JP6663971B2 - High pressure fuel supply pump with electromagnetically driven suction valve - Google Patents

Description

  The present invention relates to a high-pressure fuel supply pump provided with an electromagnetically driven suction valve, and more particularly to a so-called outward-opening type valve in which the electromagnetically driven suction valve is provided with a valve on the side of the valve seat on the pressurizing chamber side. .

  Conventionally, a high-pressure fuel supply pump of this type has a valve formed of a cylindrical member as described in, for example, JP-A-2009-203987 and JP-A-2006-291838. A valve stopper is provided between the pressure chamber and the valve, the valve stopper being provided between the valve and the valve, and the valve is closed between the valve stopper and the valve. A spring that biases the spring. And in the case of such a configuration, it is formed between the valve and the stopper. The space in which the spring is placed becomes an enclosed space that is sealed off from the surrounding fluid, and thus affects the responsiveness of the valve. For this reason, there has been provided a communication passage that communicates the sealed space with the surrounding fluid passage.

JP 2009-203987 A JP 2006-291838 A

  However, in a suction valve of a high-pressure pump, a fuel having a very fast flow rate flows around a very light valve in the opposite direction between the time of suction and the time of spill. For this reason, the valve of the intake valve moves not only in the front-back direction but also in the left-right or circumferential direction in the fuel flow. Under such circumstances, when the fuel pressure around the valve is introduced into the enclosed space, the fuel pressure around the valve was conventionally introduced from the lateral direction of the valve across the spring to the enclosed space. Unreliable and unstable operations were repeated, resulting in a drastic change in the fuel discharge flow rate. As a result, when the pressure change of the common rail when the conventional pump was used was measured, the pressure fluctuation was large as shown in FIG. 7A, which had a bad influence on the fuel injection of the injector.

  SUMMARY OF THE INVENTION An object of the present invention is to stabilize the operation of a valve and, as a result, stabilize an unintended discharge flow fluctuation of fuel, thereby reducing the fluctuation of the common rail pressure.

In order to achieve the above object, the present invention provides a suction valve which is urged in a valve opening direction by a plunger rod, a valve stopper which contacts the suction valve in a stroked state to a fully open position, and is formed on the valve stopper, A guide portion for guiding an axial stroke of the suction valve; and a guide portion disposed on an inner peripheral side of a guided surface of the suction valve guided by the guide portion, and urges the suction valve in a valve closing direction. And a communication path formed by the valve stopper and the suction valve in a state where the suction valve is stroked to the fully open position, and communicating with a space in which the spring is disposed and the pressurizing chamber. is, in the radially outer side of the spring central axis of the spring as a reference, is arranged to the suction valve is adjacent said inlet valve comprises a bottom portion for supporting one end of said spring, said from the bottom A cylindrical portion extending toward the lubrication stopper side, wherein the outer peripheral surface of the cylindrical portion is formed with the guided surface guided by the guide portion formed on the inner peripheral surface of the valve stopper, and the cylindrical portion the inner peripheral surface of the regulating surface for regulating the radial movement of the spring facing said spring and directly Ru is formed.

  Preferably, the central axis of the pressure equalizing hole is provided so as not to cross the spring inside the spring.

  Preferably, the pressure equalizing hole is a straight through hole along the center axis of the spring.

  Preferably, the valve stopper has a valve guide, and the pressure equalizing hole passes through the valve guide.

  Preferably, the pressure equalizing hole opens into the spring storage chamber beyond the valve seat position.

  Preferably the pressure equalizing hole is located on the central axis of the valve.

  Preferably, the pressure equalizing hole is located on the center line axis of the fuel introduction hole.

  Preferably, the pressure equalizing hole is located on the center line axis of the plunger rod.

  ADVANTAGE OF THE INVENTION According to this invention comprised as mentioned above, since the pressure of a pressurization chamber can be introduce | transduced inside a spring without crossing a spring, the unstable behavior of a spring and a valve by introduction pressure can be eliminated, and a valve closes. In this case, the force applied to the valve is stabilized, so that the valve closing timing can be stabilized. As a result, an unintended change in the ejection amount is less likely to occur.

1 is an overall longitudinal sectional view of a high-pressure fuel supply pump including an electromagnetically driven suction valve according to a first embodiment of the present invention. FIG. 1 is a system configuration diagram illustrating an example of a fuel supply system using a high-pressure fuel supply pump according to the present invention. 1 is an enlarged sectional view of an electromagnetically driven suction valve according to a first embodiment of the present invention, showing a state when the valve is opened (during fuel intake and spill). FIG. 4A is a view on arrow P in FIG. 3A showing a relationship between a stopper and a valve of the electromagnetically driven suction valve according to the first embodiment of the present invention. FIG. 3A is a view of the valve of the electromagnetically driven suction valve according to the first embodiment of the present invention, as viewed in the direction indicated by the arrow P in FIG. FIG. 3 is an enlarged cross-sectional view of the electromagnetically driven suction valve according to the first embodiment of the present invention, illustrating a state when fuel is discharged (when the valve is closed). 1 is an enlarged sectional view of an electromagnetically driven suction valve according to a first embodiment of the present invention, showing a state when the valve is opened (during fuel intake and spill). FIG. 5 is a sectional view showing an electromagnetically driven suction valve according to a second embodiment of the present invention. FIG. 5A is a view of a valve stopper of an electromagnetically driven suction valve according to a second embodiment of the present invention, as viewed from an arrow P in FIG. FIG. 7 is a sectional view showing an electromagnetically driven suction valve according to a third embodiment of the present invention. FIG. 7A is a view of a valve stopper of an electromagnetically driven suction valve according to a third embodiment of the present invention, as viewed from an arrow P in FIG. 4 is a graph showing pressure fluctuation of a conventional common rail. 4 is a graph showing pressure fluctuation of a common rail when the high-pressure fuel supply pump according to the present invention is used.

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

[First Embodiment]
First Embodiment A high-pressure fuel supply pump according to a first embodiment of the present invention will be described with reference to FIGS. In FIG. 1, reference numerals cannot be given to details, and reference numerals in the description which do not have the reference numerals in FIG. 1 are described in enlarged views described later.

  The pump housing 1 is provided with a concave portion 12A that forms a bottomed cylindrical space whose one end is open, and the cylinder 20 is inserted into the concave portion 12A from the open end side. The outer periphery of the cylinder 20 and the pump housing 1 are sealed by a pressure contact portion 20A. Also, since the piston plunger 2 is in sliding contact with the cylinder 20, the space between the inner peripheral surface of the cylinder 20 and the outer peripheral surface of the piston plunger 2 is sealed with fuel that enters between the sliding surfaces. As a result, a pressurizing chamber 12 is defined between the tip of the piston plunger 2, the inner wall surface of the recess 12 </ b> A, and the outer peripheral surface of the cylinder 20.

  A cylindrical hole 200 </ b> H is formed from the peripheral wall of the pump housing 1 toward the pressurizing chamber 12, and the cylindrical hole 200 </ b> H has the suction valve portion INV and the electromagnetic drive mechanism portion EMD of the electromagnetically driven suction valve mechanism 200. Has been inserted. By joining the joint surface 200R between the outer peripheral surface of the electromagnetically driven suction valve mechanism 200 and the cylindrical hole 200H with the gasket 300, the inside of the pump housing 1 is sealed from the atmosphere. The cylindrical hole 200H sealed by the attachment of the electromagnetically driven suction valve mechanism 200 functions as the low-pressure fuel chamber 10a.

  At a position facing the cylindrical hole 200H with the pressure chamber 12 interposed therebetween, a cylindrical hole 60H is provided from the peripheral wall of the pump housing 1 toward the pressure chamber 12. The discharge valve unit 60 is mounted in the cylindrical hole 60H. The discharge valve unit 60 has a valve seat 61 formed at the tip and a valve seat member 61B having a through hole 11A serving as a discharge passage at the center. A valve holder 62 surrounding the periphery of the valve seat 61 is fixed to the outer periphery of the valve seat member 61B. In the valve holder 62, a valve 63 and a spring 64 for urging the valve 63 in a direction of pressing the valve 63 against the valve seat 61 are provided. A discharge joint 11 fixed to the pump housing 1 with a screw is provided at an opening of the cylindrical hole 60H on the side opposite to the pressurizing chamber.

  The electromagnetically driven suction valve mechanism 200 includes a plunger rod 201 that is electromagnetically driven. A valve 203 is provided at the tip of the plunger rod 201, and faces a valve seat 214S formed in a valve housing 214 provided at an end of the electromagnetically driven suction valve mechanism 200.

  A plunger rod biasing spring 202 is provided at the other end of the plunger rod 201, and the valve 203 biases the plunger rod in a direction away from the valve seat 214S. A valve stopper S0 is fixed to the inner periphery of the distal end of the valve housing 214. The valve 203 is held reciprocally between the valve seat 214S and the valve stopper S0. A valve biasing spring S4 is disposed between the valve 203 and the valve stopper S0, and the valve 203 is biased by the valve biasing spring S4 in a direction away from the valve stopper S0.

  The valve 203 and the tip of the plunger rod 201 are urged by respective springs in directions opposite to each other. However, since the plunger rod urging spring 202 is constituted by a stronger spring, the plunger rod 201 is urged by the valve. The valve 203 is pushed in a direction away from the valve seat 214S (rightward in the drawing) against the force of the spring S4, and as a result, the valve 203 is pressed against the valve stopper S0.

  Therefore, when the electromagnetically driven suction valve mechanism 200 is turned off (when the electromagnetic coil 204 is not energized), the plunger rod 201 opens the valve 203 via the plunger rod 201 by the plunger rod urging spring 202. It is biased in the direction of the valve. Therefore, when the electromagnetically driven suction valve mechanism 200 is turned off, the plunger rod 201 and the valve 203 are maintained at the valve open positions as shown in FIGS. 1, 2 and 3A (the detailed configuration will be described later).

  As shown in FIG. 2, the fuel is guided from a fuel tank 50 by a low-pressure pump 51 to a suction joint 10 as a fuel inlet of the pump housing 1.

  A plurality of injectors 54 and pressure sensors 56 are mounted on the common rail 53. The injectors 54 are mounted according to the number of cylinders of the engine, and inject high-pressure fuel sent to the common rail 53 to each cylinder in response to a signal from an engine control unit (ECU) 600. Further, a relief valve mechanism (not shown) built in the pump housing 1 opens when the pressure in the common rail 53 exceeds a predetermined value, and returns the excess high-pressure fuel to the upstream side of the discharge valve 60.

  A lifter 3 provided at a lower end of the piston plunger 2 is pressed against a cam 7 by a spring 4. The piston plunger 2 is slidably held by a cylinder 20, and reciprocates by a cam 7 rotated by an engine camshaft or the like to change the volume in the pressurizing chamber 12. The outer periphery of the lower end of the cylinder 20 is held by a cylinder holder 21, and the cylinder holder 21 is fixed to the pump housing 1 to be pressed against the pump housing 1 by a metal seal portion 20 </ b> A.

  The cylinder holder 21 is provided with a plunger seal 5 for sealing the outer periphery of the small diameter portion 2A formed on the lower end side of the piston plunger 2. The assembly of the cylinder 20 and the piston plunger 2 is inserted into the pressurizing chamber, and the external thread 21A formed on the outer circumference of the cylinder holder 21 is formed on the inner circumference of the open end of the recess 12A of the pump housing 1 and the female thread 1A formed on the inner circumference. Screwed in. When the cylinder holder 21 pushes the cylinder 20 toward the pressure chamber while the step 21D of the cylinder holder 21 is locked to the peripheral edge of the cylinder 20 opposite the pressure chamber side, the sealing step 20A of the cylinder 20 is moved. It is pressed against the pump housing 1 to form a seal by metal contact.

  The O-ring 21B seals between the inner peripheral surface of the mounting hole EH formed in the engine block ENB and the outer peripheral surface of the cylinder holder 21. The O-ring 21C seals a gap between the inner peripheral surface of the recess 12A of the pump housing 1 on the side opposite to the pressurizing chamber and the outer peripheral surface of the cylinder holder 21 at a position on the side opposite to the pressurizing chamber of the screw portion 21A (1A).

  The pump is screwed to the engine block at a flange (details are omitted) of the pump housing 1 and is thereby fixed to the engine block.

  A damper chamber 10b is formed in the middle of the passage from the suction joint 10 to the low-pressure fuel chamber 10a. In this damper chamber 10b, a double metal diaphragm type damper 80 is housed while being sandwiched between the damper holder 30 and the damper cover 40. I have. The double metal diaphragm damper 80 has a pair of upper and lower metal diaphragms 80A and 80B butted against each other, and the outer periphery thereof is welded over the entire periphery to seal the inside.

  An inert gas such as argon is sealed in the hollow portion formed by the double metal diaphragms 80A and 80B, and the hollow portion changes its volume in response to an external pressure change. To play.

  Specifically, a step is formed on the inner periphery of the damper cover 40, and an annular groove is provided in the step. The outer peripheral weld of the double metal diaphragm type damper 80 fits completely into this groove, and the peripheral wall is removed from the peripheral wall. Arranged so that an external force is not transmitted and the inner surface of the one-side surface of the double metal diaphragm type damper 80 (the surface on the side where the suction joint 10 of the damper cover is provided) is welded to the inner peripheral portion of the outer peripheral welded portion. I do. The damper holder 30 is a cup-shaped member without a bottom (a member having a hole at the center and having a curved surface with a cross section bent inward around the hole). The outer periphery is press-fitted into the inner peripheral surface of the damper cover 40. The end surface of the bent portion is in contact with the annular surface inside the welded portion on the outer periphery of the double metal diaphragm type damper 80 over the entire circumference. In a state where the flange portion of the double metal diaphragm type damper 80 is sandwiched between the contact portion and the step described above, the double metal diaphragm type damper 80 is assembled together with the damper holder 30 and the damper cover 40 into one set. It is formed as a body (unit). Thus, the damper chamber 10b is formed by screwing the pump housing 1 and the damper cover 40 together. In this embodiment, the suction joint 10 is formed integrally with the damper cover 40 perpendicularly to the center of the upper surface of the damper cover 40. For this reason, even if the threaded portion formed on the outer periphery of the damper cover 40 is screwed into the threaded portion formed on the inner wall of the pump housing 1, the posture of the suction joint 10 becomes the same at any position in the rotation direction. Since the screwing position is not limited, the assemblability of the damper cover 40 is improved.

  A fuel passage 80U between the diaphragm 80A on one side of the double metal diaphragm damper 80 and the damper cover 40 is provided via a groove passage 80C provided on the inner peripheral wall of the damper cover 40 as a damper chamber 10b (two sheets). (A fuel passage facing a diaphragm 80B on one side of the metallic diaphragm damper 80). The damper chamber 10b communicates with the low-pressure fuel chamber 10a in which the electromagnetically driven suction valve 20 is located by a communication hole 10c formed in the pump housing 1 constituting the bottom wall of the damper chamber 10b. Thus, the fuel sent from the feed pump 50 flows from the suction joint 10 into the damper chamber 10b of the pump, and acts on both the diaphragms 80A, 80B of the double metal diaphragm damper 80, passes through the communication hole 10c, and passes through the low pressure fuel chamber 10a. Flows to

  The connecting portion between the small diameter portion 2A of the piston plunger 2 and the large diameter portion 2B that slides on the cylinder 21 is connected by a conical surface 2K. A fuel sub-chamber 250 is formed around the conical surface between the plunger seal 5 and the lower end surface of the cylinder 21. The fuel sub-chamber 250 captures fuel leaking from the sliding surface between the cylinder 20 and the piston plunger 2. One end of the annular passage 21G defined between the inner peripheral surface of the pump housing 1, the outer peripheral surface of the cylinder 21, and the upper end surface of the cylinder holder 21 is formed by a vertical passage 250B formed through the pump housing 1 at one end thereof. And is connected to the fuel sub-chamber 250 via a fuel passage 250A formed in the cylinder holder 21. Thus, the damper chamber 10A and the fuel sub-chamber 250 are communicated by the vertical passage 250B, the annular passage 21G, and the fuel passage 250A.

  When the piston plunger 2 moves up and down (reciprocates), the tapered surface 2K reciprocates in the fuel sub-chamber, so that the volume of the fuel sub-chamber 250 changes. When the volume of the fuel sub-chamber 250 increases, fuel flows from the damper chamber 10b into the fuel sub-chamber 250 via the vertical passage 250B, the annular passage 21G, and the fuel passage 250A. When the volume of the fuel sub-chamber 250 decreases, fuel flows from the fuel sub-chamber 250 to the damper chamber 10b via the vertical passage 250B, the annular passage 21G, and the fuel passage 250A. When the piston plunger 2 rises from the bottom dead center while the valve 203 is maintained at the open position (the coil 204 is not energized), the fuel sucked into the pressurized chamber is supplied from the suction valve 203 that is being opened to the low-pressure fuel. It overflows (spills) into the chamber 10a and flows into the damper chamber 10b through the communication hole 10c. Thus, in the damper chamber 10b, the fuel from the suction joint 10, the fuel from the fuel sub-chamber 250, the overflow fuel from the pressurizing chamber 12, and the fuel from the relief valve (not shown) are combined. . As a result, the fuel pulsations of the respective fuels merge in the damper chamber 10b and are absorbed by the two-piece metal diaphragm damper 80.

  In FIG. 2, a portion surrounded by a broken line indicates a pump main body portion in FIG. The electromagnetically driven suction valve 200 includes a yoke 205 that also serves as the body of the electromagnetically driven mechanism EMD on the inner peripheral side of the coil 204 formed in an annular shape. In the yoke 205, a fixed core 206 and an anchor 207 are housed in an inner peripheral portion with a plunger rod urging spring 202 interposed therebetween.

  As shown in detail in FIG. 3A, in this embodiment, the yoke 205 is divided into a side yoke 205A and an upper yoke 205B and joined by press fitting. The fixed core 206 is divided into an outer core 206A and an inner core 206B, and is joined by press fitting. The anchor 207 is fixed to the end of the plunger rod 201 on the side opposite to the valve by welding, and faces the inner core 206B via the magnetic gap GP. The coil 204 is housed in a yoke 205, and the two are fixed by screwing a screw provided on the outer periphery of the open end of the side yoke 205 </ b> A to the screw 1SR of the pump housing 1. By this fixing operation, the open end of the side yoke 205A pushes the flange portion 206F formed on the outer periphery of the outer core 206A toward the pump housing, and the outer periphery of the open-side end cylindrical portion 206G of the outer core 206A is connected to the pump housing. 1 is inserted into the inner peripheral surface of the guide hole 1GH. Further, an annular enlarged portion 206GS formed as a stepped portion on the outer periphery of the open end cylindrical portion 206G of the outer core 206A is pressed against the annular surface portion 1GS formed around the opening side of the guide hole 1GH of the pump housing 1. I do. At this time, the seal ring 206SR disposed between the annular surface portion 1GS formed around the opening side of the guide hole 1GH of the pump housing 1 and the flange portion 206F formed on the outer periphery of the outer core 206A is compressed. Thereby, the space on the low pressure side including the space on the inner peripheral portion of the fixed core 206 and the low pressure fuel chamber 10a is sealed from the atmosphere.

  A closed magnetic circuit CMP crossing the magnetic gap GP is formed around the coil 204 by the side yoke 205A and the upper yoke 205B, the outer core 206A and the inner core 206B, and the anchor 207. A portion of the outer core 206A facing the magnetic gap GP is formed to have a small thickness (a groove is formed when viewed from the outer periphery), and this groove portion is a magnetic aperture 206S (magnetic resistance) of the closed magnetic circuit CMP. Having the function of). Thereby, the magnetic flux leaking through the outer core 206A can be reduced, and as a result, the magnetic flux passing through the magnetic gap GP can be increased.

  As shown in FIGS. 3 (A) to 3 (C), 4 (A) and 4 (B), a valve is provided on the inner peripheral portion of the cylindrical portion 206G formed at the open end of the outer core 206A. A bearing 214B formed at one end of the housing 214 is fixed by press-fitting, and the plunger rod 201 extends through the bearing 214B to the low-pressure fuel chamber 10a in the valve housing 214. On the other hand, the left end of the valve 203 housed in the center hole 214C (functioning as a fuel introduction hole) formed on the other end side of the valve housing 214 has an end face on the pressurizing chamber 12 side of the valve housing 214. It extends from the position of the formed valve seat 214S to the low-pressure fuel chamber 10a through the center hole 214C. As a result, the tip of the plunger rod 201 faces the flat portion 203F of the valve 203 in the low-pressure fuel chamber 10a.

  A through hole 201H is formed at the center of the plunger rod 201. One end of the through hole 201H communicates with a storage space of the plunger rod biasing spring 202 formed between the inner core 206B and the anchor 207. The other end of the through hole 201H is connected to the low pressure chamber 10a inside the valve housing. When the electromagnetic drive device EMD is energized and the electromagnetic valve mechanism 200 anchor 207 is attracted to the inner core 206B of the fixed core 206 and the valve 203 is pressed against the valve seat 214S and is in a closed state, the tip of the plunger rod 201 is closed. 203 is separated from the flat portion 203F. At this time, the low-pressure fuel chamber 10a communicates with the storage space of the plunger rod biasing spring 202 through the through-hole 201, and as a result, the fuel in the storage space of the plunger rod biasing spring 202 is discharged to the low-pressure fuel chamber through the through-hole 201. You. Thereby, the movement of the anchor 207 and the plunger rod 201 becomes smooth. Further, even if the tip of the plunger rod 201 is made flat, the sticking phenomenon between the tip of the plunger rod 201 and the flat portion 203F of the valve 203 can be eliminated, and the power supplied to the coil 204 of the electromagnetic drive device EMD can be reduced. Further, by making the plunger rod 201 hollow, the weight of the plunger rod 201 is reduced, and the driving power can be reduced.

  The valve stopper S0 press-fits the inner peripheral surface of the cylindrical portion S1 (shown in FIG. 3A) at the end of the valve 203 into the outer periphery of the outer peripheral surface 214D of the valve housing 214 at the pressurizing chamber side. 214. Further, the outer peripheral surface of the cylindrical portion S1 (shown in FIG. 3A) of the valve stopper S0 is press-fitted to the inner periphery of the guide hole 1GH (diameter D4) of the pump housing 1. A valve 203 is mounted between the distal end of the plunger rod 201 and the valve stopper S0 so as to be able to reciprocate with a valve urging spring S4 interposed therebetween. The valve 203 includes an annular surface portion 203R whose one surface faces the pressurizing chamber side end surface (valve seat 214S) of the valve housing 214, and whose other surface faces the valve stopper S0. At the center of the annular surface portion 203R, there is a bottomed tubular portion extending to the tip of the plunger rod 201, and the bottomed tubular portion is composed of a cylindrical portion 203H and a flat portion 203F provided at the bottom. . The cylindrical portion 203H is housed in the center hole 214C of the valve housing 214, and protrudes into the low-pressure fuel chamber 10a. A cylindrical fuel introduction passage 10P is formed between the outer periphery of the cylindrical portion 203H and the inner periphery of the center hole 214C of the valve housing 214. In FIG. 3 (B), a part of the pump housing 1 is indicated by a ring for convenience in the hatched portion on the outer periphery. The cylindrical portion S1 of the valve housing 214 and the valve stopper S0 can be seen in the cutouts Sn1 to Sn3.

  The tip of the plunger rod 201 is dimensioned so that it can contact the surface of the flat portion 203F of the plunger rod side end of the valve 203 in the low-pressure fuel chamber 10a, but when the valve 203 is closed (FIG. In the state ()), the dimension is defined so that the valve 203 can be temporarily separated from the valve 203 (one time during energization of the electromagnetic coil) by ΔS. Four fuel through holes 214 </ b> Q are provided at equal intervals in a circumferential direction in a cylindrical portion between a bearing 214 </ b> B of the valve housing 214 and a center hole 214 </ b> C of the valve housing 214. These four fuel holes 214Q communicate the inside and outside of the low pressure fuel chamber 10a of the valve housing 214. One end of a cylindrical fuel introduction passage 10P formed between the outer peripheral surface of the cylindrical portion 203H of the valve 203 and the inner peripheral surface of the central hole 214C of the valve housing 214 is connected to the low-pressure fuel chamber 10a, and the other end. Are connected to an annular (disk-shaped) fuel passage 10S formed between the valve seat 214S and the annular surface portion 203R of the valve 203.

  The valve stopper S0 has a projection ST having a cylindrical surface portion SG projecting toward the bottomed cylindrical portion of the valve 203 at the center, and the cylindrical surface portion SG guides a stroke of the valve 203 in the axial direction. Function as The valve urging spring S4 is held between the valve-side end surface SH of the protruding portion ST of the valve stopper S0 and the bottom surface of the bottomed cylindrical portion of the valve 203. When the valve 203 is guided by the cylindrical surface portion SG of the valve stopper S0 and strokes to the fully open position, the annular projection 203S formed at the center of the annular surface portion 203R of the valve 203 is moved to the bottom surface receiving surface S2 (width HS2) of the valve stopper S0. ). At this time, an annular gap SGP is formed around the annular protrusion 203S. The annular space SGP has a function of quickly releasing the valve 203 by causing the pressure P4 of the fuel in the pressurizing chamber to act on the valve 203 when the valve 203 starts to move in the valve closing direction, so that the valve 203 is quickly separated from the valve stopper S0. Play.

  As shown in FIG. 3 (B), the valve stopper S0 has cutouts Sn1 to Sn3 formed at three locations at specific intervals. The notches Sn1-Sn3 are configured to have a larger total passage cross-sectional area than the annular fuel passage 10S formed between the valve seat 214S and the annular surface portion 203R of the valve 203. As a result, there is no passage resistance to the inflow of fuel into the pressurizing chamber or the spill of fuel from the pressurizing chamber, so that the flow of fuel is smooth.

  3C, the diameter D1 of the outer peripheral surface of the valve 203 is configured to be slightly smaller than the diameter D3 of the cutout portion of the valve stopper S0 (see FIG. 3B). As a result, in FIG. 3 (A) and FIG. 4 (B), when the fuel is in the spill state flowing from the pressurizing chamber 12 through the low-pressure fuel chamber 10 to the damper chamber 10b along the fuel flow R5 (FF), The static and dynamic fluid forces of the fuel on the pressurizing chamber 12 side indicated by the arrow P4 hardly act on the annular surface portion 203R.

  The projecting portion ST of the valve stopper S0 disposed inside the valve annular projecting portion 203S communicates the pressurizing chamber with the valve urging spring S4 storage space SP provided between the valve 203 and the valve stopper S0. An equalizing hole S5 and a larger diameter hole S6 than the equalizing hole S5 were provided.

  Accordingly, when the valve 203 is closed, fuel is supplied to the spring storage space SP that stores the valve urging spring S4 through the pressure equalizing hole S5, so that the pressure in the spring storage space SP becomes constant, and the valve 203 closes. , The valve closing timing of the valve 203 can be stabilized.

  Further, the pressure equalizing hole S5 is provided with the valve stopper S0, the protrusion ST, the valve 203, the annular protrusion 203S, the spring storage space SP, the valve biasing spring S4, the valve seat center hole 214C, the plunger 201, and the cylindrical fuel introduction. The passages 10P are arranged on all the central axes.

  Thereby, when fuel is supplied to the spring storage space SP through the pressure equalizing hole S5 when the valve 203 is closed, the fuel pressure does not act on the spring, so that the spring vibrates or the spring storage space SP The spring does not partially deform due to the action of the incoming fuel. Since the force of the spring is only about 300 grams, if the fuel directly hits the spring when it enters from the pressure equalizing hole S5, the spring is easily displaced by the fluid force and pressure of the fuel, and in extreme cases, the spring vibrates. The valve 203 may be tilted or may not move. In this embodiment, since the fuel pressure is uniformly introduced into the spring accommodating space SP from the pressurizing chamber 12 side in the inner circumferential direction of the valve 203 without contacting the spring, the valve closing timing of the valve 203 is stabilized. be able to. Further, since the equalizing hole S5 is provided at the center of the valve stopper S0, it is not necessary to assemble the valve stopper S0 while aligning the position of the equalizing hole S5 for each product, so that the assembly may be complicated. Absent.

  It is desirable that the pressure equalizing hole S5 has a smaller hole diameter. This is because the static or dynamic fluid force of the fuel on the side of the pressurizing chamber 12 indicated by the arrow P4 hardly acts, and the suction valve (valve 203) closes at an unexpected timing due to the fluid force generated by the spilling fuel. This is to prevent that. It is preferred that no dynamic components enter the spring storage space SP and only the required static pressure is introduced, but this does not deny that fuel flows into the spring storage space SP. It is acceptable if the amount of fuel in the spring housing space SP can be smoothly introduced and discharged by opening and closing the valve 203.

  A plurality of equalizing holes S5 may be formed at equal intervals around the center axis of the spring, instead of one. At this time, the pressure acting axis of the fuel introduced from each pressure equalizing hole S5 (the central axis of each pressure equalizing hole S5) is parallel to the central axis of the spring or toward the central axis of the valve urging spring S4 so as not to hit the spring directly. In this case, it is preferable to introduce the gas toward the rear surface of the flat portion 203F of the bulb 203. Care should be taken that the action of the pressure of the fuel introduced from each pressure equalizing hole S5 when viewed from the valve 203 is uniform in the circumferential direction. In the most preferred embodiment, the central axis of the valve 203 overlaps with the central axis of the valve urging spring S4, and the valve 203 is guided so that the projection received by the valve stopper S0 overlaps the center of the valve guide SG. It is preferable that the central axis of the pressure equalizing hole S5 be overlapped with the axis. Further, at this time, if the leading end of the pressure equalizing hole S5 is opened beyond the position of the valve seat 214S to a position on the flat portion 203F side of the valve 203, the pressure line of the pressure fluid of the fuel introduced from the pressure equalizing hole S5 is increased. In a state where the valve 203 is supported at the same time, an automatic centering action like a so-called yajirobe can be expected.

  In the embodiment, the weight of the bulb 203 is several milligrams, the diameter is 10.8 (mm) in the annular surface portion 203R (D1 in FIG. 3C), and the outer periphery of the cylindrical portion 203H is 6.1 (mm) in the axial direction. The length from the stopper-side end surface of the annular projection 203S of the valve 203 to the plunger rod 201-side end surface of the flat portion 203F of the valve 203 is 7.4 (mm). Then, when the passage cross-sectional area of the introduction passage 10P is obtained, the inner diameter of the guide hole 1GH is 8.0 (mm) and the outer diameter of the cylindrical portion of the valve is 6.1 mm, so that 2.1 × 10 5 (square meter) is obtained. Become. Assuming that the rotation of the engine is 6000 rpm, the rotation cycle of the cam is 50 (Hz) and the rotation speed is 314.2 (rad / sec). From this, if the cam is a 4-leaf cam, the maximum speed of the plunger 2 during spill and inhalation is about 7.6 (rad / mm), that is, 2383 (mm / sec), and the maximum flow velocity is about 8.9 (rad / mm). m / sec), and the flow rate at that time is 1.9 × 10 to the fourth power (cubic meter). In the case of a three-leaf cam, the maximum speed of the piston plunger 2 during spill and inhalation is about 8.1 (rad / mm), that is, 2,553 m (m / sec), and the maximum flow rate is about 9.5 (m / sec). The flow rate at that time is 1.9 × 10 4 (cubic meter). The force of the valve urging spring S4 is about 3 (Nm).

  As described above, the fuel having a very high flow velocity flows around the very light valve 203 in the opposite direction between the time of intake and the time of spill. For this reason, the valve 203 is moving not only in the front-back direction but also in the left-right circumferential direction in the fluid. As a result, the change in the fuel discharge flow rate was severe. When the pressure change of the common rail when the conventional pump was used was measured, the pressure fluctuation was large as shown in FIG. Specifically, when controlling to 20 Mpa, a large pressure fluctuation occurred between a maximum of 23 Mpa and a minimum of 18 Mpa. On the other hand, when the pressure change of the common rail when the high-pressure fuel supply pump adopting the present invention was used was measured, as shown in FIG. 7B, the pressure fluctuation when trying to control to 20 Mpa could be suppressed to a minute fluctuation. .

  The operation of the first embodiment will be described with reference to FIGS. 1, 2, 3A, 3B, 4A, and 4B.

≪Fuel intake state≫
First, the fuel suction state will be described with reference to FIGS. 1, 2, 3A, and 4B. In the suction step in which the piston plunger 2 descends from the top dead center position indicated by the broken line in FIG. 2 in the direction indicated by the arrow Q2, the coil 204 is in a non-energized state. The urging force SP1 of the plunger rod urging spring 202 urges the plunger rod 201 toward the valve 203 as shown by an arrow. On the other hand, the urging force SP2 of the valve urging spring S4 urges the valve 203 in the direction shown by the arrow. Since the urging force SP1 of the plunger rod urging spring 202 is set to be larger than the urging force SP2 of the valve urging spring S4, the urging forces of both springs urge the valve 203 in the valve opening direction. The valve 203 is opened by the pressure difference between the static pressure P1 of the fuel acting on the outer surface of the valve 203 typified by the flat portion 203F of the valve 203 located in the low-pressure fuel chamber 10a and the pressure P12 of the fuel in the pressurizing chamber. Subject to valve direction force. Further, the fluid frictional force P2 generated between the fuel flow flowing into the pressurizing chamber 12 along the arrow R4 through the fuel introduction passage 10P and the peripheral surface of the cylindrical portion 203H of the valve 203 causes the valve 203 to move in the valve opening direction. Energize. Further, the dynamic pressure P3 of the fuel flow passing through the annular fuel passage 10S formed between the valve seat 214 and the annular surface portion 203R of the valve 203 acts on the annular surface portion 203R of the valve 203 to move the valve 203 in the valve opening direction. Energize. Due to these urging forces, the valve 203 weighing several milligrams opens quickly when the piston plunger 2 starts to descend, and strokes until it collides with the stopper S0.

  The valve seat 214 is formed outside the cylindrical portion 203H of the valve 203 and the fuel introduction passage 10P in the diameter direction. As a result, the area where P1, P2, and P3 act can be increased, and the valve opening speed of the valve 203 can be increased. At this time, the plunger rod 201 and the anchor 207 are filled with the stagnant fuel and the frictional force with the bearing 214B acts, so that the plunger rod 201 and the anchor 207 are slightly lower than the valve opening speed of the valve 203. The stroke to the right of the drawing is delayed. As a result, a slight gap is formed between the distal end surface of the plunger rod 201 and the flat portion 203F of the valve 203. For this reason, the valve opening force applied from the plunger rod 201 decreases momentarily. However, since the pressure P1 of the fuel in the low-pressure fuel chamber 10a acts on this gap without delay, the valve 203 is opened by reducing the valve-opening force applied from the plunger rod 201 (plunger rod biasing spring 202). The fluid force in the direction to make up. Thus, when the valve 203 is opened, the static pressure and the dynamic pressure of the fluid act on the entire surface of the valve 203 on the low-pressure fuel chamber 10a side, so that the valve opening speed is increased.

  When the valve 203 is opened, the inner peripheral surface of the cylindrical portion 203H of the valve 203 is guided by a valve guide formed by the cylindrical surface SG of the projecting portion ST of the valve stopper S0, and the valve 203 is not displaced in the radial direction. Stroke smoothly. The cylindrical surface SG forming the valve guide is formed across the upstream and downstream sides of the surface on which the valve seat 214S is formed, and can not only sufficiently support the stroke of the valve 203, but also Since the circumferential dead space can be effectively used, the axial dimension of the suction valve portion INV can be reduced. Further, since the valve urging spring S4 is provided between the end surface SH of the valve stopper S0 and the bottom surface of the flat portion 203F of the valve 203 on the valve stopper S0 side, the opening portion 214P and the cylindrical portion 203H of the valve 203 are connected. The valve 203 and the valve biasing spring S4 can be arranged inside the opening 214P while sufficiently securing the passage area of the fuel introduction passage 10p formed therebetween. Further, since the valve urging spring S4 can be disposed by effectively utilizing the dead space on the inner peripheral side of the valve 203 located inside the opening 214P forming the fuel introduction passage 10p, the axial dimension of the suction valve portion INV is obtained. Can be shortened.

  The valve 203 has a valve guide (SG) at the center thereof, and has an annular projection 203S that comes into contact with the receiving surface S2 of the annular surface portion S3 of the valve stopper S0 immediately outside the valve guide (SG). Further, a valve seat 214S is formed at a position on the radially outer side, and the annular gap SGP further extends to the radially outer side, and a valve is provided outside the annular gap SGP (that is, on the outer peripheral side of the valve 203 and the stopper S0). Fuel passages S6 formed on the inner peripheral surface of the housing are sequentially formed. Since the fuel passage S6 is formed radially outside the valve seat 214, there is an advantage that the fuel passage S6 can be made sufficiently large.

  In addition, since the annular projection 203S that contacts the receiving surface S2 of the stopper S0 is provided inside the valve seat 214 inside the annular gap SGP, the fluid pressure P4 on the pressurizing chamber side is applied to the annular gap SGP during the valve closing operation described later. Can be acted on quickly to increase the valve closing speed when the valve 203 is pressed against the valve seat 214.

≪Fuel spill state≫
The fuel spill state will be described with reference to FIGS. 1, 2, 3A and 4B. Although the piston plunger 2 starts rotating from the bottom dead center position and starts to rise in the direction of the arrow Q1, part of the fuel sucked into the pressurizing chamber 12 is partially released from the fuel passages Sn1 to Sn3 because the coil 204 is not energized. Is spilled (spilled) into the low-pressure fuel chamber 10a through the annular fuel passage 10S and the fuel introduction passage 10P. When the flow of the fuel in the fuel passage S6 switches from the direction of the arrow R4 to the direction of the arrow R5, the flow of the fuel stops for a moment, and the pressure in the annular gap SGP increases. At this time, the plunger rod biasing spring 202 presses the valve 203 against the stopper S0. . Rather, the dynamic pressure of the fuel flowing into the annular fuel passage 10S of the valve seat 214 pushes the valve 203 toward the stopper S0 side, and the valve 203 and the stopper S0 are attracted by the effect of sucking out the fuel flow flowing around the outer periphery of the annular gap SGP. The valve 203 is firmly pressed against the stopper S0 by the fluid force acting on the stopper S0.

  From the moment the fuel flow is switched in the R5 direction, the fuel in the pressurizing chamber 12 flows to the low-pressure fuel chamber 10a in the order of the fuel passage S6, the annular fuel passage 10S, and the fuel introduction passage 10P. Here, the cross-sectional area of the fuel passage of the fuel passage 10S is set smaller than the cross-sectional area of the fuel passage of the fuel passage S6 and the fuel introduction passage 10P. That is, the sectional area of the fuel passage is set to be smallest in the annular fuel passage 10S. Therefore, a pressure loss occurs in the annular fuel passage 10S, and the pressure in the pressurizing chamber 12 starts to increase. However, the fluid pressure P4 is received by the annular surface of the stopper S0 on the pressurizing chamber side, and acts on the valve 203. Hateful. Further, since the pressure equalizing hole S5 has a small hole diameter, the dynamic fluid force of the fuel on the side of the pressurizing chamber 12 indicated by the arrow P4 hardly acts on the valve 203.

  In the annular space SGP, in the spill state, the fuel flows from the low-pressure fuel chamber 10a to the damper chamber 10b through the four fuel holes 214Q. On the other hand, as the piston plunger 2 moves upward, the volume of the auxiliary fuel chamber 250 increases, so that the fuel flows from the damper chamber 10b through the vertical passage 250B, the annular passage 21G, and the fuel passage 250A in the direction indicated by the arrow R8. Part of the fuel is introduced into the sub chamber 250. Thus, since the cold fuel is supplied to the fuel sub-chamber, the sliding portion between the piston plunger 2 and the cylinder 20 is cooled.

≪Fuel discharge status≫
The state of fuel discharge will be described with reference to FIG. When the coil 204 is energized based on a command from the engine control unit ECU in the above-described fuel spill state, a closed magnetic circuit CMP is generated as shown in FIG. When the closed magnetic circuit CMP is formed, a magnetic attractive force is generated between the opposing surfaces of the inner core 206B and the anchor 207 in the magnetic gap GP. This magnetic attraction overcomes the urging force of the plunger rod urging spring 202 and attracts the anchor 207 and the plunger rod 201 fixed thereto to the inner core 206B. At this time, the fuel in the storage space 206K of the plunger rod biasing spring 202 and the magnetic gap GP is discharged from the fuel passage 214K to the low pressure passage through the periphery of the through hole 201H and the anchor 207. As a result, the anchor 207 and the plunger rod 201 are smoothly displaced toward the inner core 206B. When the anchor 207 contacts the inner core 206B, the anchor 207 and the plunger rod 201 stop moving.

  The plunger rod 201 is pulled toward the inner core 206B, and the urging force that has pressed the valve 203 toward the stopper S0 disappears. Therefore, the valve 203 is urged away from the stopper S0 by the urging force of the valve urging spring S4. 203 starts a valve closing movement. At this time, the pressure in the annular space SGP located on the outer peripheral side of the annular projection 203S becomes higher than the pressure on the low-pressure fuel 10a side with the increase in the pressure in the fuel pressurizing chamber 12, thus closing the valve 203. Help exercise. The valve 203 comes into contact with the seat 214, and the valve is closed. This state is shown in FIG. Since the piston plunger 2 continuously rises, the volume of the pressurizing chamber 12 decreases, and when the pressure in the pressurizing chamber 12 increases, as shown in FIGS. 1 and 2, the discharge valve 63 of the discharge valve unit 60 becomes a discharge valve. Fuel is discharged in a direction along arrows R6 and R7 through the discharge joint 11 from the discharge passage 11A and away from the valve seat 61 by overcoming the force of the urging spring 64.

  Thus, the annular gap SGP has an effect of assisting the valve closing movement of the valve 203. With only the valve biasing spring S4, there is a problem that the valve closing motion is not stable because the valve closing force of the suction valve is too small.

  Further, when the valve 203 is closed, fuel is supplied to the spring storage space SP through the equalizing hole S5, so that the pressure in the spring storage space SP becomes constant, and the force applied when the valve 203 closes is stabilized. The valve closing timing of the valve 203 can be stabilized.

  Thus, according to the present invention, it is possible to further improve the responsiveness of both opening and closing of the valve and further reduce variation in valve closing timing.

[Second embodiment]
A second embodiment will be described with reference to FIGS. 5 (A) and 5 (B). Portions having the same functions as those of the first embodiment are denoted by the same reference numerals. The electromagnetically driven suction valve of the second embodiment shown in FIGS. 5A and 5B is a so-called open-type valve having a valve 203 on the pressure chamber 12 side of a valve seat 214S. I have. The valve 203 is disposed closer to the pressurizing chamber (downstream of the valve seat) than the valve seat 214S, and a valve stopper S0 that regulates the opening position of the valve 203 is provided between the pressurizing chamber 12 and the valve 203. The valve stopper S0 is provided with through holes SN1-SN6 (corresponding to the notches Sn1-Sn3 in the first embodiment) which form a fuel passage on the outer side in the circumferential direction of the valve 203. One end of the cylindrical fuel introduction passage 10P is connected to the low-pressure fuel chamber 10a, and the other end is connected to an annular (disk-shaped) fuel passage 10S formed between the valve seat 214S and the flat portion 203F of the valve 203. ing. The through holes SN1 to SN6 constitute a passage that connects the pressurizing chamber 12 and the annular (disk-shaped) fuel passage 10S. A valve urging spring S4 for urging the valve 203 in the closing direction is provided between the valve stopper S0 and the valve 203. Between the valve 203 and the valve stopper S0, a spring housing space SP containing the valve biasing spring S4 is formed. An equalizing hole S5 is provided at the center of the valve stopper S0 as a communication passage connecting the spring housing space SP and the pressurizing chamber 12.

  When the plunger in the pressurizing chamber 12 enters the compression process and the coil is energized at the valve closing timing, the plunger rod 201 is pulled to the left of the drawing against the force of the plunger rod biasing spring 202, and the plunger rod is pulled. The tip of 201 is separated from the flat portion 203F of the bulb 203. At this time, the valve 203 is urged in the valve closing direction by the valve urging spring S4. The pressure of the pressurizing chamber is introduced through the pressure equalizing hole S5 inside the valve biasing spring S4, especially at the center without crossing the spring. The introduced pressure is evenly distributed on the inner peripheral surface of the valve 203 and assists the valve 203 in closing without adversely affecting the valve closing operation. When the compression process is completed and the piston plunger 2 enters the suction process, the valve 203 receives the force of the plunger rod urging spring 202 and the force of the valve urging spring S4 due to the pressure difference between the upstream and downstream of the annular (disk-shaped) fuel passage 10S. In contrast, it is pushed rightward in the drawing and shifts to the valve open state. At this time, the fuel in the spring storage space SP is discharged from the pressure equalizing hole S5 by the movement of the valve 203. In this embodiment, the outer peripheral surface of the valve 203 is guided by the inner peripheral surface of the valve stopper S0, but the function of the pressure equalizing hole S5 is basically the same as that of the first embodiment.

[Third embodiment]
A third embodiment will be described with reference to FIGS. 6 (A) and 6 (B). Portions having the same functions as those of the first embodiment are denoted by the same reference numerals. The electromagnetically driven suction valve of the third embodiment shown in FIGS. 6A and 6B is a so-called open-type valve having a valve 203 on the side of the pressurizing chamber 12 of the valve seat 214S. I have. The valve 203 is disposed closer to the pressurizing chamber (downstream of the valve seat) than the valve seat 214S, and a valve stopper S0 that regulates the opening position of the valve 203 is provided between the pressurizing chamber 12 and the valve 203. The through holes SN1-SN6 penetrating the valve stopper S0 obliquely outward from the end face of the valve stopper S0 on the side of the pressurizing chamber (corresponding to the notches Sn1-Sn3 in the first embodiment, the through holes SN1-SN6 in the second embodiment). ) Is provided. In the third embodiment, the outer periphery of the valve stopper S0 is press-fitted and fixed to the inner periphery of the distal end of the valve housing 214. A guide SGV for guiding the inner peripheral surface of the valve 203 is provided on the outer periphery of the valve stopper S0 on the valve 203 side. A cylindrical fuel passage 12V is formed between the outer periphery of the valve 203 and the inner periphery of the valve housing. One end of the cylindrical fuel introduction passage 10P is connected to the low-pressure fuel chamber 10a, and the other end has an annular shape (ring) formed between the valve seat 214S and an annular projecting surface 203M protruding from the flat portion 203F of the valve 203. State) is connected to the fuel passage 10S. The through holes SN1 to SN6 constitute a passage connecting the pressurizing chamber 12 and the cylindrical fuel passage 12V, and the annular (ring-shaped) fuel passage 10S communicates with the cylindrical passage 12V. A valve urging spring S4 for urging the valve 203 in the closing direction is provided between the valve stopper S0 and the valve 203. Between the valve 203 and the valve stopper S0, a spring housing space SP containing the valve biasing spring S4 is formed. An equalizing hole S5 is provided at the center of the valve stopper S0 as a communication passage connecting the spring housing space SP and the pressurizing chamber 12. A hole S6 having a larger diameter than the pressure equalizing hole S5 is provided on the pressure chamber 12 side of the pressure equalizing hole S5, and the pressure equalizing hole S5 penetrates from the bottom of the hole S6 to the spring storage chamber SP. The configuration of the equalizing holes S5 with the holes having different diameters is the same as that of the first embodiment. In this embodiment, one end outer circumference of the valve housing 214 is press-fitted into the inner circumference of a guide hole 1GH provided in the pump housing 1, and the other end is axially fixed by a C-type ring CR locked to the pump housing 1. I have.

  When the plunger in the pressurizing chamber 12 enters the compression process and the coil is energized at the valve closing timing, the plunger rod 201 is pulled to the left against the force of a spring (not shown), and the tip of the plunger rod 201 Is separated from the annular projection 203M of the valve 203. At this time, the valve 203 is urged in the valve closing direction by the valve urging spring S4. The pressure of the pressurizing chamber is introduced through the pressure equalizing hole S5 into the valve biasing spring S4, particularly at the center, without crossing the valve biasing spring S4. The pressure introduced into the spring accommodating space SP is evenly distributed on the inner peripheral surface of the valve 203, and assists the valve 203 in closing without adversely affecting the valve closing operation. When the compression process is completed and the piston plunger 2 enters the suction process, the valve 203 is actuated by the force of the spring (not shown) of the electromagnetic drive device and the pressure difference between the upstream and downstream of the annular (ring-shaped) fuel passage 10S. Is pushed to the right of the drawing against the force of (1) and shifts to the valve open state. At this time, the fuel in the spring storage chamber SP is discharged from the pressure equalizing hole S5 by the movement of the valve 203. In this embodiment, the inner peripheral surface of the valve 203 is guided by a guide SGV formed on the outer periphery of the valve stopper S0, but the function of the pressure equalizing hole S5 is basically the same as that of the first embodiment.

Reference Signs List 1 pump housing 2 piston plunger 3 lifter 4 spring 5 plunger seal 6 discharge valve 7 cam 10 suction joint 10a low-pressure fuel chamber 10b damper chamber 10p fuel introduction passage 10S annular fuel passage 11 discharge joint 12 pressurizing chamber 20 cylinder 21 cylinder holder 22 seal Holder 30 Damper holder 40 Damper cover 50 Fuel tank 51 Low pressure pump 53 Common rail 54 Injector 56 Pressure sensor 80 Metal diaphragm damper (assembly)
200 electromagnetic drive type suction valve mechanism 201 plunger rod 203 valve 203H cylindrical portion 214 valve housing 214P opening 214S valve seat 250 fuel sub-chamber 600 engine control unit (ECU)
EMD Electromagnetic drive mechanism INV Suction valve S0 Valve stopper SG Valve guide

Claims (10)

A suction valve urged in a valve opening direction by a plunger rod,
A valve stopper that comes into contact with the suction valve in a stroke to a fully open position,
A guide portion formed on the valve stopper, for guiding an axial stroke of the suction valve;
A spring disposed on the inner peripheral side of the guided surface of the suction valve guided by the guide portion, and biasing the suction valve in a valve closing direction;
In a state where the suction valve has been stroked to the fully open position, a communication path formed by the valve stopper and the suction valve, and in which the space in which the spring is disposed and the pressurizing chamber are communicated, is formed.
On the radial outer side of the spring with respect to the center axis of the spring, the suction valve is disposed adjacent to the spring ,
The suction valve has a bottom portion supporting one end of the spring, and a cylindrical portion extending from the bottom portion to the valve stopper side,
On the outer peripheral surface of the cylindrical portion, the guided surface guided by the guide portion formed on the inner peripheral surface of the valve stopper is formed,
Wherein the inner peripheral surface of the cylindrical portion, the high-pressure fuel supply pump according to claim Rukoto regulating surface is formed in which the facing spring directly regulates the radial movement of the spring. The high-pressure fuel supply pump according to claim 1,
At least a part of the suction valve is a high-pressure fuel supply pump facing the communication path without interposing a member constituting the spring between the communication path and the communication path. The high-pressure fuel supply pump according to claim 2,
A high-pressure fuel supply pump in which at least a part of the suction valve faces an opening of the communication passage on the side opposite to the pressurizing chamber without interposing a member constituting the spring between the communication passage and the suction passage. A suction valve urged in a valve opening direction by a plunger rod,
A valve stopper that comes into contact with the suction valve in a stroke to a fully open position,
A guide portion formed on the valve stopper, for guiding an axial stroke of the suction valve;
A spring disposed on the inner peripheral side of the guided surface of the suction valve guided by the guide portion, and biasing the suction valve in a valve closing direction;
In a state where the suction valve has been stroked to the fully open position, a communication path formed by the valve stopper and the suction valve, and in which the space in which the spring is disposed and the pressurizing chamber are communicated, is formed.
The suction valve has an annular surface portion where a contact portion with the valve stopper is formed, and the annular surface portion forms a gap between the suction valve and the valve stopper when the suction valve is in contact with the valve stopper. It is configured to be,
The suction valve has a bottom portion supporting one end of the spring, and a cylindrical portion extending from the bottom portion to the valve stopper side,
On the inner peripheral surface of the cylindrical portion, the guided surface guided by the guide portion formed on the outer peripheral surface of the valve stopper, and directly face the spring to restrict the radial movement of the spring. A high-pressure fuel supply pump , wherein a regulating surface is formed . The high-pressure fuel supply pump according to claim 4,
The high-pressure fuel supply pump, wherein the annular surface portion is formed on an outer peripheral side of the guided surface of the suction valve. The high-pressure fuel supply pump according to claim 4 or 5,
A high-pressure fuel supply pump, wherein the annular surface portion of the suction valve has a surface substantially perpendicular to a closing direction of the suction valve. The high-pressure fuel supply pump according to any one of claims 4 to 6,
The valve stopper is provided with a fuel passage that communicates a space between the annular surface portion of the suction valve and the valve seat with the pressurizing chamber, and all of the suction valve is on the inner circumferential side with respect to the fuel passage. High-pressure fuel supply pump located in the. The high-pressure fuel supply pump according to claim 1 or 4 ,
A high-pressure fuel supply pump in which a plurality of the communication passages are formed at equal intervals around a central axis of the spring. The high-pressure fuel supply pump according to claim 1 or 4 ,
A high-pressure fuel supply pump formed so that a center axis of the suction valve overlaps a center axis of the guide portion of the valve stopper. The high-pressure fuel supply pump according to claim 1 or 4 ,
A high-pressure fuel supply pump formed such that a center axis of the communication passage overlaps a center axis of the guide portion of the valve stopper.