JP6527995B2 - High-pressure fuel supply pump with an electromagnetically driven suction valve - Google Patents

Description

  The present invention relates to a high pressure fuel supply pump provided with an electromagnetic drive type suction valve, and in particular, the electromagnetic drive type suction valve is constituted by a so-called outer opening type valve provided with a valve on the pressure chamber side of the valve seat. About things.

  Conventionally, in this type of high-pressure fuel supply pump, as described in, for example, JP 2009-203987 A, the valve is formed of a cylindrical member, and the pressurizing chamber side (the downstream side of the valve seat) The outer peripheral surface of the said valve was guided by the inner peripheral part of the cylindrical valve holder located in 2.).

JP, 2009-203987, A

  For this reason, a large space for installing the valve and the valve holder is required between the valve seat portion and the circumferential surface portion of the pressure chamber, and the pump can not be miniaturized.

The object of the present invention is to make it possible to easily assemble an electromagnetically driven suction valve mechanism of a high-pressure fuel supply pump .

In order to achieve the above object, according to the present invention, in a high pressure fuel supply pump, a piston plunger (2) reciprocated inside a pressurizing chamber (12) and an intake side of the pressurizing chamber (12) are provided. An electromagnetically driven suction valve mechanism (200), the electromagnetically driven suction valve mechanism (200) comprising: an anchor (207) for driving the plunger rod (201); and a fixed core (201) for attracting the anchor (207). and 206), a yoke (205), wherein the fixed core (206) is disposed on the inner peripheral portion, has, at the bottom of the front Symbol fixed core (206) through holes (206H) is formed, the fixed The core (206) is press-fitted into the inner peripheral surface of the cylindrical space (205H) of the yoke (205), and is fixed by abutting against the bottom of the yoke (205) .

Specifically, it is desirable to have a spring (202) which biases the plunger rod (201) in a direction in which the suction valve (203) moves away from the valve seat (214S). Also, a cylindrical hole (200H) is formed from the peripheral wall of the pump housing (1) toward the pressurizing chamber (12), and the yoke (205) is the cylindrical hole (200H) of the pump housing (1). It is desirable to insert into the inside of said cylindrical hole (200H) from the open end side of. In addition, it is desirable that the outer peripheral portion (205X ) of the yoke (205) be press-fitted and fixed in the insertion hole (200H) of the pump housing (1). Further, a coil (202) for generating a magnetic attraction force between opposing surfaces of the fixed core (206) and the anchor (207), and a cup-shaped side yoke (204Y) for housing the coil (202) The inner peripheral surface on the side of the pump housing (1) and the outer peripheral surface (205Y) of the yoke (205) are fixed to the fixed core (206) of the cup-shaped side yoke (204Y) by press fitting. Is desirable.
In addition, a coil (202) for generating a magnetic attraction force between opposing surfaces of the fixed core (206) and the anchor (207), and a cup-shaped side yoke (204Y) in which the coil (202) is disposed. And when the coil (202) is energized, the cup-shaped side yoke (204Y), the yoke (205), the fixed core (206) and the anchor (207) form a closed magnetic path (CMP) as a magnetic field. Preferably, it is formed around the coil (202) across the air gap (GP). Preferably, the spring (202) is disposed on the inner circumferential surface of the fixed core (206). The fixed core (206) preferably has a cylindrical space (206K) inside, and the spring (202) is preferably disposed in the cylindrical space (206K). Further, it is desirable that a cylindrical space portion (207K) in which the spring (202) is disposed be formed inside the anchor (207). Further, it is desirable that the anchor (207) be drawn to the fixed core (206) against the biasing force of the spring (202) at the timing of closing the suction valve (203). Further, when the anchor (207) is magnetically attracted to the fixed core (206) against the biasing force of the spring (202), the plunger rod (201) is pulled away from the suction valve (203). It is desirable to be configured.

According to the present invention configured as described above, it is possible to easily assemble the electromagnetically driven suction valve mechanism of the high pressure fuel supply pump.

FIG. 1 is an overall longitudinal sectional view of a high pressure fuel supply pump provided with an electromagnetic drive type suction valve according to a first embodiment of the present invention. FIG. 1 is a system configuration diagram showing an example of a fuel supply system using a high pressure fuel supply pump according to the present invention. FIG. 1 is an enlarged cross-sectional view of an electromagnetic drive type suction valve according to a first embodiment of the present invention, showing a state at the time of fuel suction. FIG. 1 is an enlarged cross-sectional view of an electromagnetic drive type suction valve according to a first embodiment of the present invention, showing a state at the time of a fuel overflow (spill). FIG. 1 is an enlarged cross-sectional view of an electromagnetic drive type suction valve according to a first embodiment of the present invention, showing a state at the time of fuel discharge. FIG. 3 is an enlarged cross-sectional view of an electromagnetic drive type suction valve according to a first embodiment of the present invention, and is a view on arrows P in FIGS. 3A and 4A; The left side is a P arrow view of the valve. It is a partial section disassembled perspective view of an electromagnetic drive type suction valve which becomes the 1st example in which the present invention was carried out. FIG. 6 is an exploded perspective view, partly in section, of an electromagnetic drive type suction valve according to a first embodiment of the present invention; FIG. FIG. 1 is a partial cross-sectional perspective view of an electromagnetic drive type suction valve according to a first embodiment in which the present invention is implemented, showing an assembled state; FIG. 2 is a partially enlarged cross-sectional view of an electromagnetic drive type suction valve according to a second embodiment of the present invention, showing a fuel suction state and a state at the time of spill (spill). FIG. 8A is a view on arrow P of FIG. 8A and is a view on arrow P of the stopper. The fuel discharge state is shown in a partially enlarged cross-sectional view of an electromagnetic drive type suction valve according to a second embodiment of the present invention. It is a partially expanded sectional view of a portion of a stopper of an electromagnetic drive type suction valve according to a second embodiment of the present invention, and a partially cut perspective view.

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

First Embodiment
A first embodiment of a high pressure fuel supply pump according to the present invention will be described with reference to FIGS. 1 to 7. As FIG. 1 can not be numbered in detail, the symbols in the description which are not numbered in FIG. 1 are listed in the enlargements of FIGS. 2 to 7.

  The pump housing 1 is provided with a recess 12A that forms a bottomed cylindrical space with one end opened, and the cylinder 20 is inserted into the recess 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. Further, since the piston plunger 2 is in sliding engagement 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 by the fuel which enters between the sliding surfaces. As a result, the pressurizing chamber 12 is defined between the tip of the piston plunger 2 and the inner wall surface of the recess 12A and the outer peripheral surface of the cylinder 20.

  A cylindrical hole 200H is formed from the peripheral wall of the pump housing 1 toward the pressure chamber 12, and the suction valve portion INV and the electromagnetic drive mechanism portion EMD of the electromagnetic drive type suction valve mechanism 200 are formed in the cylindrical hole 200H. A part of is inserted. The inside of the pump housing 1 is sealed from the atmosphere by joining the joint surface 200R of the outer peripheral surface of the electromagnetically driven suction valve mechanism 200 and the cylindrical hole 200H by laser welding. The cylindrical hole 200H sealed by attaching the electromagnetically driven suction valve mechanism 200 functions as the low pressure fuel chamber 10A.

  A cylindrical hole 60H is provided from the circumferential wall of the pump housing 1 toward the pressure chamber 12 at a position facing the cylindrical hole 200H with the pressure chamber 12 interposed therebetween. The discharge valve unit 60 is attached to the cylindrical hole 60H. The discharge valve unit 60 includes a valve seat member 61B having a valve seat 61 at its front end and a through hole 11A serving as a discharge passage at its 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 biasing the valve 63 in the direction of pressing the valve seat 61 are provided. A discharge joint 11 fixed to the pump housing 1 by welding is provided on the counter pressure chamber side opening of the cylindrical hole 60H.

The electromagnetically driven suction valve mechanism 200 includes a plunger rod 201 which 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 electromagnetic drive type suction valve mechanism 200.

A plunger rod urging spring 202 is provided at the other end of the plunger rod 201, and the valve 203 urges the plunger rod in a direction away from the valve seat 214S. A valve stopper S <b> 0 is fixed to a tip inner peripheral portion of the valve housing 214.
The valve 203 is reciprocably held 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 away from the valve stopper S0 by the valve biasing spring S4.

  The valve 203 and the tip of the plunger rod 201 are biased by the respective springs in opposite directions, but since the plunger rod biasing spring 202 is constituted by a stronger spring, the plunger rod 201 is biased by the valve. The valve 203 is pushed in a direction (right direction in the drawing) away from the valve seat against the force of the spring S4, and as a result, the valve 203 is pressed against the valve stopper S0.

  Therefore, the plunger rod 201 opens the valve 203 via the plunger rod 201 by the plunger rod biasing spring 202 when the electromagnetic drive type suction valve mechanism 200 is OFF (when the electromagnetic coil 204 is not energized). It is biased in the direction of the valve. Therefore, when the electromagnetic drive type suction valve mechanism 200 is OFF, the plunger rod 201 and the valve 203 are maintained at the open position as shown in FIG. 1, FIG. 2 and FIG. 3A (detailed structure will be described later).

  Fuel is introduced 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 in accordance with the number of cylinders of the engine, and inject the high-pressure fuel sent to the common rail 53 to each of the cylinders according to the signal of the 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 6.

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

  The cylinder holder 21 is mounted 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 a male screw 21A formed on the outer periphery of the cylinder holder 21 is formed on the inner periphery of the open side end of the recess 12A of the pump housing 1 Screw into With the step 21D of the cylinder holder 21 locked to the periphery of the end opposite to the pressure chamber side of the cylinder 20, the cylinder holder 21 pushes the cylinder 20 toward the pressure chamber, whereby the sealing step 20A of the cylinder 20 is The pump housing 1 is pressed 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 between the inner peripheral surface of the anti-pressure chamber side end of the recess 12A of the pump housing 1 and the outer peripheral surface of the cylinder holder 21 at a position on the anti-pressure chamber side of the screw portion 21A (1A).

  The mounting flange 1D fixed to the outer periphery of the anti-pressure chamber side end portion of the pump housing 1 by the welding portion 1C is a screw fixing auxiliary sleeve 1E with the end outer periphery of the cylinder holder 21 inserted into the mounting hole EH of the engine block ENB. Is screwed to the engine block with a screw 1F, thereby fixing the pump 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, and a metal diaphragm damper 80 of a two-sheet metal diaphragm type is formed in the damper holder 30 (upper damper holder 30A, lower damper holder 30B) It is stored in a state of being held by The damper chamber 10B is formed by welding and joining the lower end portion of the cylindrical side wall of the damper cover 40 to the outer peripheral portion of the annular recess formed in the upper surface outer wall portion of the pump housing 1. In this embodiment, the suction joint 10 is fixed at the center of the damper cover 40 by welding.

  The metal diaphragm damper 80 seals the inside by welding the outer peripheral portion of the pair of upper and lower metal diaphragms 80A and 80B to each other over the entire periphery. The annular edge of the lower end on the inner peripheral side of the upper damper holder 30A is in contact with the upper annular edge of the metal diaphragm damper 80 inside the weld 80C of the metal diaphragm damper 80. The annular edge of the upper end on the inner peripheral side of the lower damper holder 30 is in contact with the lower annular edge of the metal diaphragm damper 80 inside the weld 80 C of the metal diaphragm damper 80. Thus, the metal diaphragm damper 80 is held between the upper damper holder 30A and the lower damper holder 30B at the upper and lower surfaces of the annular edge.

  The outer periphery of the damper cover 40 is formed in a cylindrical shape, and is fitted to the cylindrical portion 1G of the pump housing 1, and at this time, the inner peripheral surface of the damper cover 40 abuts on the upper annular surface of the upper damper holder 30A. The metal diaphragm damper 80 is fixed in the damper chamber by pressing the damper holder 30 together with the damper holder 30 against the step 1 H of the pump housing 1. In this state, the periphery of the damper cover 40 is laser welded, and the damper cover 40 is joined and fixed to the pump housing 1.

  An inert gas such as argon is enclosed in the hollow portion formed by the two-piece type metal diaphragms 80A and 80B, and this hollow portion changes its volume in response to a change in external pressure, thereby providing a pulsation damping function. Play. The fuel passage 80U between the metal diaphragm damper 80 and the damper cover 40 is a passage 30P formed in the upper damper holder 30A, and a passage 80P formed between the outer periphery of the upper damper holder 30A and the inner peripheral surface of the pump housing 1 It is connected with the damper chamber 10B as a fuel passage. The damper chamber 10B communicates with the low pressure fuel chamber 10A of the electromagnetically driven suction valve 20 through a communication hole 10C formed in the pump housing 1 as a bottom wall of the damper chamber 10B.

  A connecting portion between the small diameter portion 2A of the piston plunger 2 and the large diameter portion 2B in sliding engagement with the cylinder 20 is connected by a conical surface 2K. A fuel sub chamber 250 is formed between the plunger seal and the lower end surface of the cylinder 20 around the conical surface. The fuel sub chamber 250 captures the fuel leaking from the joint surface between the cylinder 20 and the piston plunger 2.

  An annular passage 21G partitioned between the inner peripheral surface of the pump housing 1, the outer peripheral surface of the cylinder 20, and the upper end surface of the cylinder holder 21 has one end formed by the damper chamber 10B by a vertical passage 250B formed through the pump housing 1 , And is connected to the fuel sub chamber 250 via a fuel passage 250A formed in the cylinder holder 21. Thus, the damper chamber 10B and the fuel sub-chamber 250 are in communication 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 is increased, 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 into the damper chamber 10B via the vertical passage 250B, the annular passage 21G, and the fuel passage 250A.

  When the piston plunger 2 ascends from the bottom dead center in a state where the valve 203 is maintained at the open position (the coil 204 is not energized), the fuel sucked into the pressurizing chamber is the low pressure fuel chamber from the valve 203 being opened. It spills to 10A and flows to 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 pressure chamber 12, and the fuel from the relief valve (not shown) are merged. . As a result, the fuel pulsations of the respective fuels merge at the damper chamber 10 B and are absorbed by the metal diaphragm damper 80.

  In FIG. 2, the portion enclosed by a broken line shows the pump body portion of FIG. The electromagnetically driven suction valve 200 includes a bottomed cup-shaped yoke 205 which also serves as the body of the electromagnetic drive mechanism part EMD on the inner peripheral side of the coil 204 formed annularly. In the yoke 205, a fixed core 206 and an anchor 207 are accommodated at the inner peripheral portion with the plunger rod biasing spring 202 interposed therebetween. As shown in detail in FIG. 3A, the fixed core 206 is firmly fixed to the bottom of the yoke 205 by press fitting. The anchor 207 is fixed to the other end of the plunger rod 201 by press fitting, and faces the fixed core 206 via the magnetic gap GP. The coil 204 is housed in a cup-shaped side yoke 204Y, and the inner peripheral surface of the open end of the side yoke 204Y is press-fit fitted on the outer peripheral portion of the annular flange portion 205F of the yoke 205 to fix them both. ing. A closed magnetic path CMP crossing the magnetic gap GP is formed around the coil 204 by the yoke 205, the side yoke 204Y, the fixed core 206, and the anchor 207. The portion of the yoke 205 facing the periphery of the magnetic gap GP is formed to have a small thickness, and forms a magnetic diaphragm 205S. Thereby, the magnetic flux leaking through the yoke 205 is reduced, and the magnetic flux passing through the magnetic gap GP can be increased.

  As shown in FIGS. 3A and 3B, a valve housing 214 having a bearing portion 214B is fixed by press-fitting to the inner peripheral portion of the open side end cylindrical portion 205G of the yoke 205. 201 extends through the bearing 209 to a valve 203 provided on the inner periphery of the opposite end portion of the valve housing 214 on the side opposite to the bearing 209.

  As shown in FIG. 4A in an enlarged manner, three press-fit surface portions SP1-SP3 of the valve stopper S0 are press-fitted to the annular stepped inner peripheral surface 214D of the end of the valve housing 214 opposite the bearing 214B and fixed by laser welding. It is done. The width of the press-fit step portion of the inner circumferential surface 214D and the width in the press-fit direction of the three press-fit surface portions SP1-SP3 are formed to be the same.

  A valve 203 is mounted between the tip of the plunger rod 201 and the valve stopper S0 so as to be capable of reciprocating with the valve biasing spring S4 interposed therebetween. The valve 203 is provided with an annular surface portion 203R in which the surface on one side faces the valve seat 214S formed in the valve housing 214 and the surface on the other side faces the valve stopper S0. A bottomed cylindrical portion extending to the tip of the plunger rod 201 is provided at the center of the annular surface portion 203R, and the bottomed cylindrical portion is constituted by a bottom flat portion 203F and a cylindrical portion 203H. The cylindrical portion 203H protrudes into the low pressure fuel chamber 10A through an opening 214P formed in the valve housing 214 inside the valve seat 214S.

  The tip of the plunger rod 201 is in contact with the surface of the flat portion 203F of the plunger rod side end of the valve 203 in the low pressure fuel chamber 10A. In the cylindrical portion between the bearing 214B of the valve housing 214 and the opening 214P, four fuel through holes 214Q are provided at equal intervals in the circumferential direction. The four fuel through holes 214Q communicate the low pressure fuel chamber 10A inside and outside the valve housing 214. A cylindrical fuel introduction passage 10P connected to the annular fuel passage 10S between the valve seat 214S and the annular surface portion 203R is formed between the outer peripheral surface of the cylindrical portion 203H and the peripheral surface of the opening 214P.

  The valve stopper S0 has a projecting portion ST provided with a cylindrical surface portion SG projecting to the bottomed cylindrical portion side of the valve 203 at the center of the annular surface portion S3, and the cylindrical surface portion SG has a stroke in the axial direction of the valve 203 It functions as a guiding portion to guide (hereinafter, the cylindrical surface portion SG is also referred to as a valve guide).

  The valve biasing spring S4 is held between the valve side end surface SH of the projecting 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 travels to the fully open position, the annular projection 203S formed at the center of the annular surface portion 203R of the valve 203 is the annular surface S3 (width HS3) of the annular surface portion S3. Contact the receiving surface S2 (width HS2). At this time, an annular gap SGP is formed around the annular protrusion 203S. The annular gap SGP causes the pressure P4 of the fuel on the pressurizing chamber side to act on the valve 203 when the valve 203 starts to move in the valve closing direction so that the valve 203 quickly separates from the valve stopper S0. Play.

  As shown in FIG. 4B, the valve stopper S0 is provided with press-in surface portions SP1 to SP3 formed in three places at specific intervals on the outer peripheral surface of the valve stopper S0. Further, notches SN1 to SN3 each having an angle θ in the circumferential direction at an angle θ in the circumferential direction are provided between the press-fit surface portions SP1 (SP2, SP3). The plurality of press-fit surface portions SP1-SP3 of the valve stopper S0 are press-fit fitted on the cylindrical inner peripheral surface of the valve housing 214 on the downstream side of the valve seat 214S, and between the press-fit fitting portion and the press-fit fitting portion Between the circumferential surface of the stopper and the inner circumferential surface of the valve housing 214, three valve seat downstream side fuel passages S6 of width H1 are formed across the angle θ in the circumferential direction. The valve seat downstream side fuel passage S6 is formed as a fuel passage having a large area on the outer side of the outer peripheral surface of the valve 203, so the passage area can be made larger than the annular fuel passage 10S formed in the valve seat 214S. As a result, the flow of fuel becomes smooth since the passage resistance against the inflow of fuel into the pressurizing chamber and the spilling of fuel from the pressurizing chamber does not occur.

  In FIG. 4B, the diameter D1 of the outer peripheral surface of the valve 203 is slightly smaller than the diameter D3 of the notch portion of the valve stopper S0. As a result, in FIG. 3B, in the spill state where fuel flows from the pressurizing chamber to the low pressure fuel chamber and the damper chamber 10B along the fuel flow R5, the pressurizing chamber 12 indicated by the arrow P4 on the annular surface portion 203R of the valve 203 It is difficult for static and dynamic fluid forces of the side fuel to act. Therefore, the force of the plunger rod urging spring 202 for applying a force to press the valve 203 against the valve stopper S0 in this state does not have to overcome the fluid force P4, and therefore a weak spring can be used. As a result, the anchor 207 is magnetically attracted to the fixed core 206 against the force of the plunger rod biasing spring 202 at the valve closing timing of the valve 203, and the plunger rod 201 is valve 203 as shown in FIG. The electromagnetic force at the time of pulling away from is small. This means that the number of turns of the coil 204 can be reduced, and the size of the electromagnetic drive mechanism part EMD can be reduced accordingly.

  As shown in FIGS. 3A, 3B, 4A, and 4B, the annular surface portion 203R of the valve 203 has a diameter D1 that is a protrusion of the valve stopper S0 provided at the central portion thereof. It comprised 1.5 to 3 times the diameter D2 of the inner peripheral surface which receives the valve guide formed of cylindrical surface part SG of ST. The radial width VS1 of the annular projection 203S in contact with the receiving surface S2 (width HS2) of the annular surface S3 (width HS3) of the valve stopper S0 formed on the outside is the annular gap SGP formed on the outside It was configured smaller than the width VS2. Furthermore, the valve seat 214 is formed inward from the outer periphery of the annular surface portion 203R of the valve 203 to a width VS3. As a result, the acting force of the fuel from the low pressure fuel chamber 10A side when the valve 203 is opened and the acting force of the fuel acting on the valve from the pressurizing chamber side when the valve 203 is closed are also uniform in the radial direction of the valve 203 Because it acts in a well-balanced manner, the radial rattling of the valve 203 also reduces the force to tilt in the direction of inclination with respect to the central axis of the valve 203, and the on-off valve Operation is smooth. This is an important effect when using small valves of a few millimeters in diameter and a few grams in weight and where the flow direction reverses during high flow rates and short times.

  As shown in FIG. 4A, in this embodiment, at the moment when the valve 203 is closed, the plunger rod 201 is attracted to the left by the electromagnetic force at the moment it is closed, so the tip thereof separates from the flat portion 203F of the valve 203 A gap 201G is formed therebetween. At this time, since the pressure in the low pressure fuel chamber 10A is rising from the bottom dead center of the piston plunger 2, fuel is replenished from the damper chamber 10B and the low pressure fuel chamber 10A by an increase in the volume in the fuel sub chamber 250. Therefore, the pressure in the low pressure fuel chamber 10A is lower than when the volume of the fuel sub chamber 250 is reduced accordingly. This lowered pressure also acts on the area of the flat portion 203F of the valve 203 where the tip of the plunger rod 201 is in contact, so the pressure difference between the pressure chamber and the low pressure chamber becomes large, and the valve 203 is closed. The action is faster.

  Further, the insertion hole 200H of the diameter DS1 into which the suction valve portion INV is inserted is provided with a tapered portion TA at the middle part in the insertion direction, and the diameter DS3 on the pressurizing chamber side of this tapered portion TA is smaller than the diameter DS1. . The outer diameter of the cylindrical parts 214F and 214G of the valve housing 214 located at the tip of the suction valve INV is smaller than that of the section SF1 (cylindrical part 214F) in the section SF2 (cylindrical part 214G) on the outer periphery of the tip. ing. In the section of section SF1, the outer diameter of the cylindrical portion 214F is larger than the diameter DS1 of the insertion hole 200H, and is fitted in the insertion hole 200H of the pump housing 1 by interference fit. In the section SF2, the outer diameter of the cylindrical portion 214G is smaller than the diameter DS1 of the insertion hole 200H, and this portion is loosely fitted. This makes it easy to automatically center the tip of the valve housing 214 by the tapered portion TO of the inlet when inserting the suction valve portion INV into the insertion hole 200H, and further, it is automatically centripetally inclined by the internal tapered portion TA. This is a device to prevent insertion. This improves the yield at the time of automatic assembly. Further, by achieving the fluid seal on the pressure chamber 12 side and the low pressure fuel chamber 10A side in the interference fit portion (section SF1) of the cylindrical portion 214F only by the press fitting operation, the workability of the automatic assembly is improved. is there.

  If the tip end portion 205Z of the yoke 205 is dimensioned to be inserted into the taper TO immediately after the end edge portion of the valve housing 214 is inserted into the taper TA, the centripetal action at the time of assembly can be smoothly performed. That is, since the electromagnetic drive mechanism unit EMD performs automatic centripetal after centripetal of the suction valve INV is completed, the centripetal action of the suction valve unit INV and the centripetal action of the electromagnetic drive mechanism part EMD do not interfere with each other. As a result, centripetal work in automatic assembly can be smoothly performed, and assembly defects can be reduced.

  The outer diameter of the tip of the yoke 205 inserted into the insertion hole 200H is smaller than the inner diameter DS1 of the insertion hole 200H, and the two are loosely fitted. This reduces the insertion force of the yoke 205 attached to the tip of the suction valve unit INV as much as possible, and prevents the excessive force from acting on the suction valve unit INV at the time of insertion of the electromagnetic drive mechanism unit EMD. It has the effect of shortening the working time of the work. When the yoke 205 is completely inserted into the insertion hole 200H, the joint end surface 205J of the yoke 205 abuts on the mounting surface of the pump housing 1. In this state, the entire circumference of the joint portion W1 is laser-welded to seal the inside, and the electromagnetic drive mechanism portion EMD is fixed to the pump housing 1.

  As for the outer diameter of the bearing portion 214B of the valve housing 214, the outer diameter of the press-fit portion 214J on the outer periphery of the bearing portion 214B on the valve 203 side is larger than the outer diameter of the tip portion 214N on the opposite valve 203 side. . This is to obtain an automatic centripetal effect when the bearing portion 214B is press-fitted to the inner peripheral surface of the cylindrical projection 205N formed at the tip of the yoke 205. A plurality of fuel through holes 214K are formed in the bearing portion 214B. When the anchor 207 reciprocates, the fuel flows in and out through the fuel through hole 214K, whereby the operation of the anchor 207 becomes smooth.

  Further, fuel flows in and out through a fuel through hole 201K formed in the plunger rod 201, a space 206K between the fixed core 206 in which the plunger rod biasing spring 202 is accommodated and the anchor 207, and the anchor 207. This further smoothens the operation of the anchor 207. Without the fuel through hole 201K, when the fixed core 206 and the anchor 207 are in contact with each other, the space 206K is completely sealed. In this state, when the anchor 207 and the plunger rod 201 start the valve opening movement to the right in the figure by the plunger rod biasing spring 202, the pressure of the space 206K is reduced for a moment, the valve opening is delayed or the valve opening movement is Although there was a problem that it became unstable, it was able to solve this by the above-mentioned composition.

  The operation of the first embodiment will be described based on FIG. 1, FIG. 2, FIG. 3 (A), FIG. 3 (B), FIG. 4 (A) and FIG. 4 (B).

<< fuel intake state >>
First, the fuel suction state will be described with reference to FIGS. 3 (A) and 3 (B). In the suction process in which the piston plunger 2 is lowered 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 the non-energized state. The biasing force SP1 of the plunger rod biasing spring 202 biases the plunger rod 201 toward the valve 203 as shown by the arrow. On the other hand, the biasing force SP2 of the valve biasing spring S4 biases the valve 203 in the direction indicated by the arrow. Since the biasing force of the plunger rod biasing spring 202 is set larger than the biasing force SP2 of the valve biasing spring S4, the biasing forces of both springs bias the valve 203 in the valve opening direction at this time. In addition, 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 represented 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. It receives a force in the valve direction. Further, the fluid frictional force P2 generated between the fuel flow flowing into the pressure chamber 12 along the arrow R4 through the fuel introduction passage 10P and the circumferential surface of the cylindrical portion 203H of the valve 203 moves the valve 203 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 214S and the annular surface portion 203R of the valve 203 acts on the annular surface portion 203R of the valve 203 to attach the valve 203 in the valve opening direction. Power up. Due to these biasing forces, the valve 203 having a weight of several milligrams opens quickly as the piston plunger 2 starts to descend, and travels until it strikes the stopper ST.

  The valve seat 214S 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 on which 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 slightly charged from the valve opening speed of the valve 203 by the fact that the periphery of the plunger rod 201 and the anchor 207 is filled with the stagnant fuel and the frictional force with the bearing 214B acts. The stroke to the right in the drawing is delayed. As a result, a slight gap is created between the tip end surface of the plunger rod 201 and the flat portion 203F of the valve 203. Therefore, the valve opening force applied from the plunger rod 201 is reduced momentarily. However, since the pressure P1 of the fuel in the low pressure fuel chamber 10A acts on this gap without delay, the valve opening force applied from the plunger rod 201 (plunger rod urging spring 201) is reduced to open this valve 203. The fluid force in the direction of Thus, when the valve 203 is opened, static pressure and dynamic pressure of fluid act on the entire surface of the low pressure fuel chamber 10A side of the valve 203, 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 the valve guide formed by the cylindrical surface portion SG of the projecting portion ST of the valve stopper S0, and the valve 203 is not displaced in the radial direction Smooth strokes. The cylindrical surface portion SG forming the valve guide is formed on the upstream side and the downstream side across the surface on which the valve seat 214 is disposed, and can not only sufficiently support the stroke of the valve 203 but also the inner peripheral side of the valve 203 Since the dead space of can be used effectively, the axial dimension of the suction valve portion INV can be shortened.

  Further, since the valve biasing spring S4 is disposed between the end surface SH of the valve stopper S0 and the bottom surface portion of the flat portion 203F of the valve 203 on the valve stopper S0 side, between the opening 214P and the cylindrical portion 203H of the valve The valve 203 and the valve biasing spring S4 can be disposed inside the opening 214P while securing a passage area of the fuel introduction passage 10P formed in the above. Further, since the valve biasing 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 dimension of the suction valve INV in the axial direction Can be shortened.

  The valve 203 has a valve guide (SG) at its center, and an annular projection 203S that contacts the receiving surface S2 of the annular surface S3 of the valve stopper S0 immediately outside the valve guide (SG). Further, the valve seat 214S is formed at the radially outer position, and the annular gap SGP further extends to the radially outer side, and outside the annular gap SGP (that is, on the outer peripheral side of the valve 203 and the valve stopper S0). A fuel passage S6 formed by the inner circumferential surface of the valve housing is sequentially formed. Since the fuel passage S6 is formed on the radially outer side of the valve seat 214S, there is an advantage that the fuel passage S6 can be made sufficiently large. By making the fuel passage S6 sufficiently large, it is possible to suppress that the flow velocity of the suctioned fuel becomes extremely fast at the time of suction operation to cause a sonic phenomenon or cavitation in the fuel passage S6 or the pressurizing chamber. As a result, it is possible to suppress the occurrence of erosion in the fuel passage S6 and the edge portion of the metal in the pressurizing chamber.

  Further, since the annular projection 203S contacting the receiving surface S2 of the valve stopper S0 is provided inside the valve seat 214S inside the annular gap SGP, the fluid pressure on the pressurizing chamber side is transferred to the annular gap SGP at the time of valve closing operation described later. The valve closing speed at the time of pressing the valve 203 against the valve seat 214S can be increased by causing P4 to act quickly.

«Fuel spill condition»
The fuel spill state will be described with reference to FIG. 2 and FIG. 3 (B). The piston plunger 2 turns from the bottom dead center position and starts rising in the direction of the arrow Q1, but since the coil 204 is in the non-energized state, a part of the fuel taken into the pressure chamber 12 is the fuel passage S6, annular The low pressure fuel chamber 10A is spilled (overflowed) through the fuel passage 10S and the fuel introduction passage 10P. When the flow of fuel in the fuel passage S6 switches from the direction of arrow R4 to the direction of R5, the flow of fuel stops for a moment, and the pressure in the annular gap SGP increases. At this time, the plunger biasing spring 202 presses the valve 203 against the valve stopper S0. . Rather, the dynamic force of the fuel flowing into the annular fuel passage 10S of the valve seat 214S presses the valve 203 against the valve stopper S0 side, and the suction effect of the fuel flow flowing around the annular gap SGP The fluid force acting to attract forces the valve 203 firmly against the valve stopper S0.

  From the moment the fuel flow is switched to 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 · annular fuel passage 10S and fuel introduction passage 10P. Here, the fuel passage cross-sectional area of the annular fuel passage 10S is set smaller than the fuel passage cross-sectional area of the fuel passage S6 · and the fuel introduction passage 10P. That is, the fuel passage cross-sectional area is set to be the 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 rise, but the fluid pressure P4 is received by the annular surface on the pressurizing chamber side of the valve stopper S0 and acts on the valve 203 It is difficult to do.

  In the spill state, the annular space SGP flows from the low pressure fuel chamber 10A to the damper chamber 10B through the four fuel through holes 214Q. On the other hand, as the piston plunger 2 ascends, the volume of the sub fuel chamber 250 is increased, so the fuel flow in the downward arrow direction of the arrow R8 passing through the vertical passage 250B, the annular passage 21G and the fuel passage 250A causes the damper chamber 10B to A part of the fuel is introduced into fuel 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 condition»
The fuel discharge state will be described with reference to FIG. When the coil 204 is energized on the basis of a command from the engine control unit ECU in the aforementioned fuel spill state, a closed magnetic path CMP is generated as shown in FIG. 3 (A). When the closed magnetic path CMP is formed, a magnetic attraction force is generated between the fixed core 206 and the facing surface of the anchor 207 in the magnetic gap GP. The magnetic attraction force overcomes the biasing force of the plunger rod biasing spring 202 and attracts the anchor 207 and the plunger rod 201 fixed thereto to the stationary core 205. At this time, fuel in the magnetic gap GP and the storage chamber 206 K of the plunger rod biasing spring 202 is discharged from the fuel passage 214 K to the low pressure passage through the periphery of the fuel passage 201 K and the anchor 207. As a result, the anchor 207 and the plunger rod 201 are smoothly displaced to the fixed core 206 side. When the anchor 207 contacts the fixed core 206, the anchor 207 and the plunger rod 201 stop moving.

  Since the plunger rod 201 is pulled toward the fixed core 206 and the biasing force pressing the valve 203 against the valve stopper S0 disappears, the biasing force of the valve biasing spring S4 biases the valve 203 away from the valve stopper S0. The valve 203 starts the closing motion. At this time, the pressure in the annular gap SGP positioned on the outer peripheral side of the annular protrusion 203S becomes higher than the pressure on the low pressure fuel chamber 10A with the pressure increase in the pressurizing chamber 12, thus closing the valve 203 Help with exercise. The valve 203 comes in contact with the seat 214S to close the valve. This state is shown in FIG. 4 (A). As the piston plunger 2 continues to rise, the volume of the pressurizing chamber 12 decreases, and when the pressure in the pressurizing chamber 12 rises, as shown in FIGS. 1 and 2, the discharge valve 63 of the discharge valve unit 60 is a discharge valve. The fuel is discharged in a direction along arrows R6 and R7 from the discharge passage 11A through the discharge joint 11 by separating from the valve seat 61 by overcoming the force of the biasing spring 64.

  Thus, the annular gap SGP has the effect of assisting the valve closing movement of the valve 203. There is a problem that the valve closing movement is not stable because the valve closing force of the suction valve is too small with the valve biasing spring S4 alone, but this problem could be solved in the embodiment.

The moment the valve 203 contacts the seat 214S and the valve is completely closed, the plunger rod 201 is completely drawn toward the fixed core 206, and the tip of the plunger rod 201 is separated from the low pressure fuel chamber 10A side end face of the valve 203 An air gap 201G is formed.
Thus, the valve 203 does not receive a force in the valve opening direction by the plunger rod 201 at the time of the valve closing operation of the valve 203, so the valve closing operation becomes faster. Further, since the valve 203 does not collide with the plunger rod 201 at the time of the valve closing operation of the valve 203 and no striking sound is generated, a quiet valve mechanism can be obtained.

  After the valve 203 is completely closed and the pressure in the pressurizing chamber 12 is increased to start high-pressure discharge, the coil 204 is deenergized. The magnetic attraction force generated between the opposing surfaces of the fixed core 206 and the anchor 207 disappears, and the anchor 207 and the plunger rod 201 start moving toward the valve 203 by the biasing force of the plunger rod biasing spring 202, and the plunger rod When 201 contacts the bottom flat portion 203F of the valve 203, the movement is stopped. Since the valve closing force by the pressure in the pressurizing chamber 12 is already sufficiently larger than the acting force of the plunger rod urging spring 202, even if the plunger rod 201 pushes the low pressure fuel chamber 10A side surface of the valve 203, the valve 203 It does not open. This state is a preparation operation in which the plunger rod 201 urges the valve 203 in the valve opening direction at the moment when the piston plunger 2 shifts from the top dead center to the lowering direction Q2. Since the air gap 201G is a slight air gap of several tens to several hundreds of microns and the valve 203 is urged by the pressure in the pressure chamber 12 to make the valve 203 rigid, the valve of the plunger rod 201 is The collision noise upon collision to 203 does not become noise because its frequency is higher than the audio frequency and its energy is also small.

  By controlling the timing at which the coil 204 is energized based on the command from the engine control unit ECU, the fuel discharged at high pressure can be adjusted. If the energization timing is controlled so that the valve 203 is closed immediately after the piston plunger 2 shifts from the bottom dead center to the top dead center, less fuel is spilled and more fuel is discharged at high pressure. If the energization timing is controlled so that the valve 203 is closed immediately before the piston plunger 2 shifts from the top dead center to the bottom dead center, the amount of fuel to be spilled and the amount of fuel to be discharged at high pressure are reduced.

  The assembly procedure of the suction valve unit INV will be described with reference to FIGS. 5 to 7.

  The partial cross-sectional perspective views of FIGS. 5 to 7 show cross sections cut 90 degrees toward the central axis. The outer periphery of the cylindrical fixed space 206 with a bottom is inserted into the cylindrical space 205 H at the center of the cylindrical yoke 205 with a bottom, and the outer periphery is press-fitted and fixed to the inner circumferential surface of the cylindrical space 205 H. A through hole 206H functioning as an air vent at the time of press-fitting is formed in the bottomed portion of the fixed core 206, and a cylindrical space 206K is formed inside. The open end of the fixed core 206 is located inside the magnetic diaphragm 205S formed on the outer periphery of the yoke 205.

  The anchor 207 and the plunger rod 201 are press-fit fitted and fixed in advance. A partition 207J is provided inside the anchor 207, and a cylindrical space portion 207K formed inside the anchor 207 at the center of the partition 207J to form a part of the accommodation space of the plunger urging spring 202 and the plunger rod 201 An opening 207H communicating with the fuel passage 201K formed at the center of the valve is provided. The plunger rod biasing spring 202 is housed in the cylindrical space portion 206K of the fixed core 206, and the plunger rod biasing spring is held in the cylindrical space portion 207K on the opposite plunger rod 201 side of the anchor 207 in which the plunger rod 201 is press fitted. The outer periphery of the anchor 207 on the side opposite to the plunger rod 201 is loosely fitted in the cylindrical space portion 205H of the yoke 205 so that the half portion of 202 is housed. The end on the side opposite to the plunger rod 201 of the anchor 207 faces the end face of the fixed core 206 across the magnetic air gap GR at a portion inside the magnetic diaphragm 205S of the yoke 205.

  The annular flange portion 205F of the yoke 205 is provided with a circumferential surface 205Y to which the open end side inner circumferential surface of the side yoke 204Y shown in FIG. 3A is press-fit fitted. Since the coil 204 is mounted between the side yoke 204Y and the outer periphery of the yoke 205, the radial width of the annular flange portion 205F is formed to a width corresponding to the radial width of the coil 204. A stepped portion 205K having a joint end face 205J (smaller in diameter than the annular flange portion 205F) abutting on the mounting surface of the pump housing 1 is provided on the side opposite to the fixed core 206 of the annular flange portion 205F. A small diameter cylindrical projection 205N is provided which protrudes from the lower end. The cylindrical projection 205N is fitted into the cylindrical insertion hole 200H of the pump housing 1 from the open end side of the cylindrical insertion hole 200H of the pump housing 1 until the joint end surface 205J abuts on the mounting surface of the pump housing 1 It is inserted.

  The suction valve portion INV is formed in advance by assembling the valve housing 214, the valve 203, the valve biasing spring S4, and the valve stopper S0. The cylindrical portion 203H of the valve 203 is inserted into the opening 214P of the valve housing 214 and assembled so that the annular surface portion 203R of the valve 203 faces the valve seat 214S. Next, the valve biasing spring S4 is inserted into the cylindrical portion 203H of the valve 203. Finally, the projecting portion ST provided with the cylindrical surface portion SG of the valve stopper S0 is inserted into the inner periphery of the cylindrical portion 203H of the valve 203, and the press-fit surface portions SP1-SP3 of the valve stopper S0 are press-fitted into the annular stepped portion 214D of the valve housing. In combination, the suction valve unit INV is configured.

  The outer periphery of the bearing portion 214B of the valve housing 214 is press-fit into the inner periphery of the cylindrical projection 205N of the yoke 205 in which the fixed core 206, the plunger rod biasing spring 202 and the assembly of the anchor 207 and the plunger rod 201 are assembled in this order. By being fixed by fitting, the suction valve unit INV and the electromagnetic drive mechanism unit EMD are assembled integrally. In this state, the anti-anchor 207 side end of the plunger rod 201 is inserted through the bearing hole 214H at the center of the bearing portion 214B and supported so as to be capable of reciprocating.

  The thus assembled electromagnetically driven suction valve mechanism 200 press-fits the suction valve portion INV into the insertion hole 200H of the pump housing 1, and inserts the outer periphery 205X of the cylindrical projection portion 205N of the electromagnetic drive mechanism portion EMD. It is fixed to the pump housing by laser welding the outer periphery of 205J. In this manner, the assembly of the plunger rod 201 and the suction valve unit INV are sequentially assembled on the inner peripheral portion of one side of the yoke 205, and the coil 204 and the side yoke 204Y are sequentially assembled on the outer peripheral portion on the other side. Two hundred can be formed, and an assembly configuration suitable for automation is obtained.

Second Embodiment
8 to 10 show a second embodiment. The same reference numerals as in the first embodiment indicate the same as those in the first embodiment. In the second embodiment, the shape of the valve stopper S0 and the arrangement of the valve biasing spring S4 are different. A hollow cylindrical portion STH extending along the inner circumferential surface of the cylindrical portion 203H of the valve 203 is provided at the central portion of the valve stopper S0. The valve biasing spring S4 is accommodated in the inner peripheral portion of the hollow cylindrical portion STH. The outer peripheral surface of the hollow cylindrical portion STH is in sliding contact with the inner peripheral surface of the cylindrical portion 203H of the valve 203 to guide the reciprocation of the valve 203. In this embodiment, the dimension of the valve biasing spring S4 can be made longer than that of the first embodiment. The other configuration is the same as in the first embodiment. FIG. 8 shows a fuel intake state and a fuel spill state (valve open state), which correspond to FIGS. 3 (A) and 3 (B) of the first embodiment. FIG. 8B is a view on arrow P of FIG. 8A, which corresponds to FIG. 4B of the first embodiment. FIG. 9 shows a fuel discharge state (valve closing state), which corresponds to FIG. 4 (A) of the first embodiment.

  Although in the first and second embodiments, the valve seat and the valve are in contact with each other in the annular flat portion, the present invention can be applied to those in which the conical surface is in contact. In these embodiments, the axial dimension including the valve 203 and the valve stopper S0 can be reduced to several millimeters. In this embodiment, the distance from the mounting surface of the electromagnetically driven suction valve mechanism 200 of the pump housing 1 to the end surface on the valve stopper pressurizing chamber side can be reduced, and the physique of the high pressure pump including the electromagnetically driven suction valve mechanism 200 It can be made smaller.

  Furthermore, according to the present embodiment, the following problems can be solved.

  When the piston plunger starts to move to the bottom dead center side (enters the suction process), the suction valve starts opening movement by the spring force and the pressure before and after the suction valve, but the area receiving the pressure before and after this suction valve is small As a result, there is a problem that the valve opening movement is delayed and unstable. Furthermore, when the area of the suction valve is increased in order to improve the response and stability of the valve opening movement, there are the following problems. When the piston plunger starts to move upward from the bottom dead center to the top dead center, the pressure loss and fluid force generated by the spilled fuel increase, and the suction valve may close at an unexpected timing. There is sex.

  In this embodiment, between the valve stopper and the valve, an annular projection forming a contact surface to be brought into contact when the valve moves to the fully open position and an annular gap located on the outer periphery of the annular projection are formed. . The pressure in the annular gap located on the outer peripheral side of the annular protrusion becomes higher than the pressure on the low pressure fuel passage side with the pressure increase in the fuel pressurizing chamber, and thus the annular gap has the effect of assisting the valve closing movement. There is. There is a problem that the valve closing motion is not stable because the valve closing force of the suction valve is too small if only the valve biasing spring is used, but this problem can be solved in the embodiment.

DESCRIPTION OF SYMBOLS 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 203 H cylindrical portion 214 valve housing 214 P opening portion 214 S valve seat 250 fuel sub chamber 600 engine control unit (ECU)
EMD Electromagnetic drive mechanism unit INV Intake valve unit S0 Valve stopper SG Cylindrical surface (valve guide)

Claims (11)

In the high pressure fuel supply pump,
A piston plunger (2) that reciprocates inside the pressure chamber (12);
An electromagnetic drive type suction valve mechanism (200) provided on the suction side of the pressure chamber (12);
The electromagnetically driven suction valve mechanism (200) comprises an anchor (207) for driving a plunger rod (201), a fixed core (206) for attracting the anchor (207), and the fixed core (206) at an inner peripheral portion. And a yoke (205) in which the
Through hole (206H) is formed in a bottom portion of the front Symbol fixed core (206),
The fixed core (206) is press-fit into the inner peripheral surface of the cylindrical space (205H) of the yoke (205) and fixed by abutting against the bottom of the yoke (205) . In the high pressure fuel supply pump according to claim 1,
A high pressure fuel supply pump comprising a spring (202) for biasing the plunger rod (201) in a direction away from the suction valve (203) from a valve seat (214S). In the high pressure fuel supply pump according to claim 2,
A cylindrical hole (200H) is formed from the peripheral wall of the pump housing (1) toward the pressure chamber (12),
The high pressure fuel supply pump is inserted into the cylindrical hole (200H) from the open end side of the cylindrical hole (200H) of the pump housing (1) as the yoke (205). In the high pressure fuel supply pump according to claim 3,
A high-pressure fuel supply pump in which an outer peripheral portion (205X ) of the yoke (205) is press-fitted and fixed in a through hole (200H) of the pump housing (1). In the high pressure fuel supply pump according to claim 1,
A coil (202) for generating a magnetic attraction between opposing surfaces of the fixed core (206) and the anchor (207);
A cup-shaped side yoke (204Y) for housing the coil (202);
High pressure in which the inner peripheral surface on the pump housing (1) side and the outer peripheral surface (205Y) of the yoke (205) are fixed to the fixed core (206) of the cup-shaped side yoke (204Y) by press fitting. Fuel supply pump. In the high pressure fuel supply pump according to claim 1 or 2,
A coil (202) for generating a magnetic attraction between opposing surfaces of the fixed core (206) and the anchor (207);
And a cup-shaped side yoke (204Y) in which the coil (202) is disposed;
When the coil (202) is energized, a closed magnetic circuit (CMP) is separated by a magnetic gap (GP) by the cup-shaped side yoke (204Y), the yoke (205), the fixed core (206) and the anchor (207). A high pressure fuel supply pump formed around the coil (202) accordingly. In the high pressure fuel supply pump according to claim 2,
The high pressure fuel supply pump, wherein the spring (202) is disposed on the inner circumferential surface of the fixed core (206). In the high pressure fuel supply pump according to claim 2,
The fixed core (206) has a cylindrical space (206K) inside,
The high pressure fuel supply pump, wherein the spring (202) is disposed in the cylindrical space (206K). In the high pressure fuel supply pump according to claim 2,
A high pressure fuel supply pump in which a cylindrical space (207K) in which the spring (202) is disposed is formed inside the anchor (207). In the high pressure fuel supply pump according to claim 2,
A high-pressure fuel supply pump configured such that the anchor (207) is attracted to the fixed core (206) against the biasing force of the spring (202) at the closing timing of the suction valve (203). In the high pressure fuel supply pump according to claim 9,
When the anchor (207) is magnetically attracted to the fixed core (206) against the biasing force of the spring (202), the plunger rod (201) is pulled away from the suction valve (203) High-pressure fuel supply pump configured to.

Images