressurizing fuel, a plunger 4 assembled to the pump body 1a, an intake valve mechanism 300, and a discharge valve mechanism 500. . The plunger 4 pressurizes the fuel in the pressurization chamber 3 by reciprocating motion. The intake valve mechanism 300 functions as a capacity variable mechanism that adjusts the flow rate of fuel sucked into the pressurization chamber 3 . The discharge valve mechanism 500 discharges the fuel pressurized by the plunger 4 to the common rail 105 side. A pressure pulsation reduction mechanism 12 is provided on the upstream side of the intake valve mechanism 300 to reduce the pressure pulsation generated in the high-pressure fuel supply pump 1 from reaching the intake pipe 104 .

The feed pump 102 , the intake valve mechanism 300 of the high-pressure fuel supply pump 1 , and the injector 103 are electrically connected to an engine control unit (hereinafter referred to as ECU) 107 and controlled by control signals output from the ECU 107 . A detection signal from the pressure sensor 106 is input to the ECU 107 .

In the fuel supply system, fuel in a fuel tank 101 is pumped up by a feed pump 102 driven based on a control signal from an ECU 107 . This fuel is pressurized to an appropriate feed pressure by the feed pump 102 and sent to the low-pressure fuel suction port 2 a of the high-pressure fuel supply pump 1 through the suction pipe 104 . The fuel that has passed through the low-pressure fuel suction port 2a reaches the suction valve mechanism 300 via the pressure pulsation reduction mechanism 12 and the suction passage 2d. The fuel that has flowed into the intake valve mechanism 300 passes through openings that are opened and closed by the intake valve 30 . This fuel is sucked into the pressure chamber 3 during the downward stroke of the plunger 4 which reciprocates, and is pressurized in the pressure chamber 3 during the upward stroke of the plunger 4 . The pressurized fuel is pumped from the discharge valve mechanism 500 to the common rail 105 through the fuel discharge port 2h. High-pressure fuel in the common rail 105 is injected into each cylinder of the engine by each injector 103 driven based on control signals from the ECU 107 . The high-pressure fuel supply pump 1 discharges a desired fuel flow rate by opening and closing the intake valve 30 of the intake valve mechanism 300 according to a control signal from the ECU 107 to the intake valve mechanism 300 .

[First embodiment]
Next, the configuration of each part of the high-pressure fuel supply pump according to the first embodiment of the invention will be described with reference to FIGS. 2 and 3. FIG. BRIEF DESCRIPTION OF THE DRAWINGS It is a longitudinal cross-sectional view which shows the high pressure fuel supply pump which concerns on the 1st Embodiment of this invention. FIG. 3 is a cross-sectional view of the high-pressure fuel supply pump according to the first embodiment of the present invention shown in FIG. 2, viewed from the line III--III.

2 and 3, the high-pressure fuel supply pump 1 includes a pump body 1a having a pressure chamber 3 for pressurizing fuel, a plunger 4 assembled to the pump body 1a, an intake valve mechanism 300, and a discharge valve mechanism 500. (shown only in FIG. 3), and a relief valve mechanism 600 . The high-pressure fuel supply pump 1 is attached to the pump mounting portion 111 (shown only in FIG. 2) of the engine via a mounting flange 1b (shown only in FIG. 3) provided on the pump body 1a by a plurality of bolts (not shown). Fixed. An O-ring 15 (shown in FIG. 2) is fitted to the outer peripheral surface of the pump body 1a that fits with the pump mounting portion 111. As shown in FIG. The O-ring 15 seals between the pump mounting portion 111 and the pump body 1a to prevent engine oil or the like from leaking to the outside of the engine.

As shown in FIG. 2, an insertion hole 1d extending in the longitudinal direction (the vertical direction in FIG. 2) is formed in the central portion of the pump body 1a, and a cylinder 5 is press-fitted into the insertion hole 1d. installed. The cylinder 5 guides the reciprocating motion of the plunger 4 and forms a part of the pressure chamber 3 together with the pump body 1a. A fixing portion 1c provided at the opening edge of the insertion hole 1d of the pump body 1a is engaged with the central portion of the cylinder 5 in the axial direction. The fixing portion 1c presses the cylinder 5 toward the pressurizing chamber 3, and the fuel pressurized in the pressurizing chamber 3 flows from between the end surface of the cylinder 5 and the wall surface of the insertion hole portion 1d of the pump body 1a to the low pressure side. sealed to prevent leakage.

A tappet 6 is provided on the tip side of the plunger 4 (lower end side in FIG. 2). The tappet 6 converts the rotational motion of a cam 112 attached to a camshaft (not shown) of the engine into linear reciprocating motion and transmits it to the plunger 4 . The plunger 4 is pressed against the tappet 6 by the biasing force of the spring 8 via the retainer 7 . As a result, the plunger 4 reciprocates along the cylinder 5 and the volume of the pressurizing chamber 3 increases or decreases as the tappet 6 reciprocates along with the rotational movement of the cam 112 .

A seal holder 9 having a cylindrical portion with a bottom is fixed to the pump body 1 a closer to the engine than the cylinder 5 , and the plunger 4 passes through the bottom of the seal holder 9 . Inside the seal holder 9, an auxiliary chamber 9a is formed for storing fuel leaking from the pressure chamber 3 through the sliding portion of the plunger 4 and the cylinder 5. As shown in FIG. A plunger seal 10 is held inside the seal holder 9 on the bottom side (lower end side in FIG. 2). The plunger seal 10 is installed so that the outer peripheral surface of the plunger 4 is in slidable contact therewith. The plunger seal 10 prevents the fuel in the auxiliary chamber 9a from flowing out to the engine side when the plunger 4 reciprocates. At the same time, it prevents lubricating oil (including engine oil) in the engine from flowing into the pump body 1a from the engine side.

A suction joint 17 is attached to the outer peripheral wall of the pump body 1a, as shown in FIG. A suction pipe 104 (see FIG. 1) is connected to the suction joint 17, and fuel from a fuel tank 101 (see FIG. 1) is supplied to the interior of the high-pressure fuel supply pump 1 through a low-pressure fuel suction port 2a of the suction joint 17. be done. A suction passage 2b is provided in the pump body 1a immediately downstream of the low-pressure fuel suction port 2a, and a suction filter 18 is arranged in the suction passage 2b. The intake filter 18 has the function of preventing foreign matter existing between the fuel tank 101 and the low-pressure fuel intake port 2a from being absorbed into the high-pressure fuel supply pump 1 by the flow of fuel.

Further, as shown in FIG. 2, a cup-shaped cover 13 is attached to the end portion (upper end portion in FIG. 2) of the pump body 1a on the side opposite to the engine. A low-pressure fuel chamber 2c is formed by the tip of the pump body 1a and the cover 13. As shown in FIG. A pressure pulsation reduction mechanism 12 is arranged in the low-pressure fuel chamber 2c. The pressure pulsation reduction mechanism 12 is composed of, for example, a damper 12a as a mechanism body and a plurality of holding members 12b that hold the damper 12a inside the low-pressure fuel chamber 2c. The damper 12a is, for example, formed by stacking two metal diaphragms and filling the space between the two metal diaphragms with an inert gas. The damper 12a reduces pressure pulsation by expanding and contracting the space containing the inert gas. A plurality of holding members 12b hold the damper 12a in the low-pressure fuel chamber 2c by sandwiching the damper 12a between the cover 13 and the tip of the pump body 1a.

Further, as shown in FIGS. 2 and 3, the outer peripheral wall of the pump body 1a is provided with a first mounting hole portion 1f. The first mounting hole 1f communicates with the low-pressure fuel chamber 2c through a suction passage 2d (only shown in FIG. 2) formed in the pump body 1a, and presses through a suction passage 2e formed in the pump body 1a. It communicates with the pressure chamber 3 .

A suction valve mechanism 300 is attached to the first attachment hole portion 1f. The intake valve mechanism 300 is of an electromagnetic drive type, and is roughly divided into a valve body unit, an anchor unit, and a solenoid unit.

The valve body unit has, for example, an intake valve 30, an intake valve housing 31, an intake valve stopper 32, and an intake valve biasing spring 33. The suction valve housing 31 includes a cylindrical valve housing portion 31a for housing the suction valve 30, a valve seat portion 31b on which the suction valve 30 can be seated and unseated, and a rod 39 of an anchor unit, which will be described later. The supporting rod guide portion 31c is integrally formed. The intake valve housing 31 is provided with a plurality of intake ports 31d communicating with the intake passage 2d of the pump body 1a on the downstream side of the low-pressure fuel chamber 2c. The intake valve stopper 32 is fixed to the opening of the valve accommodating portion 31a of the intake valve housing 31, and restricts the movement (lift) of the intake valve 30 in the valve opening direction. The suction valve biasing spring 33 is arranged between the suction valve 30 and the suction valve stopper 32, and biases the suction valve 30 toward the valve seat portion 31b (valve closing direction). The details of the structure of each component of the valve body unit will be described later.

The anchor unit includes a fixed core 35 and an outer core 36 as fixed portions, and an anchor 38 and rod 39 as movable portions. The fixed core 35 and the outer core 36 are connected to each other via a tubular seal ring 37 . The fixed core 35 and the anchor 38 are arranged so as to face each other, and the facing end surfaces of the fixed core 35 and the anchor 38 form magnetic attraction surfaces on which magnetic attraction acts between them. The anchor 38 is arranged radially inward of the outer core 36 and the seal ring 37 so as to be movable toward and away from the fixed core 35 . The fixed core 35, outer core 36, and anchor 38 form a magnetic circuit around an electromagnetic coil 43 of the solenoid unit, which will be described later. The rod 39 has a tip on one side (the right side in FIGS. 2 and 3) that can come into contact with the intake valve 30, and a rod collar 39a on the other side (the left side in FIGS. 2 and 3). have. The rod 39 is slidably supported on the inner peripheral side of the rod guide portion 31c of the intake valve housing 31 and the inner peripheral side of the anchor 38, and the rod collar portion 39a is engaged with the portion of the anchor 38 on the fixed core 35 side. configured to be compatible.

The anchor unit further comprises a rod biasing spring 40 and an anchor biasing spring 41 that bias the movable part. A rod biasing spring 40 is arranged between the fixed core 35 and the rod 39 . The rod biasing spring 40 biases the rod 39 in a direction (valve opening direction) to pull the rod 39 away from the fixed core 35 , and applies force to the intake valve 30 via the rod 39 in the valve opening direction. An anchor biasing spring 41 is arranged between the rod guide portion 31 c of the intake valve housing 31 and the anchor 38 . The anchor biasing spring 41 biases the anchor 38 toward the fixed core 35 side. The rod biasing spring 40 is set to exert a necessary and sufficient biasing force against the anchor biasing spring 41 to keep the suction valve 30 open when the electromagnetic coil 43 is not energized.

The solenoid unit has, for example, an electromagnetic coil 43, a connector fitting portion 44 (only shown in FIG. 2), and a connection terminal 45. As shown in FIG. The electromagnetic coil 43 is annularly formed on the outer peripheral side of the fixed core 35 and the outer core 36 of the anchor unit. The connector fitting portion 44 is formed of a resin material or the like, and is connectable to the connector fitting portion of the control line of the ECU 107 (see FIG. 1). The connection terminal 45 is partially embedded in the connector fitting portion 44 and electrically connected to the electromagnetic coil 43 at one end. The other end of the connection terminal 45 is exposed in the internal space of the connector fitting portion 44 and is connectable to the control line of the ECU 107 (see FIG. 1).

Further, as shown in FIG. 3, a second mounting hole portion 1g is provided at a position shifted in the circumferential direction from the first mounting hole portion 1f in the outer peripheral wall of the pump body 1a. The second mounting hole portion 1g communicates with the pressurizing chamber 3 through a discharge passage 2f formed in the pump body 1a, and a fuel discharge port, which will be described later, through a discharge passage 2g formed in the pump body 1a. 2h.

A discharge valve mechanism 500 is attached to the second attachment hole portion 1g. The discharge valve mechanism 500 includes, for example, a discharge valve seat 51 , a discharge valve 52 that can be seated and separated from the discharge valve seat 51 , and a discharge valve spring 53 that biases the discharge valve 52 toward the discharge valve seat 51 . and a discharge valve stopper 54 for limiting the movement (lift) of the discharge valve 52 in the valve opening direction. The discharge valve seat 51 is held in the pump body 1a by, for example, press fitting. The discharge valve 52 is configured to be guided by the outer peripheral surface of the shaft-like protrusion of the discharge valve stopper 54 . The discharge valve stopper 54 is held by the plug 55 . The plug 55 is welded to the pump body 1a and has a function of preventing fuel from leaking to the outside.

In the discharge valve mechanism 500, when there is no fuel differential pressure between the pressure chamber 3 and the internal space on the secondary side of the discharge valve 52 (the internal space communicating with the discharge passage 2g), the biasing force of the discharge valve spring 53 is applied. , the discharge valve 52 is pressed against the discharge valve seat 51 to be closed. The discharge valve 52 is configured to open against the biasing force of the discharge valve spring 53 only when the fuel pressure in the pressure chamber 3 becomes higher than the fuel pressure in the internal space on the secondary side of the discharge valve 52 . ing. The discharge valve mechanism 500 configured as described above functions as a check valve that restricts the flow direction of the fuel.

Further, as shown in FIGS. 2 and 3, a third mounting hole portion 1h is provided at a position opposite to the first mounting hole portion 1f across the pressure chamber 3 in the outer peripheral wall of the pump body 1a. there is A discharge joint 19 having a fuel discharge port 2h is fixed to the opening of the third mounting hole 1h. A relief valve mechanism 600 is arranged in a housing space formed by the third mounting hole portion 1h of the pump body 1a and the internal space of the discharge joint 19. As shown in FIG.

The relief valve mechanism 600 includes, for example, a relief valve seat 61, a relief valve 62 that contacts and separates from the relief valve seat 61, a relief valve holder 63 that holds the relief valve 62, and a relief valve 62 attached to the relief valve seat 61 side. It consists of a relief spring 64 for biasing and a relief valve housing 65 containing these members 61, 62, 63, 64. As shown in FIG. The relief valve housing 65 also functions as a relief body that forms a relief valve chamber. After the relief spring 64, the relief valve holder 63, and the relief valve 62 are inserted in this order into the relief valve housing 65, the relief valve seat 61 is press-fitted and fixed. The relief spring 64 has one end in contact with the relief valve housing 65 and the other end in contact with the relief valve holder 63 . The relief valve 62 is pressed against the relief valve seat 61 by the biasing force of the relief spring 64 via the relief valve holder 63, thereby blocking the flow of fuel. The opening pressure of the relief valve 62 is determined by the biasing force of the relief spring 64 . The relief valve mechanism 600 in this embodiment communicates with the pressure chamber 3 via a relief passage 2i formed in the pump body 1a. Although the relief valve mechanism 600 is arranged in the space formed by the third mounting hole portion 1h of the pump body 1a and the internal space of the discharge joint 19, it is not limited to this.

The relief valve mechanism 600 is actuated when the common rail 105 (see FIG. 1) or the members beyond it have some problem and the common rail 105 becomes abnormally high pressure. That is, the relief valve mechanism 600 is configured to open the relief valve 62 against the biasing force of the relief spring 64 when the differential pressure between the upstream side and the downstream side of the relief valve 62 exceeds the set pressure. It is The relief valve mechanism 600 in this embodiment is configured to return fuel to the pressurization chamber 3 when the valve is opened, but it may be configured to return fuel to the low-pressure fuel chamber 2c or the intake passage 2b. be.

Next, the structure of the valve body unit of the intake valve mechanism according to the first embodiment of the present invention will be described with reference to FIGS. 4 to 6. FIG. 4 and 5 are cross-sectional views showing an enlarged state of a portion of the intake valve mechanism according to the first embodiment of the present invention shown in FIG. 4 shows the open state of the intake valve mechanism, while FIG. 5 shows the closed state of the intake valve mechanism. 6 is a perspective view showing an intake valve stopper forming part of the intake valve mechanism according to the first embodiment of the present invention shown in FIG. 4. FIG.

4 and 5, the valve body unit of the intake valve mechanism 300 includes the intake valve 30, the intake valve housing 31, the intake valve stopper 32, and the intake valve biasing spring 33, as described above. 4 and 5, part of the rod guide portion 31c of the intake valve housing 31 is omitted.

The intake valve housing 31 has a substantially axially symmetrical shape with the axis A as the center. As described above, the intake valve housing 31 has the valve accommodating portion 31a, the intake valve seat portion 31b, and the rod guide portion 31c (only a portion of which is shown). The valve accommodating portion 31a is a cylindrical portion that opens to one side of the axis A (the right side in FIGS. 4 and 5). The intake valve seat portion 31b is an annular portion projecting inwardly from the valve housing portion 31a, and a flow path is formed inside in the radial direction thereof. The rod guide portion 31c is positioned on the other side of the axis A (the left side in FIGS. 4 and 5) with respect to the valve housing portion 31a, and slidably supports the rod 39 of the anchor unit on the inner peripheral portion. be.

The intake valve 30 is movably arranged inside the valve accommodating portion 31 a of the intake valve housing 31 . The intake valve 30 is a valve body that is substantially axially symmetrical about the axis A. As shown in FIG. The intake valve 30 includes, for example, a valve body portion 71 seated on the intake valve seat portion 31b of the intake valve housing 31, and a guided portion extending from the valve body portion 71 toward the intake valve stopper 32 (valve opening direction). 72 are integrally formed.

The valve main body portion 71 is formed in a plate shape, for example, and is located on the side opposite to the first surface 71a as a seat surface to be seated on the intake valve seat portion 31b of the intake valve housing 31 and the first surface 71a. and a second surface 71b. One end of the rod 39 contacts the first surface 71a.

The guided portion 72 is formed in a tubular shape, and is a portion that slides on a tubular portion 82 (to be described later) of the intake valve stopper 32 and is guided in the contact/separation direction with respect to the valve seat portion 31b. The guided portion 72 according to the present embodiment is configured such that an outer peripheral surface 72 a thereof serves as a sliding surface on which the cylindrical portion 82 of the intake valve stopper 32 slides. The guided portion 72 is provided radially inward of the valve seat portion 31 b of the valve body portion 71 . That is, the guided portion 72 is formed such that its outer diameter D2 is smaller than the seat diameter D1 of the valve seat portion 31b. A tip portion 72c of the guided portion 72 in the direction of the axis A is configured as a contact portion that contacts the intake valve stopper 32 when the intake valve 30 moves in the valve opening direction.

An internal space surrounded by the inner peripheral surface 72 b of the guided portion 72 forms an accommodation space S<b>1 that accommodates the intake valve biasing spring 33 together with the intake valve stopper 32 . A portion of the valve main body portion 71 radially inward of the guided portion 72 forms a spring seat surface 71c with which one end side (the left end side in FIGS. 4 and 5) of the intake valve biasing spring 33 contacts. .

The guided portion 72 has at least one through-hole 73 (two are shown in FIGS. 4 and 5) penetrating in the radial direction. The through-hole 73 communicates between the inner space in the radial direction of the guided portion 72 and the outer space in the outer side in the radial direction. At least part of the radially outer opening of the through-hole 73 is in the valve-open state (see FIG. 4) in which the distal end portion 72c of the guided portion 72 is in contact with the suction valve stopper 32. It is formed at a position where it does not overlap a sliding surface (inner peripheral surface 82a) of a cylindrical portion 82 of the intake valve stopper 32, which will be described later, in the moving direction of the intake valve stopper 30. As shown in FIG.

The suction valve stopper 32 is located on the opposite side of the valve seat portion 31 b with respect to the suction valve 30 , and is arranged at a position closer to the pressure chamber 3 than the suction valve 30 . 4 to 6, the intake valve stopper 32 is composed of a central stopper main body 81 and a cylindrical portion extending from the outer edge of the stopper main body 81 toward the valve seat 31b. A tubular portion 82 and an annular cover portion 83 protruding radially outward from the tip of the tubular portion 82 (the end on the side of the valve seat portion 31b) are integrally formed as one component. . The intake valve stopper 32 has a substantially axially symmetrical shape with respect to the axis A, and is configured to cover the valve body portion 71 from the second surface 71b side. The intake valve stopper 32 according to the present embodiment functions not only as a stopper portion that restricts movement of the intake valve 30 in the valve opening direction, but also as a guide portion that guides the movement of the intake valve 30. A barrier portion that prevents the flow of fuel from flowing directly toward the second surface 71b of the valve main body portion 71 of the intake valve 30 when the fuel in the pressure chamber 3 returns to the upstream side (intake port 31d side) of the intake valve 30. It has a function as That is, in the present embodiment, the intake valve stopper 32, which is a part, serves as a valve stopper having both a stopper portion that restricts the movement of the intake valve 30 in the valve opening direction and a guide portion that guides the movement of the intake valve 30. It is configured.

The stopper body portion 81 functions as a stopper portion that restricts the movement (lift) of the intake valve 30 in the valve opening direction. The stopper body portion 81 has an annular contact surface 81a with which the tip portion 72c of the guided portion 72 of the intake valve 30 contacts. A concave portion 86 is formed radially inward of the contact surface 81 a of the stopper body portion 81 . The recessed portion 86 constitutes an accommodation space S<b>1 for the intake valve biasing spring 33 together with the internal space of the guided portion 72 . The bottom surface of the recess 86 forms a spring seat surface 86a with which the other end side (the right end side in FIGS. 4 and 5) of the intake valve biasing spring 33 contacts.

The cylindrical portion 82 functions as a guide portion that guides the movement of the intake valve 30 in the contact/separation direction of the valve seat portion 31b. The tubular portion 82 as the guide portion forms a sliding contact surface in which the inner peripheral surface 82a is in sliding contact with the outer peripheral surface 72a of the guided portion 72. As shown in FIG. The cylindrical portion 82 is set with an appropriate gap and sliding length with respect to the outer peripheral surface 72a of the guided portion 72 for suppressing inclination and eccentricity of the valve body portion 71 with respect to the valve seat portion 31b.

A chamfered portion 84 is formed on the inner peripheral portion of the opening edge of the cylindrical portion 82 . One side of the chamfered portion 84 is continuous with the inner peripheral surface 82 a , and the other side is continuous with a later-described facing surface 83 a of the cover portion 83 . At least a part of the through hole 73 of the guided portion 72 is formed in the space surrounded by the chamfered portion 84 when the tip portion 72c of the guided portion 72 is in contact with the stopper body portion 81 in the valve open state. is configured to open. The chamfered portion 84 according to the present embodiment is formed as an R chamfer, for example.

The cover portion 83 is positioned radially outward of the guided portion 72 of the suction valve 30 and covers a portion of the valve body portion 71 radially outward of the guided portion 72 from the second surface 71b side. The cover portion 83 faces the second surface 71b of the valve body portion 71 with a gap G therebetween in the valve open state (see FIG. 4) in which the distal end portion 72c of the guided portion 72 contacts the stopper body portion 81. It has an annular facing surface 83a. That is, in the range from the closed state (see FIG. 5) to the open state (see FIG. 4) of the intake valve 30, between the second surface 71b of the valve main body portion 71 and the facing surface 83a of the cover portion 83, A gap G is formed. The facing surface 83 a is continuous with the chamfered portion 84 on the inner peripheral edge side thereof.

An outer peripheral portion 83b of the cover portion 83 is a portion that is press-fitted into the opening portion of the valve accommodating portion 31a of the intake valve housing 31 . A notch 87 (shown in FIG. 6) is provided in the outer peripheral portion 83b of the cover portion 83 so as to penetrate the cover portion 83 in the thickness direction (the direction of the axis A). For example, a plurality of notches 87 (four in FIG. 6) are provided at intervals in the circumferential direction. The notch 87 connects the space located upstream of the intake valve stopper 32 and the space located downstream of the intake valve stopper 32 (the space on the intake valve 30 side and the space on the pressurizing chamber 3 side with the intake valve stopper 32 as a boundary). make up the road.

A suction valve biasing spring 33 is arranged in a housing space S1 formed by the inner space of the guided portion 72 of the suction valve 30 and the suction valve stopper 32 (the inner space of the concave portion 86 and the cylindrical portion 82). . One end of the intake valve biasing spring 33 is in contact with the spring seat surface 71c inside the guided portion 72 of the valve body portion 71, and the other end is in contact with the spring seat surface 86a of the stopper body portion 81 of the intake valve stopper 32. is in contact with At both ends of the intake valve biasing spring 33, the radial deflection is restricted by the spring seat surfaces 71c and 86a. The inner peripheral surface 72b of the guided portion 72 and the side surface of the recessed portion 86 of the intake valve stopper 32 are provided with recesses so that the side surfaces of the intake valve biasing spring 33 do not rub strongly. The capacity of the accommodation space S<b>1 for the intake valve biasing spring 33 increases or decreases according to the opening/closing operation (movement) of the intake valve 30 .

Fuel flows into and out of the accommodation space S1 via the flow path P by increasing or decreasing the volume of the accommodation space S1. The flow path P connects the accommodation space S1 of the intake valve biasing spring 33 and the space on the secondary side of the intake valve 30 (downstream side of the valve seat portion 31b). The flow path P is a space surrounded by the through hole 73 of the guided portion 72 of the suction valve 30 and the chamfered portion 84 of the suction valve stopper 32, the second surface 71b of the valve body portion 71 of the suction valve 30, and the suction valve stopper 32. and a gap G formed between the cover portion 83 and the facing surface 83a of the cover portion 83. As shown in FIG. Further, the gap formed between the outer peripheral surface 72a of the guided portion 72 and the inner peripheral surface 82a of the cylindrical portion 82 of the suction valve stopper 32 also functions as part of the flow path P. The housing space S1 for the valve biasing spring 33 and the space surrounded by the chamfered portion 84 are communicated with each other.

In the present embodiment, when the suction valve 30 is opened, the tip portion 72c of the guided portion 72 of the suction valve 30 and the contact surface 81a of the stopper body portion 81 of the suction valve stopper 32 are in contact with each other. The valve body portion 71 of the suction valve 30 and the cover portion 83 of the suction valve stopper 32 are configured to be out of contact with each other. That is, at any position between the closed state (see FIG. 5) and the open state (see FIG. 4) of the intake valve 30, the gap between the second surface 71b of the valve main body portion 71 and the facing surface 83a of the cover portion 83 is A gap G that constitutes a part of the flow path P is formed in the . Therefore, it is not necessary to machine a radially extending groove for securing the flow path P in the intake valve 30 and the intake valve stopper 32 . When machining grooves extending radially or axially in a substantially axially symmetrical structure such as the suction valve 30 or the suction valve stopper 32, it is difficult to complete the cutting process with a single machine tool. . In addition, since the parts must be fixed again according to the change in the machining method, there is a tendency for the number of man-hours for cutting to increase. On the other hand, in the intake valve 30 and the intake valve stopper 32 according to the present embodiment, it is not necessary to machine the grooves extending in the radial direction and the axial direction of the parts, so that the machining can be simplified. , which enables easy and low-cost part manufacturing.

Further, in the present embodiment, a chamfered portion 84 is formed continuously between the inner peripheral surface 82a as the sliding surface of the cylindrical portion 82 of the intake valve stopper 32 and the opposing surface 83a forming the gap G in the cover portion 83. By doing so, communication between the gap G forming the flow path P and the through hole 73 of the guided portion 72 is ensured when the suction valve 30 is opened. The chamfered portion 84 can be realized by processing using a lathe, and parts can be manufactured easily and at low cost.

Further, in the present embodiment, a notch 87 is provided in the cover portion 83 of the intake valve stopper 32 so as to penetrate the cover portion 83 in the direction of the axis A (thickness direction of the cover portion 83). side space and downstream space (a space on the suction valve 30 side and a space on the pressurizing chamber 3 side with the suction valve stopper 32 as a boundary) are formed. In the machining of the notch 87, the direction of chucking the suction valve stopper 32 is not limited, so the suction valve stopper 32 can be chucked in a direction that facilitates the work, facilitating the manufacture of parts.

Next, operation of the high-pressure fuel supply pump will be described with reference to FIGS. 2 to 5. FIG.

In the high-pressure fuel supply pump 1 shown in FIG. 3, fuel flows in from the low-pressure fuel inlet 2a of the suction joint 17, and the suction filter 18 removes foreign substances in the fuel. After that, the fuel flowing into the low-pressure fuel chamber 2c shown in FIG. 2 reaches the intake valve mechanism 300 through the intake passage 2d of the pump body 1a. At this time, pressure pulsation propagating in the fuel is reduced by the damper 12a in the low-pressure fuel chamber 2c.

When the plunger 4 shown in FIG. 2 moves downward by the rotation of the cam 112 to move toward the cam 112, the volume of the pressurizing chamber 3 increases and the fuel pressure in the pressurizing chamber 3 decreases. At this time, when the fuel pressure in the pressurizing chamber 3 shown in FIG. 4 becomes lower than the pressure at the intake port 31d of the intake valve mechanism 300, the intake valve 30 of the intake valve mechanism 300 is opened. Therefore, the fuel flows into the pressurization chamber 3 through the intake valve 30 . This state is called an inhalation process.

The intake valve 30 is opened by the load L<b>1 from the rod 39 acting in the valve opening direction against the biasing force of the intake valve biasing spring 33 . In the valve opening operation of the intake valve 30, the movement in the lift direction is guided by the outer peripheral surface 72a of the guided portion 72 sliding against the inner peripheral surface 82a of the cylindrical portion 82 of the intake valve stopper 32. Further, the tip portion 72c of the guided portion 72 comes into contact with the contact surface 81a of the stopper body portion 81 of the intake valve stopper 32, thereby restricting movement in the lift direction. Since the cylindrical portion 82 functions as a guide portion for the intake valve 30, eccentricity and inclination of the valve body portion 71 of the intake valve 30 with respect to the valve seat portion 31b are suppressed. Therefore, the occurrence of cavitation erosion due to the eccentricity of the valve body portion 71 can be suppressed, and the unstable valve opening operation due to the inclination of the valve body portion 71 can be suppressed.

The opening operation of the intake valve 30 reduces the volume of the accommodation space for the intake valve biasing spring 33 formed between the intake valve 30 and the intake valve stopper 32 . At this time, the fuel in the storage space flows through the through hole 73 that constitutes the flow path P, the gap formed between the outer peripheral surface 72a of the guided portion 72 and the inner peripheral surface 82a of the cylindrical portion 82, and It flows into the space on the secondary side of the intake valve 30 through the gap G formed between the second surface 71b of the valve main body 71 and the opposing surface 83a of the cover portion 83 of the intake valve stopper 32 . As a result, the pressure in the housing space does not increase so much, so the responsiveness of the intake valve 30 during the valve opening operation does not deteriorate.

After that, the plunger 4 shown in FIG. 2 turns to upward movement after finishing the downward movement. Here, the electromagnetic coil 43 is kept in a non-energized state, and no magnetic biasing force is generated. In this case, the intake valve 30 is kept open by the biasing force of the rod biasing spring 40 transmitted via the rod 39 (see FIG. 4). The volume of the pressurizing chamber 3 decreases as the plunger 4 moves upward, but when the intake valve 30 is open, the fuel once drawn into the pressurizing chamber 3 flows through the opening of the intake valve 30 again into the pump body 1a. , the pressure in the pressurizing chamber 3 does not rise. This state is called a return stroke.

In this state, when a control signal from the ECU 107 (see FIG. 1) is applied to the intake valve mechanism 300 , current flows through the electromagnetic coil 43 via the connection terminal 45 . Then, a magnetic attractive force acts between the fixed core 35 and the anchor 38, and the fixed core 35 and the anchor 38 collide with each other on the magnetically attractive surfaces facing each other. The magnetic attraction force overcomes the biasing force of the rod biasing spring 40 to bias the anchor 38 , and the anchor 38 engages with the rod flange 39 a to move the rod 39 away from the suction valve 30 .

At this time, the intake valve 30 is closed by the fluid force caused by the urging force of the intake valve urging spring 33 and the fuel flowing into the intake passage 2d (see FIG. 5). As shown in FIG. 5, the valve closing operation of the intake valve 30 is performed by sliding the outer peripheral surface 72a of the guided portion 72 against the inner peripheral surface 82a of the tubular portion 82, thereby moving the intake valve 30 in the direction toward the valve seat portion 31b. movement is guided, and finally, the first surface 71a of the valve body portion 71 is seated on the valve seat portion 31b. Since the cylindrical portion 82 functions as a guide portion for the intake valve 30, inclination and eccentricity of the valve body portion 71 with respect to the valve seat portion 31b are suppressed. Therefore, it is possible to suppress the occurrence of unstable valve closing operation and cavitation erosion due to inclination or eccentricity of the valve body portion 71 with respect to the valve seat portion 31b.

The closing operation of the intake valve 30 increases the volume of the accommodation space for the intake valve biasing spring 33 . At this time, the fuel in the space on the secondary side of the intake valve 30 flows through the gap G forming the flow path P, the space surrounded by the chamfered portion 84, the through hole 73, and the outer peripheral surface 72a of the guided portion 72. It flows into the housing space through a gap formed between the cylindrical portion 82 and the inner peripheral surface 82a. As a result, the closing operation of the intake valve 30 is performed smoothly.

When the intake valve 30 closes, the fuel pressure in the pressurizing chamber 3 rises in accordance with the upward motion of the plunger 4, and when it exceeds the pressure at the fuel discharge port 2h shown in FIG. opens. As a result, the high-pressure fuel in the pressurizing chamber 3 is discharged from the fuel discharge port 2h through the discharge passage 2f, the discharge valve mechanism 500, and the discharge passage 2g, and supplied to the common rail 105 (see FIG. 1). This state is called a discharge stroke.

That is, the upward movement of the plunger 4 from the lower start point to the upper start point shown in FIG. 2 consists of a return stroke and a discharge stroke. Further, by controlling the energization timing of the electromagnetic coil 43 of the intake valve mechanism 300, the flow rate of the discharged high-pressure fuel can be controlled. If the timing of energizing the electromagnetic coil 43 is advanced, the proportion of the return stroke during the rising movement of the plunger 4 becomes small, and the proportion of the discharge stroke becomes large. That is, less fuel is returned from the pressurization chamber 3 to the intake passage 2d, while more fuel is discharged at high pressure. On the other hand, if the energization timing is delayed, the ratio of the return stroke during the upward motion becomes large, and the ratio of the discharge stroke becomes small. That is, while the amount of fuel returned from the pressurization chamber 3 to the intake passage 2d increases, the amount of fuel discharged at high pressure decreases. The timing of energizing the electromagnetic coil 43 is controlled by a command from the ECU 107 .

As described above, in the high-pressure fuel supply pump 1, by controlling the timing of energization of the electromagnetic coil 43, the amount of fuel discharged under high pressure can be controlled to the amount required by the engine.

If the pressure at the fuel discharge port 2h becomes higher than the set pressure of the relief valve mechanism 600 due to some failure or the like, the relief valve 62 is opened and abnormally high pressure fuel is applied through the relief passage 2i. The pressure chamber 3 is relieved.

In the present embodiment, the leading end portion 72c of the guided portion 72 of the intake valve 30 that slides against the cylindrical portion 82 of the intake valve stopper 32 that functions as a guide portion contacts the intake valve stopper 32, Movement of the intake valve 30 in the valve opening direction is restricted. That is, the guided portion 72 is configured such that its axial length (direction of the axis A) is longer than the length of the cylindrical portion 82 in its axial direction (direction of the axis A). Therefore, in the guided portion 72 of the present embodiment, the valve body portion 71 of the intake valve 30 is brought into contact with the intake valve stopper 32 to restrict the movement of the intake valve 30 in the valve opening direction. to lengthen the sliding portion. Thereby, the stability of the opening/closing operation of the intake valve 30 can be improved.

Further, in the present embodiment, the guided portion 72 is provided at a position radially inside the valve seat portion 31b of the valve body portion 71 . When the intake valve 30 is open, as shown in FIG. 4, the radial central portion of the valve body portion 71 is pressed in the valve opening direction by the distal end portion of the rod 39 (see white arrow L1). The distal end portion 72c of the guided portion 72 contacts the stopper body portion 81 and is pressed in the valve closing direction (see the white arrow L2). That is, when the valve is opened, the suction valve 30 is sandwiched between the rod 39 and the suction valve stopper 32, and the plate-like valve body 71 is bent. However, by providing the guided portion 72 at a position radially inner than the valve seat portion 31b in the valve body portion 71 (position near the point of action of the rod 39), the guided portion 72 functions as a rib to The rigidity of the portion 71 is strengthened, and the deflection (deformation) of the valve body portion 71 can be suppressed. Therefore, the reliability of the intake valve 30 is improved, and the thickness and weight of the valve body 71 can be reduced.

As described above, the intake valve mechanism 300 according to the first embodiment of the present invention includes the intake valve 30 (valve element) that can be seated and unseated with respect to the valve seat portion 31b (valve seat), a suction valve stopper 32 (valve stopper) located on the opposite side of the valve seat portion 31b (valve seat) with respect to the valve 30 (valve disc) and restricting the movement of the suction valve 30 (valve disc) in the valve opening direction; It has The intake valve 30 (valve element) includes a valve body portion 71 that is seated on a valve seat portion 31b (valve seat), and a suction valve stopper from a position radially inside the valve seat portion 31b (valve seat) in the valve body portion 71. 32 (valve stopper) side. The suction valve stopper 32 (valve stopper) includes a stopper body portion 81 (stopper portion) that restricts the movement of the suction valve 30 (valve body) in the valve opening direction by coming into contact with the tip portion 72c of the guided portion 72; Extending from the stopper body portion 81 (stopper portion) toward the valve seat portion 31b (valve seat), the movement of the suction valve 30 (valve element) is caused by the sliding movement of the guided portion 72 along the valve seat portion 31b (valve seat). It has a cylindrical portion 82 (guide portion) that guides in the contact/separation direction with respect to the valve seat.

According to this configuration, by sliding the guided portion 72 on the cylindrical portion 82 (guide portion) to guide the movement of the intake valve 30 (valve element), the eccentricity and inclination of the intake valve 30 (valve element) can be reduced. can be suppressed. Furthermore, the movement of the suction valve 30 (valve element) in the valve opening direction is not caused by the abutment between the valve body portion 71 and the suction valve stopper 32 (valve stopper), but by the guided portion 72 of the suction valve 30 (valve element). Since the structure is regulated by contact between the tip portion 72c of the suction valve stopper 32 (valve stopper) and the structure of the suction valve 30 (valve body) and the suction valve stopper 32 (valve stopper), the radial direction of the structure Even without forming a groove in the axial direction, it is possible to secure a flow path that allows fluid to flow in and out of the internal space of the cylindrical guided portion 72 when the suction valve 30 (valve body) is opened and closed. . Therefore, it is possible to easily manufacture parts while suppressing inclination and eccentricity of the intake valve 30 (valve element) and suppressing a decrease in responsiveness of the intake valve 30 (valve element).

In the present embodiment, the valve body portion 71 is a plate-like portion having a first surface 71a seated on the valve seat portion 31b (valve seat) and a second surface 71b located on the opposite side of the first surface 71a. The intake valve stopper 32 (valve stopper) has a facing surface 83a located radially outside the guided portion 72 and facing the second surface 71b. Further, a gap G is formed between the second surface 71b and the opposing surface 83a in a state where the tip portion 72c of the guided portion 72 is in contact with the stopper body portion 81 (stopper portion).

According to this configuration, since the opposing surface 83a of the intake valve stopper 32 (valve stopper) faces the second surface 71b of the valve main body 71, the fuel on the downstream side of the intake valve 30 (valve element) flows upstream. When it is returned to the side, the direct flow to the second surface 71b of the valve body portion 71 can be blocked by the intake valve stopper 32 (valve stopper). Further, a gap G formed between the second surface 71b and the opposing surface 83a forms a flow path P connecting the inner space of the guided portion 72 and the radially outer space (downstream space) of the intake valve 30. Since it constitutes a part, it is not necessary to form a groove for securing the flow path P in the valve main body 71 and the intake valve stopper 32 (valve stopper).

Further, the intake valve stopper 32 (valve stopper) according to the present embodiment has an annular cover portion 83 positioned radially outside the guided portion 72 and covering the valve body portion 71 with a gap G therebetween. are doing.

According to this configuration, when the fuel on the downstream side of the intake valve 30 (valve element) is returned to the upstream side, the cover portion 83 of the intake valve stopper 32 (valve stopper) causes the second surface 71b of the valve main body portion 71 to move. can block direct flow to Furthermore, the gap G between the valve main body portion 71 and the cover portion 83 forms part of the flow path P connecting the inner space of the guided portion 72 and the radially outer space (downstream space) of the intake valve 30. Therefore, it is not necessary to form a groove for securing the flow path P in the valve main body 71 and the suction valve stopper 32 (valve stopper).

Further, the guided portion 72 according to the present embodiment has a through hole 73 penetrating in the radial direction. The through hole 73 is open at a position where at least a part thereof does not overlap with the tubular portion 82 (guide portion) when the guided portion 72 is in contact with the stopper body portion 81 (stopper portion).

According to this configuration, fuel can flow into and out of the internal space of the guided portion 72 through the through hole 73 when the intake valve 30 (valve body) is opened and closed. It is possible to reduce the resistance that occurs when the portion 72 flows into and out of the internal space. As a result, a decrease in responsiveness of the opening/closing operation of the intake valve 30 (valve body) is suppressed.

In addition, the intake valve stopper 32 (valve stopper) according to the present embodiment is a single part in which the stopper main body portion 81 (stopper portion) and the guide portion are integrally formed. The guide portion extends from the outer edge portion of the stopper body portion 81 (stopper portion) toward the valve seat portion 31b (valve seat) side, and the outer peripheral surface 72a of the guided portion 72 slides against the inner peripheral surface 82a thereof. It is configured as a moving tubular portion 82 . The cylindrical portion 82 (guide portion) has a chamfered portion 84 at its opening edge. The through-hole 73 opens into a space at least partially surrounded by the chamfered portion 84 when the tip portion 72c of the guided portion 72 is in contact with the stopper body portion 81 (stopper portion).

According to this configuration, the channel P on the radially outer side of the guided portion 72 is expanded by the space formed between the chamfered portion 84 and the outer peripheral surface 72a of the guided portion 72, so that the through hole 73 is expanded. It is possible to reduce the resistance caused to the fuel flowing into and out of the internal space of the guided portion 72 through the guide portion 72 .

Further, the chamfered portion 84 according to the present embodiment is R-chamfered. According to this configuration, the guided portion 72 of the suction valve 30 (valve element) is assembled (inserted) into the cylindrical portion 82 (guide portion) of the suction valve stopper 32 (valve stopper) by the chamfered portion 84 of the R chamfer. ) becomes easier. Also, it becomes smoother. The flow in the vicinity of the chamfered portion 84 flowing in and out through the through hole 73 becomes smooth, and turbulence in the flow can be reduced.

Further, the guide portion according to the present embodiment is configured as a tubular portion 82 in which the outer peripheral surface 72a of the guided portion 72 slides on the inner peripheral surface 82a. In addition, a suction valve biasing spring 33 (biasing spring) that biases the suction valve 30 (valve element) toward the valve seat portion 31b (valve seat) is provided in the internal space surrounded by the inner peripheral surface 72b of the guided portion 72. ) are placed.

According to this configuration, by using the internal space of the guided portion 72 as the accommodation space S1 for the intake valve biasing spring 33 (biasing spring), the accommodation space for the intake valve biasing spring 33 (biasing spring) can be reduced. Since there is no need to provide a separate intake valve mechanism 300, the size of the intake valve mechanism 300 can be reduced.

Further, the high-pressure fuel supply pump 1 according to the present embodiment includes the intake valve mechanism 300 (valve mechanism) described above. Therefore, it is possible to easily manufacture parts while suppressing inclination and eccentricity of the intake valve 30 (valve element) and suppressing a decrease in responsiveness of the intake valve 30 (valve element).

[Modification of First Embodiment]
Next, the configuration of the valve body unit in the intake valve mechanism according to the modified example of the first embodiment of the present invention will be described with reference to FIG. FIG. 7 is a cross-sectional view showing an enlarged state of the valve body unit of the intake valve mechanism according to the modification of the first embodiment of the present invention. In FIG. 7, parts having the same reference numerals as those shown in FIGS. 1 to 6 are the same parts, and detailed description thereof will be omitted.

The intake valve mechanism 300A according to the modification of the first embodiment shown in FIG. 7 differs from the intake valve mechanism 300 (see FIG. 4) according to the first embodiment in that part of the intake valve mechanism 300A The chamfered portion 84A of the opening edge portion of the cylindrical portion 82 of the suction valve stopper 32A constituting . One side of the chamfered portion 84A is continuous with the inner peripheral surface 82a of the tubular portion 82, and the other side is continuous with the facing surface 83a of the cover portion 83. As shown in FIG. The chamfered portion 84A forms at least a portion of the through hole 73 of the guided portion 72 of the intake valve 30 when the tip portion 72c of the guided portion 72 of the intake valve 30 is in contact with the stopper body portion 81 of the intake valve stopper 32A in the valve open state. is configured to open into the space surrounded by the chamfered portion 84A.

Other configurations and structures of the intake valve mechanism 300A according to the modification of the present embodiment are the same as those of the intake valve mechanism 300 according to the first embodiment. 7 shows only one through-hole 73 of the guided portion 72 (two are shown in FIG. 4). The number of through-holes 73 can be reduced in order to reduce the number of processing man-hours if the required flow passage area can be secured.

In the modified example of the first embodiment described above, similarly to the first embodiment, the guided portion 72 is slid along the cylindrical portion 82 (guide portion) to move the intake valve 30 (valve element). By guiding the movement, eccentricity and inclination of the suction valve 30 (valve element) can be suppressed. Further, since the structure restricts the movement of the suction valve 30 (valve element) in the valve opening direction by the contact between the tip portion 7c of the guided portion 72 and the suction valve stopper 32 (valve stopper), the suction valve 30 (valve element) ) and the intake valve stopper 32 (valve stopper), the passage P that allows the fluid to flow into and out of the internal space of the guided portion 72 can be secured without forming grooves in the radial direction or the axial direction. can. Therefore, it is possible to easily manufacture parts while suppressing inclination and eccentricity of the intake valve 30 (valve element) and suppressing a decrease in responsiveness of the intake valve 30 (valve element).

Further, in the intake valve stopper 32A according to this modified example, the chamfered portion 84A is chamfered. According to this configuration, since the boundary line between the inner peripheral surface 82a (sliding surface) of the tubular portion 82 (guide portion) of the intake valve stopper 32A and the chamfered portion 84A is clear, the tubular portion 82 (guide portion) The guide length of the inner peripheral surface 82a (sliding surface) can be controlled with high accuracy. Further, by adjusting the chamfering angle of the chamfered portion 84A, the guide length of the inner peripheral surface 82a (sliding surface) of the cylindrical portion 82 (guide portion) can be adjusted. This makes it possible to adjust the inclination of the valve body portion 71 with respect to the valve seat portion 31b (valve seat) within a desired tolerance range.

[Second embodiment]
Next, the configuration of the valve body unit of the suction valve mechanism according to the second embodiment of the present invention will be described with reference to FIG. FIG. 8 is a cross-sectional view showing an enlarged state of a portion of the intake valve mechanism according to the second embodiment of the present invention. In FIG. 8, parts having the same reference numerals as those shown in FIGS. 1 to 7 are the same parts, and detailed description thereof will be omitted.

The main difference between the intake valve mechanism 300B according to the second embodiment of the invention shown in FIG. 8 and the intake valve mechanism 300 (see FIG. 4) according to the first embodiment is that the intake valve 30B The sliding surface of the guide portion 72B is changed from the outer peripheral surface 72a to the inner peripheral surface 72b, and the portion that functions as the guide portion that guides the movement of the intake valve 30B is different from the cylindrical portion 82B of the intake valve stopper 32B. It is changed to the guide member 89 which is a separate member, and the intake valve biasing spring 33 is arranged not on the inner peripheral side but on the outer peripheral side of the guided portion 72B of the intake valve 30B.

Specifically, the suction valve 30B has a substantially axially symmetrical structure similar to the suction valve 30 (see FIG. 4) of the first embodiment, and the valve body portion 71 and the guided portion 72B are integrally formed. It is a member that has been The suction valve 30B is guided in the contact/separation direction of the valve seat portion 31b by the inner peripheral surface 72b of the guided portion 72B serving as a sliding surface against the guide member 89. As shown in FIG. The internal space surrounded by the inner peripheral surface 72b of the guided portion 72B is a space into which the guide member 89 is inserted, and does not form a housing space for the intake valve biasing spring 33. As shown in FIG.

The suction valve stopper 32B has a substantially axially symmetrical shape similar to the suction valve stopper 32 (see FIG. 4) of the first embodiment, and the stopper body portion 81, the cylindrical portion 82B, and the cover portion 83 are integrally formed. It is a formed member. As in the first embodiment, the stopper main body portion 81 has a contact surface 81a with which the tip portion 72c of the guided portion 72B contacts when the intake valve 30B is opened. The tubular portion 82B is positioned radially outward of the guided portion 72B, but unlike the first embodiment, it does not function as a guide portion that guides the suction valve 30B. The tubular portion 82B is configured such that an annular space is formed between its inner peripheral surface 82a and the outer peripheral surface 72a of the guided portion 72B. As in the first embodiment, the cover portion 83 is located radially outside the guided portion 72B and covers the valve body portion 71 of the intake valve 30B from the second surface 71b side. The cover portion 83 has an annular facing surface 83a that faces the second surface 71b of the valve body portion 71 with a gap G therebetween.

One end of a guide member 89 is press-fitted into the concave portion 86B formed in the stopper body portion 81 . The guide member 89 is a hollow shaft-shaped member extending in the direction of the axis A from the stopper main body portion 81 toward the valve seat portion 31b side, or a hollow cylindrical member. inserted. An outer peripheral surface 89a of the guide member 89 is configured as a sliding surface that slides on the inner peripheral surface 72b of the guided portion 72B.

In the present embodiment, the intake valve stopper 32B has the function of restricting the movement of the intake valve 30B in the valve opening direction, while the guide member 89 has the function of guiding the movement of the intake valve 30B. In other words, the two-part assembly in which the guide member 89 is attached to the suction valve stopper 32B has both functions of a stopper portion that restricts the movement of the suction valve 30B in the valve opening direction and a guide portion that guides the movement of the suction valve 30B. A valve stop is configured.

A suction valve biasing spring 33 is arranged between the outer peripheral surface 72a of the guided portion 72B and the inner peripheral surface 82a of the tubular portion 82B. One end of the intake valve biasing spring 33 contacts a portion of the second surface 71b of the valve body 71 radially outside the guided portion 72B, and the other end contacts the contact surface 81a of the stopper body 81. It abuts on a portion radially outside of.

The internal space S2 formed by the space surrounded by the inner peripheral surface 72b of the guided portion 72B and the guide member 89 increases and decreases in volume according to the opening/closing operation (movement) of the suction valve 30B. Fuel flows into and out of the internal space S2 via the flow path P by increasing or decreasing the volume of the internal space S2. The flow path P connects the internal space S2 and the space on the secondary side of the intake valve 30B (downstream of the valve seat portion 31b). The flow path P is a space surrounded by the through hole 73 of the guided portion 72B, the chamfered portion 84 of the intake valve stopper 32B, the second surface 71b of the valve body portion 71 of the intake valve 30B, and the cover portion 83 of the intake valve stopper 32B. and a gap G formed between the opposing surface 83a. A gap formed between the inner peripheral surface 72b of the guided portion 72B and the outer peripheral surface 89a of the guide member 89 also functions as part of the flow path P. As shown in FIG.

In the present embodiment, when the intake valve 30B is opened, the tip portion 72c of the guided portion 72 of the intake valve 30B and the stopper body portion 81 of the intake valve stopper 32 are in contact with each other. The main body portion 71 and the cover portion 83 of the intake valve stopper 32B are configured to be out of contact with each other. That is, part of the flow path P is formed between the second surface 71b of the valve body 71 and the facing surface 83a of the cover 83 at any position between the closed state and the open state of the intake valve 30B. A gap G is formed. Therefore, since it is not necessary to process grooves extending in the radial direction for securing the flow path P in the suction valve 30B, the suction valve stopper 32B, and the guide member 89, the processing can be simplified. This enables easy and low-cost manufacturing of parts.

Next, the opening/closing operation of the intake valve mechanism according to the second embodiment of the present invention will be described with reference to FIG.

In the opening operation of the intake valve 30B, the inner peripheral surface 72b of the guided portion 72B slides against the outer peripheral surface 89a of the guide member 89, thereby guiding the movement in the lift direction. The tip portion 72c of the intake valve stopper 32 abuts against the abutment surface 81a of the stopper main body portion 81 of the intake valve stopper 32, thereby restricting movement in the lift direction. Since the guide member 89 functions as a guide portion of the suction valve 30B, eccentricity and inclination of the valve body portion 71 of the suction valve 30B with respect to the valve seat portion 31b are suppressed. Therefore, the occurrence of cavitation erosion due to the eccentricity of the valve body portion 71 can be suppressed, and the unstable valve opening operation due to the inclination of the valve body portion 71 can be suppressed.

Due to the opening operation of the intake valve 30B, the volume of the internal space S2 formed between the guided portion 72 of the intake valve 30B and the guide member 89 is reduced. At this time, the fuel in the internal space S2 flows through the gap formed between the through-hole 73 constituting the flow path P, the inner peripheral surface 72b of the guided portion 72B, and the outer peripheral surface 89a of the guide member 89, and the valve Through a gap G formed between the second surface 71b of the main body portion 71 and the opposing surface 83a of the cover portion 83, the air flows out into the space on the secondary side of the intake valve 30B. As a result, the pressure in the internal space S2 hardly rises, and the responsiveness when the intake valve 30B is opened does not deteriorate.

On the other hand, in the valve closing operation of the intake valve 30B, the inner peripheral surface 72b of the guided portion 72B slides against the outer peripheral surface 89a of the guide member 89, thereby guiding the movement in the direction toward the valve seat portion 31b. Finally, the first surface 71a of the valve body portion 71 is seated on the valve seat portion 31b. Since the guide member 89 functions as a guide portion of the intake valve 30B, eccentricity and inclination of the valve body portion 71 with respect to the valve seat portion 31b are suppressed. Therefore, it is possible to suppress the occurrence of unstable valve closing operation and cavitation erosion due to inclination or eccentricity of the valve body portion 71 with respect to the valve seat portion 31b.

The closing operation of the intake valve 30B increases the volume of the internal space S2. At this time, the fuel in the space on the secondary side of the intake valve 30B flows through the gap G that forms the flow path P, the space surrounded by the chamfered portion 84, the through hole 73, and the inner peripheral surface 72b of the guided portion 72B. and the outer peripheral surface 89a of the guide member 89 into the internal space S2. As a result, the closing operation of the intake valve 30B is performed smoothly.

The intake valve mechanism 300B according to the second embodiment of the present invention described above includes an intake valve 30B (valve element) that can be seated and separated from a valve seat portion 31b (valve seat), and an intake valve 30B ( A valve stopper (between the intake valve stopper 32 and the guide member 89) is located on the opposite side of the valve seat portion 31b (valve seat) with respect to the valve body) and restricts the movement of the intake valve 30B (valve body) in the valve opening direction. assembly). The intake valve 30B (valve element) includes a valve body portion 71 that is seated on a valve seat portion 31b (valve seat), and a suction valve stopper from a position radially inside the valve body portion 71 relative to the valve seat portion 31b (valve seat). and a tubular guided portion 72B extending toward the 32B (valve stopper) side. The valve stopper includes an intake valve stopper 32B (stopper portion) that restricts the movement of the intake valve 30B (valve body) in the valve opening direction by coming into contact with the tip portion 72c of the guided portion 72B, and an intake valve stopper 32B (stopper portion). ) toward the valve seat portion 31b (valve seat), and the movement of the suction valve 30B (valve element) in the contact/separation direction with respect to the valve seat portion 31b (valve seat) by sliding the guided portion 72B. It has a guide member 89 (guide portion) that guides to.

According to this configuration, by sliding the guided portion 72B on the guide member 89 (guide portion) to guide the movement of the suction valve 30B (valve disc), the eccentricity and inclination of the suction valve 30B (valve disc) can be reduced. can be suppressed. Furthermore, since the structure restricts the movement of the suction valve 30B (valve element) in the valve opening direction by the contact between the tip portion 72c of the guided portion 72B and the suction valve stopper 32B (stopper portion), the suction valve 30B (valve element) ) and the suction valve stopper 32B (stopper portion), a flow path P that allows fluid to flow into and out of the internal space S2 of the guided portion 72B is secured without forming radial or axial groove portions. can be done. Therefore, it is possible to facilitate manufacturing of parts while suppressing inclination and eccentricity of the intake valve 30B (valve element) and suppressing a decrease in responsiveness of the intake valve 30B (valve element).

Further, the guide portion according to the present embodiment is a guide member 89 as a shaft-like portion along which the inner peripheral surface 72b of the guided portion 72B slides on the outer peripheral surface 89a. According to this configuration, the guided portion 72 can be supported and guided by the guide member 89 on the inner peripheral side.

Further, in the present embodiment, the guide portion is a guide member 89 (member) that is separate and different from the suction valve stopper 32B (stopper portion), and the valve stopper is the guide member 89 that is attached to the suction valve stopper 32B (stopper portion). It is composed of an assembly in which (a guide portion) is assembled. According to this configuration, it is possible to manufacture the guide member 89 as a guide portion that supports and guides the guided portion 72B on the inner peripheral side by simple processing.

Further, in the present embodiment, a suction valve biasing spring 33 that biases the suction valve 30B (valve element) toward the valve seat portion 31b (valve seat) is positioned radially outward of the guided portion 72B. spring) is placed. According to this configuration, even if the intake valve biasing spring 33 cannot be arranged in the internal space S2 of the guided portion 72B, the intake valve biasing spring 33 can be arranged.

[Other embodiments]
In addition, the present invention is not limited to the above-described embodiments, and includes various modifications. The above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the described configurations. A part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment. Moreover, it is also possible to add, delete, or replace a part of the configuration of each embodiment with another configuration.

For example, in the first and second embodiments described above, the intake valve housings 31 of the intake valve mechanisms 300, 300A, and 300B have valve seat portions 31b and rod guide portions 31c. However, the intake valve housing may have only the valve seat portion 31b, and the rod guide portion may be a component separate from the intake valve housing.

Further, in the above-described embodiment, an example of a configuration in which the intake valve stoppers 32, 32A, and 32B are press-fitted into the intake valve housing 31 is shown. However, this configuration is not a constraint for applying the present invention, and a configuration in which the suction valve stopper is fixed to a member separate from the suction valve housing 31 is also possible.

Further, in the above-described embodiment, an example of the configuration in which the flow path is formed by providing the notch 87 in the outer peripheral portion 83b of the cover portion 83 of the intake valve stoppers 32, 32A, 32B has been shown. However, it is also possible to form a passage by providing a through hole instead of the notch 87 in the cover portion 83 of the intake valve stoppers 32, 32A, 32B.

Moreover, in the above-described embodiment, an example of a configuration in which the through holes 73 are provided in the guided portions 72 and 72B of the intake valves 30 and 30B is shown, but a configuration in which the through holes 73 are not provided is also possible. In this case, the flow path P that communicates the inner space surrounded by the inner peripheral surface 72b of the guided portion and the radially outer (downstream) space of the suction valve is the second surface of the valve body portion 71 of the suction valve. The gap G formed between 71b and the opposing surface 83a of the cover portion 83 of the intake valve stopper 32, 32A, 32B, and the sliding surface (outer peripheral surface 72a or inner peripheral surface 72b) of the guided portion of the intake valve. and the sliding surface (inner peripheral surface 82a) of the cylindrical portion 82 as the guide portion or the sliding surface (outer peripheral surface 89a) of the guide member 89. As shown in FIG. Even in this case, by appropriately setting the size of the gap between the sliding surfaces, it is possible for the fluid to flow in and out of the internal space of the guided portion through the flow path P during the opening and closing operation of the intake valve. .

Further, in the above-described embodiment, an example of a configuration in which the intake valve stoppers 32, 32A, 32B have the cover portion 83 that covers the valve body portion 71 of the intake valves 30, 30B from the second surface 71b side has been shown. However, the intake valve stopper may be configured to have a stopper function at least for the intake valves 30 and 30B, and a configuration without the cover portion 83 is also possible.

Further, in the above-described second embodiment, the valve stopper having both functions of a stopper portion (stopper function) and a guide portion (guide function) for the intake valve 30B is formed by assembling the guide member 89 to the intake valve stopper 32B. An example configured by an assembly of parts is shown. However, the valve stopper having both functions can also be constituted by a single part in which the suction valve stopper 32B and the guide member 89 are integrally formed. In this configuration, the valve stopper is provided with a hollow shaft-like projection extending from the radially inner side of the contact surface 81a of the stopper body portion 81 toward the valve seat portion 31b. Also in this configuration, the parts can be easily manufactured because they can be formed in a substantially axially symmetrical shape.

REFERENCE SIGNS LIST 1 high-pressure fuel supply pump 30, 30B suction valve (valve body) 31b valve seat (valve seat) 32, 32A, 32B suction valve stopper (valve stopper, stopper portion) 33 with suction valve Force spring (biasing spring) 71... Valve main body 71a... First surface 71b... Second surface 72, 72B... Guided part 72a... Outer peripheral surface 72b... Inner peripheral surface 72c... Tip part 73... Through hole 81... Stopper main body (stopper part) 82... Cylindrical part (guide part) 82a... Inner peripheral surface 83... Cover part 83a... Opposite surface 84, 84A... Chamfered part 89... Guide member (guide portion) 89a... Outer peripheral surface 300, 300A, 300B... Suction valve mechanism (valve mechanism) G... Gap

Claims (12)

a valve body that can be seated and separated from the valve seat;
a valve stopper located on the opposite side of the valve seat with respect to the valve body and restricting movement of the valve body in the valve opening direction;
The valve body
a valve body seated on the valve seat;
a cylindrical guided portion extending toward the valve stopper from a position radially inside the valve seat in the valve main body;
The valve stopper is
a stopper portion that restricts the movement of the valve body in the valve opening direction by coming into contact with the tip portion of the guided portion;
and a guide portion that extends from the stopper portion toward the valve seat side and guides the movement of the valve body in a contacting/separating direction with respect to the valve seat by sliding of the guided portion. valve mechanism. The valve mechanism of claim 1, wherein
The valve body portion is a plate-like portion having a first surface seated on the valve seat and a second surface located on the opposite side of the first surface,
the valve stopper has a facing surface located radially outside the guided portion and facing the second surface;
A valve mechanism, wherein a gap is formed between the second surface and the opposing surface in a state where the tip of the guided portion is in contact with the stopper portion. The valve mechanism of claim 1, wherein
The valve stopper has an annular cover portion positioned radially outward of the guided portion and covering the valve body portion with a gap therebetween. The valve mechanism of claim 1, wherein
The guided portion has a through hole penetrating in a radial direction,
The through hole is open at a position where at least a part thereof does not overlap with the guide portion when the tip portion of the guided portion is in contact with the stopper portion. A valve mechanism according to claim 4, wherein
The valve stopper is a single component in which the stopper portion and the guide portion are integrally formed,
The guide portion is configured as a cylindrical portion extending from the outer edge portion of the stopper portion toward the valve seat side, and the outer peripheral surface of the guided portion slides against the inner peripheral surface thereof,
The guide portion has a chamfered portion at its opening edge,
At least a part of the through-hole opens into a space surrounded by the chamfered portion in a state where the tip portion of the guided portion is in contact with the stopper portion. A valve mechanism according to claim 5, wherein
The chamfered portion is an R-chamfered valve mechanism. A valve mechanism according to claim 5, wherein
The chamfered portion is a C-chamfered valve mechanism. The valve mechanism of claim 1, wherein
The guide portion is configured as a cylindrical portion in which the outer peripheral surface of the guided portion slides on the inner peripheral surface thereof,
A valve mechanism, wherein a biasing spring that biases the valve body toward the valve seat is arranged in an internal space surrounded by the inner peripheral surface of the guided portion. The valve mechanism of claim 1, wherein
The guide portion is a shaft-shaped portion along which the inner peripheral surface of the guided portion slides on the outer peripheral surface thereof. A valve mechanism according to claim 9, wherein
The guide portion is a different member separate from the stopper portion,
The valve mechanism, wherein the valve stopper is configured by an assembly in which the guide portion is attached to the stopper portion. A valve mechanism according to claim 9, wherein
A valve mechanism, wherein a biasing spring that biases the valve body toward the valve seat is arranged at a radially outer position of the guided portion. A high-pressure fuel supply pump comprising the valve mechanism according to claim 1.

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