JP5798799B2 - High pressure fuel supply pump with electromagnetically driven suction valve - Google Patents

Description

  The present invention relates to a high-pressure fuel supply pump having an electromagnetically driven intake valve, and in particular, the electromagnetically driven intake valve is configured as a so-called outwardly-opening type valve having a valve on the pressure chamber side of a valve seat. About things.

  Conventionally, in this type of high-pressure fuel supply pump, as described in, for example, Japanese Patent Laid-Open No. 2009-203987, the amount of high-pressure pumped fuel is adjusted by controlling the ON (energization) timing to the solenoid. . When the solenoid is turned on (energized) during the compression process by the piston plunger of the high pressure fuel supply pump, the intake valve is closed and high pressure pumping of fuel is started. Immediately after the start of high-pressure pumping and before the next suction process by the piston plunger starts, the solenoid is turned off (energization is completed), and the suction valve is opened by the biasing force of the spring in synchronization with the start of the suction stroke.

JP 2009-203987 A

  As soon as the intake stroke starts, the intake valve starts opening, and when the intake valve opens completely, the intake valve collides with the stopper and ends the opening movement.However, especially when the vehicle is idling, where quietness is required. There was a problem that the sound of this collision was loud. In another conventional technique, a plunger of an electromagnetic mechanism collides with a fixed core portion to generate sound.

  An object of the present invention is to reduce the speed at which the suction valve opens, and to reduce the collision sound generated when the suction valve or the plunger collides with another member.

  In order to achieve the above object, according to the present invention, after the solenoid is turned on (energized) during the compression process by the piston plunger of the high-pressure fuel supply pump, the energized state continues until the next intake process by the piston plunger. did. The magnetic attraction force generated by the energization current to the solenoid during the suction process is configured to weaken the acting force for opening the suction valve.

  According to the present invention configured as described above, the following effects can be obtained.

  The magnetic force generated by the current applied to the solenoid during the suction process acts in the direction opposite to the opening direction of the suction valve, but it is weaker than the force to open the suction valve, so the suction valve starts to open. Then, the valve is opened slowly, and the suction valve or the plunger collides with a fixed member such as a stopper to stop the movement. Since the speed of the suction valve immediately before the collision is reduced by the amount of the magnetic force, it is possible to reduce the sound generated when the suction valve or the plunger collides with the fixed member.

1 is an overall longitudinal sectional view of a high-pressure fuel supply pump including an electromagnetically driven intake valve according to a first embodiment in which the present invention is implemented. 1 is a system configuration diagram showing an example of a fuel supply system using a high-pressure fuel supply pump in which the present invention is implemented. 1 is an enlarged cross-sectional view of an electromagnetically driven intake valve according to a first embodiment in which the present invention is implemented, and shows a state during fuel intake. FIG. 1 is an enlarged cross-sectional view of an electromagnetically driven intake valve according to a first embodiment in which the present invention is implemented, and shows a state at the time of fuel overflow (spill). 1 is an enlarged cross-sectional view of an electromagnetically driven intake valve according to a first embodiment in which the present invention is implemented, and shows a state during fuel discharge. FIG. FIG. 3 is an enlarged cross-sectional view of the electromagnetically driven suction valve according to the first embodiment in which the present invention is implemented, and shows a P arrow view of FIGS. 3 (A) and 4 (A). The left side is a P arrow view of the valve. 1 is a partial cross-sectional exploded perspective view of an electromagnetically driven intake valve according to a first embodiment in which the present invention is implemented. FIG. 6 is a partially sectional exploded perspective view of the electromagnetically driven suction valve according to the first embodiment in which the present invention is implemented, and shows a state in which a part of FIG. 5 is assembled. 1 is a partial cross-sectional perspective view of an electromagnetically driven intake valve according to a first embodiment in which the present invention is implemented, and shows an assembled state. It is a figure of the control method of the electromagnetically driven suction valve which becomes 1st Example with which this invention was implemented. It is a figure of the control method of the electromagnetically driven suction valve which becomes 2nd Example with which this invention was implemented.

  Embodiments of the present invention will be described below with reference to the drawings.

[First embodiment]
A first embodiment of a high-pressure fuel supply pump in which the present invention is implemented will be described with reference to FIGS.

  Since the reference numerals in FIG. 1 cannot be attached to the details, the reference numerals in the description that are not shown in FIG. 1 are shown in the enlarged views of FIGS.

  The pump housing 1 is provided with a recess 12A that forms a bottomed cylindrical space with one end open, and a 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. Since the piston plunger 2 is slidingly engaged 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, the pressurizing chamber 12 is defined between the tip of the piston plunger 2, 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 pressurizing chamber 12, and the cylindrical hole 200H has a suction valve portion INV and an electromagnetic drive mechanism portion EMD of the electromagnetically driven suction valve mechanism 200. A part of is inserted. The joint surface 200R between the outer peripheral surface of the electromagnetically driven suction valve mechanism 200 and the cylindrical hole 200H is joined by laser welding, so that the inside of the pump housing 1 is sealed from the atmosphere. The cylindrical hole 200H sealed by attaching the electromagnetically driven intake valve mechanism 200 functions as the low pressure fuel chamber 10A.

  A cylindrical hole 60 </ b> H is provided from the peripheral wall of the pump housing 1 toward the pressurizing chamber 12 at a position facing the cylindrical hole 200 </ b> H across the pressurizing chamber 12. A discharge valve unit 60 is mounted in the cylindrical hole 60H. The discharge valve unit 60 includes a valve seat member 61B having a valve seat 61 formed at the tip and 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. A valve 63 and a spring 64 that urges the valve 63 in a direction to press the valve 63 against the valve seat 61 are provided in the valve holder 62. A discharge joint 11 fixed to the pump housing 1 by welding is provided at the opening portion on the side opposite to the pressure chamber of the cylindrical hole 60H.

  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 214 </ b> S formed on a valve housing 214 provided at an end of the electromagnetically driven intake 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 S 0 is fixed to the inner peripheral portion of the tip of the valve housing 214. The valve 203 is held between the valve seat 214S and the valve stopper S0 so as to be able to reciprocate. A valve urging spring S4 is disposed between the valve 203 and the valve stopper S0, and the valve 203 is urged in a direction away from the valve stopper S0 by the valve urging spring S4.

  The valve 203 and the tip of the plunger rod 201 are urged by respective springs in opposite directions. However, since the plunger rod urging spring 202 is formed of a stronger spring, the plunger rod 201 is urged by the valve. The valve 203 is pressed against the force of the spring S4 in a direction away from the valve seat (right direction in the drawing), 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 electromagnetically driven suction valve mechanism 200 is OFF (when the electromagnetic coil 204 is not energized). It is energizing in the direction of valve. Therefore, when the electromagnetically driven suction valve mechanism 200 is OFF, the plunger rod 201 and the valve 203 are maintained in the valve open position as shown in FIGS. 1, 2, and 3A (detailed configuration will be described later).

  The fuel is guided from the fuel tank 50 to the suction joint 10 as the fuel inlet of the pump housing 1 by the low pressure pump 51.

  A plurality of injectors 54 and pressure sensors 56 are attached to the common rail 53. The injectors 54 are mounted in accordance with the number of cylinders of the engine, and inject high-pressure fuel sent to the common rail 53 into each cylinder in response to a signal from an engine control unit (ECU) 600. 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 excess high-pressure fuel to the upstream side of the discharge valve 6.

  A lifter 3 provided at the 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 the cylinder 20 and reciprocates by the cam 7 rotated by an engine cam shaft 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 and is 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 that seals 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 male thread portion 21A formed on the outer periphery of the cylinder holder 21 is the thread portion 1A of the female thread portion formed on the inner periphery of the open side end of the recess 12A of the pump housing 1. Screw in. The cylinder holder 21 pushes the cylinder 20 toward the pressurizing chamber while the stepped portion 21D of the cylinder holder 21 is engaged with the peripheral edge of the cylinder 20 on the side opposite to the pressurizing chamber. It is pressed against the pump housing 1 to form a seal portion 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 21 </ b> C seals the space between the inner peripheral surface of the recess 12 </ b> A of the recess 12 </ b> A of the pump housing 1 and the outer peripheral surface of the cylinder holder 21 at the position of the screw portion 21 </ b> A (1 </ b> A) on the anti-pressurization chamber side.

  The mounting flange 1D fixed to the outer periphery of the end of the pump housing 1 on the side opposite to the pressurization chamber by the welded portion 1C is inserted into the mounting hole EH of the engine block ENB and the screw fixing auxiliary sleeve 1E. And screwed to the engine block with a screw 1F, whereby the pump is 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, and a double metal diaphragm type metal diaphragm damper 80 is provided in the damper holder 30 (upper damper holder 30A, lower damper holder 30B). It is stored in a state of being sandwiched between the two. The damper chamber 10 </ b> B 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 an annular recess formed in the upper surface outer wall portion of the pump housing 1. In this embodiment, the suction joint 10 is fixed to the center of the damper cover 40 by welding.

  The double metal diaphragm damper 80 has a pair of upper and lower metal diaphragms 80 </ b> A and 80 </ b> B butted together and welded around the entire circumference to seal the inside. The annular end edge of the lower end on the inner peripheral side of the upper damper holder 30 </ b> A is in contact with the upper annular edge of the double metal diaphragm damper 80 on the inner side of the welded portion 80 </ b> C of the double metal diaphragm damper 80. The annular edge at the upper end on the inner peripheral side of the lower damper holder 30 is in contact with the annular edge at the lower side of the double metal diaphragm damper 80 inside the welded portion 80C of the double metal diaphragm damper 80. Thus, the double metal diaphragm damper 80 is sandwiched 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 into 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 and is a double metal By pressing the diaphragm damper 80 together with the damper holder 30 against the step portion 1H of the pump housing 1, the double metal diaphragm damper 80 is fixed in the damper chamber. 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 sealed in the hollow portion formed by the two-plate metal diaphragms 80A and 80B, and the volume of the hollow portion changes in response to an external pressure change. Play. A fuel passage 80U between the double metal diaphragm damper 80 and the damper cover 40 is formed between a passage 30P formed in the upper damper holder 30A, and the outer periphery of the upper damper holder 30A and the inner peripheral surface of the pump housing 1. It is connected to a damper chamber 10B as a fuel passage through a passage 80P. The damper chamber 10B is communicated with the low pressure fuel chamber 10A of the electromagnetically driven suction valve 200 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 that slides on 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 fuel leaking from the sliding surface between the cylinder 20 and the piston plunger 2.

  An annular passage 21G defined 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 a damper chamber 10B at one end by a vertical passage 250B formed through the pump housing 1. And is connected to the fuel sub chamber 250 via a fuel passage 250 </ b> A formed in the cylinder holder 21. Thus, the damper chamber 10B and the fuel sub chamber 250 communicate with each other by the longitudinal passage 250B, the annular passage 21G, and the fuel passage 250A.

  When the piston plunger 2 moves up and down (reciprocating), the taper 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 to the fuel sub chamber 250 through 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 rises from the bottom dead center in a state where the valve 203 is maintained at the valve open position (the coil 204 is not energized), the fuel sucked into the pressurized chamber is transferred from the valve 203 being opened to the low pressure fuel chamber. It overflows (spills) to 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, the portion surrounded by a broken line indicates the pump body portion of FIG. The electromagnetically driven suction valve mechanism 200 includes a cup-shaped yoke 205 with a bottom that also serves as the body of the electromagnetically driven mechanism EMD on the inner peripheral side of the annularly formed coil 204. In the yoke 205, a fixed core 206 and an anchor 207 are accommodated in an inner peripheral portion with a plunger rod biasing spring 202 interposed therebetween. As shown in detail in FIG. 3A, the fixed core 206 is firmly fixed to the bottomed portion of the yoke 205 by press fitting. The anchor 207 is fixed to the end of the plunger rod 201 on the side opposite to the valve by press fitting, and faces the fixed core 206 via a magnetic gap GP. The coil 204 is housed in a cup-shaped side yoke 204Y, and the inner peripheral surface of the open end portion of the side yoke 204Y is press-fitted and fitted to the outer peripheral portion of the annular flange portion 205F of the yoke 205, so that both are fixed. ing. A closed magnetic path CMP that crosses 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 that faces the periphery of the magnetic gap GP is formed with 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 tubular portion 205G of the yoke 205, and the plunger rod 201 extends through the bearing 209 to the valve 203 provided at the inner peripheral portion of the end of the valve housing 214 on the side opposite to the bearing 209.

  As shown in an enlarged view in FIG. 4A, three press-fitting surface portions SP1-SP3 of the valve stopper S0 are press-fitted into the annular stepped inner peripheral surface 214D at the end of the valve housing 214 opposite to the bearing 214B and fixed by laser welding. Has been. The width of the press-fitting step portion of the inner peripheral surface 214D and the width of the three press-fitting surface portions SP1-SP3 in the press-fitting direction are formed to have the same dimension.

  A valve 203 is mounted between the tip of the plunger rod 201 and the valve stopper S0 so as to be able to reciprocate with a valve biasing spring S4 interposed therebetween. The valve 203 includes an annular surface portion 203R whose one surface faces a valve seat 214S formed on the valve housing 214 and whose other surface faces the valve stopper S0. A center portion of the annular surface portion 203R has a bottomed cylindrical portion extending to the tip of the plunger rod 201, and the bottomed cylindrical portion is composed of a bottom plane portion 203F and a cylindrical portion 203H. The cylindrical portion 203H protrudes into the low pressure fuel chamber 10A through the opening 214P formed in the valve housing 214 inside the valve seat 214S.

  The distal end of the plunger rod 201 is in contact with the surface of the flat portion 203F at the plunger rod side end of the valve 203 in the low pressure fuel chamber 10A. Four fuel passage holes 214Q are provided at equal intervals in the cylindrical portion between the bearing 214B and the opening 214P of the valve housing 214 in the circumferential direction. These four fuel passage holes 214Q communicate with 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 having a cylindrical surface portion SG projecting toward the bottomed cylindrical portion 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 guide portion for guiding (the cylindrical surface portion SG is also referred to as a valve guide SG).

  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 protrusion 203S formed at the center of the annular surface portion 203R of the valve 203 becomes the annular surface portion S3 (width HS3) of the valve stopper S0. It contacts the receiving surface S2 (width HS2). At this time, an annular gap SGP is formed around the annular protrusion 203S. This annular gap SGP has a function of quickly separating the valve 203 by quickly applying the pressure P4 of the fuel on the pressurizing chamber side to the valve 203 when the valve 203 starts to move in the valve closing direction so that the valve 203 can be quickly separated from the valve stopper S0. Play.

  As shown in FIG. 4B, the valve stopper S0 includes press-fitting surface portions SP1-SP3 formed at three positions with a specific interval on the outer peripheral surface of the valve stopper S0. Further, a notch SN1-SN3 having an angle θ in the circumferential direction and a radial width H1 is provided between the press-fit surface portions SP1 (SP2, SP3). The plurality of press-fitting surface portions SP1-SP3 of the valve stopper S0 are press-fitted and fitted to the cylindrical inner peripheral surface of the valve housing 214 on the downstream side of the valve seat 214S, and between the press-fitting fitting portion and the press-fitting fitting portion, Between the circumferential surface of the stopper S0 and the inner circumferential surface of the valve housing 214, three valve seat downstream side fuel passages S6 having a width H1 are formed in the circumferential direction over an angle θ. Since the valve seat downstream side fuel passage S6 is formed as a fuel passage having a larger area further outside the outer peripheral surface of the valve 203, the passage area can be made larger than the annular fuel passage 10S formed in the valve seat 214S. As a result, there is no passage resistance against the inflow of fuel into the pressurizing chamber and the fuel spill from the pressurizing chamber, so that the fuel flow is smooth.

  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 of the valve stopper S0. As a result, in FIG. 3B, when the fuel is in a spill state where the fuel flows along the fuel flow R5 from the pressurizing chamber to the low pressure fuel chamber and the damper chamber 10B, the pressurizing chamber 12 indicated by the arrow P4 on the annular surface portion 203R of the valve 203 is shown. The static and dynamic fluid forces of the side fuel are difficult to act. Therefore, in this state, the force of the plunger rod biasing spring 202 that applies the force for pressing the valve 203 against the valve stopper S0 does not need to overcome the fluid force P4, and thus a weaker 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 urging spring 202 at the valve closing timing, and the plunger rod 201 is moved to the valve 203 as shown in FIG. The electromagnetic force when pulling away from the machine is small. This means that the number of turns of the coil 204 can be reduced, and the electromagnetic drive mechanism EMD can be made smaller by that amount.

  As shown in FIGS. 3 (A), 3 (B), 4 (A), and 4 (B), the annular surface portion 203R diameter D1 of the valve 203 is a protruding portion of the valve stopper S0 provided at the center thereof. It was configured to be 1.5 to 3 times the diameter D2 of the inner peripheral surface that receives the valve guide formed by the cylindrical surface portion SG of ST. Further, the radial width VS1 of the annular projection 203S that contacts the receiving surface S2 (width HS2) of the annular surface portion S3 (width HS3) of the valve stopper S0 formed on the outer side thereof is the annular gap SGP formed on the outside thereof. It was configured to be smaller than the width VS2. Furthermore, the valve seat 214S is formed in the portion of the width VS3 from the outer periphery of the annular surface portion 203R of the valve 203 to the inside. 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. Since the valve 203 operates in a well-balanced manner, the radial backlash of the valve 203 and the force to tilt the valve 203 in the tilt direction are reduced, and the opening / closing valve of the valve 203 is synergistic with the guide by the cylindrical surface portion SG of the valve stopper S0. The operation becomes smooth. This is an important effect when a small valve with a diameter of several millimeters and a weight of several grams is used in a place where the flow direction is reversed in a short time with a high flow rate.

  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 in the drawing by electromagnetic force. A gap 201G is formed between them. At this time, the pressure in the low pressure fuel chamber 10A is replenished with fuel from the damper chamber 10B and the low pressure fuel chamber 10A as much as the volume in the fuel sub chamber 250 is increased because the piston plunger 2 is rising from the bottom dead center. Therefore, the pressure in the low pressure fuel chamber 10A becomes lower than that when the volume of the fuel sub chamber 250 is reduced accordingly. This reduced pressure also acts on the area where the tip of the plunger rod 201 of the flat surface portion 203F of the valve 203 is in contact, so that the pressure difference between the pressure chamber side and the low pressure chamber side becomes large, and the valve 203 is closed. The movement is faster.

  Further, the insertion hole 200H having a diameter DS1 into which the suction valve portion INV is inserted has a taper portion TA at an intermediate portion in the insertion direction, and the diameter DS3 on the pressurizing chamber side from the taper portion TA is smaller than the diameter DS1. . The outer diameters of the cylindrical portions 214F and 214G of the valve housing 214 located at the distal end portion of the intake valve portion INV are configured to be smaller in the section SF2 (cylindrical portion 214G) on the outer periphery of the distal end portion than the section SF1 (cylindrical portion 214F). ing. In the section SF1, the outer diameter of the cylindrical portion 214F is larger than the diameter DS1 of the insertion hole 200H, and is fitted into the insertion hole 200H of the pump housing 1 by an 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 is because when the suction valve portion INV is inserted into the insertion hole 200H, the tip portion of the valve housing 214 is automatically centered by the tapered portion TO at the inlet portion, and is easy to insert, and further is automatically tilted by the internal tapered portion TA. It is a device to prevent it from being inserted. This improved the yield during automatic assembly. In addition, in the interference fitting portion (section SF1) of the cylindrical portion 214F, the fluid seal on the pressurizing chamber 12 side and the low pressure fuel chamber 10A side is achieved only by press fitting operation, thereby improving the workability of automatic assembly. is there.

  If the dimensions are such that the tip edge portion 205Z of the yoke 205 is inserted into the taper TO immediately after the tip edge portion of the valve housing 214 is inserted into the taper TA, the centripetal action during assembly can be performed smoothly. That is, since the electromagnetic drive mechanism EMD performs automatic centering after completion of the centripetal operation of the suction valve unit INV, the centripetal operation of the suction valve unit INV and the centripetal operation of the electromagnetic drive mechanism unit EMD do not interfere with each other. As a result, the centripetal operation in the automatic assembly can be performed smoothly, and assembly defects are 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 automatically reduces the insertion force of the yoke 205 attached to the tip of the suction valve portion INV as much as possible, and prevents the force from acting on the suction valve portion INV when the electromagnetic drive mechanism portion EMD is inserted. This has the effect of shortening the work time. When the yoke 205 is completely inserted into the insertion hole 200H, the joining end surface 205J of the yoke 205 comes into contact with the mounting surface of the pump housing 1. In this state, the entire circumference is laser-welded at the joint W1 to seal the inside, and the electromagnetic drive mechanism EMD is fixed to the pump housing 1.

  The outer diameter of the bearing portion 214B of the valve housing 214 is such that 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 counter valve 203 side. . This obtains an automatic centripetal effect when the bearing 214B is press-fitted into the inner peripheral surface of the cylindrical projection 205N formed at the tip of the yoke 205. A plurality of fuel passage holes 214K are formed in the bearing portion 214B. When the anchor 207 reciprocates, the fuel enters and exits through the fuel passage hole 214K, so that the operation of the anchor 207 becomes smooth.

  Further, the fuel enters and exits through a fuel passage hole 201 </ b> K formed in the plunger rod 201, a space 206 </ b> K between the fixed core 206 in which the plunger rod biasing spring 202 is accommodated and the anchor 207, and the periphery of the anchor 207. As a result, the operation of the anchor 207 becomes smoother. Without the fuel through hole 201K, when the fixed core 206 and the anchor 207 are in contact, 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 side in the figure by the plunger rod biasing spring 202, the pressure in the space 206K decreases for a moment, the valve opening is delayed, or the valve opening movement is not performed. Although there was a problem of becoming unstable, this configuration could solve this problem.

  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. 3 (A) and 3 (B). In the suction process 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 biasing force SP1 of the plunger rod biasing spring 202 biases the plunger rod 201 toward the valve 203 as indicated by an arrow. On the other hand, the urging force SP2 of the valve urging spring S4 urges the valve 203 in the direction indicated by the arrow. Since the urging force of the plunger rod urging spring 202 is set larger than the urging force of the urging force SP2 of the valve urging spring S4, the urging force of both springs urges the valve 203 in the valve opening direction at this time. Further, 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 fuel pressure P12 in the pressurized chamber. Receives force in the valve direction. 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 open 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. Rush. The valve 203 having a weight of several milligrams is quickly opened when the piston plunger 2 starts to descend by these urging forces, and strokes until it collides with the stopper ST.

  The valve seat 214S is formed outside in the diametrical direction from the cylindrical portion 203H of the valve 203 and the fuel introduction passage 10P. 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 filled with the staying fuel, and the friction force with the bearing 214B acts, so that the plunger rod 201 and the anchor 207 are slightly more 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 provided from the plunger rod 201 falls for a moment. However, since the pressure P1 of the fuel in the low pressure fuel chamber 10A acts without delay in this gap, the valve 203 is opened to reduce the valve opening force applied from the plunger rod 201 (plunger rod biasing spring 202). The fluid force in the direction is compensated. Thus, when the valve 203 is opened, the static pressure and 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 portion SG of the protruding portion ST of the valve stopper S0, and the valve 203 is not displaced in the radial direction. Stroke smoothly. The cylindrical surface portion SG forming the valve guide is formed on the upstream side and the downstream side with respect to the surface on which the valve seat 214S is arranged, and not only can sufficiently support the stroke of the valve 203 but also the inner peripheral side of the valve 203. Since the dead space can be effectively used, the axial dimension of the suction valve portion INV can be shortened.

  Further, since the valve urging spring S4 is disposed between the end surface SH of the valve stopper S0 and the bottom surface of the flat surface portion 203F of the valve 203 on the valve stopper S0 side, the valve urging spring S4 is provided between the opening 214P and the cylindrical portion 203H of the valve. The valve 203 and the valve urging spring S4 can be arranged inside the opening 214P while ensuring a sufficient passage area of the fuel introduction passage 10P formed in the above. Further, since the valve biasing spring S4 can be arranged by effectively using the dead space on the inner peripheral side of the valve 203 located inside the opening 214P that forms the fuel introduction passage 10P, the dimension in the axial direction of the intake valve INV Can be shortened.

  The valve 203 has a valve guide (SG) at its center, and has an annular protrusion 203S that contacts the receiving surface S2 of the annular surface S3 of the valve stopper S0 on the outer periphery of the valve guide (SG). Further, a valve seat 214S is formed at a position outside in the radial direction, and the annular gap SGP further extends to the outside in the radial direction, 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 on the inner peripheral 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 the occurrence of a sonic phenomenon due to the extremely high flow rate of the intake fuel during the intake operation and the occurrence of cavitation in the fuel passage S6 and the pressurized chamber. As a result, it is possible to suppress the occurrence of erosion in the fuel passage S6 and the metal edge portion in the pressurizing chamber.

  Further, since the annular protrusion 203S that contacts the receiving surface S2 of the valve stopper S0 is provided inside the annular seat SGP inside the annular seat SGP, the fluid pressure on the pressurizing chamber side is applied to the annular seat SGP during the valve closing operation described later. It is possible to increase the valve closing speed when pressing the valve 203 against the valve seat 214S by causing P4 to act quickly.

≪Fuel spill condition≫
The fuel spill state will be described with reference to FIGS. 2 and 3B. The piston plunger 2 turns from the bottom dead center position and begins to rise in the direction of the arrow Q1, but the coil 204 is in a non-energized state. The fuel is spilled (overflowed) into the low pressure fuel chamber 10A through the fuel passage 10S and the fuel introduction passage 10P. When the fuel flow in the fuel passage S6 switches from the arrow R4 direction to the R5 direction, the fuel flow 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 valve 203 and the valve stopper S0 are connected by the fluid force that presses the valve 203 toward the valve stopper S0 by the dynamic pressure of the fuel flowing into the annular fuel passage 10S of the valve seat 214S and the suction effect of the fuel flow that flows around the outer periphery of the annular gap SGP. The valve 203 is firmly pressed against the valve stopper S0 by the fluid force acting to attract.

  From the moment when the fuel flow is switched in the R5 direction, the fuel in the pressurizing chamber 12 flows into 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 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 smallest fuel flow path cross-sectional area is set in the annular fuel path 10S. For this reason, pressure loss occurs in the annular fuel passage 10S and the pressure in the pressurizing chamber 12 starts to rise. However, the fluid pressure P4 is received by the annular surface of the valve stopper S0 on the pressurizing chamber side and acts on the valve 203. Hard to do.

  In the spill state, the annular gap SGP flows from the low pressure fuel chamber 10A to the damper chamber 10B through the four fuel passage holes 214Q. On the other hand, as the piston plunger 2 moves up, the volume of the auxiliary fuel chamber 250 increases, so that the fuel flow in the downward arrow direction of the arrow R8 passing through the longitudinal passage 250B, the annular passage 21G and the fuel passage 250A causes Part of the fuel is introduced into the 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 state≫
The fuel discharge state 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 fuel spill state described above, a closed magnetic circuit CMP is generated as shown in FIG. When the closed magnetic path CMP is formed, a magnetic attractive force is generated between the opposing surfaces of the fixed core 206 and the anchor 207 in the magnetic gap GP. This 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 fixed core 205. At this time, the fuel in the storage chamber 206K of the magnetic gap GP and the plunger rod biasing spring 202 is discharged from the fuel passage 214K to the low-pressure passage through the periphery of the fuel passage 201K and the anchor 207. As a result, the anchor 207 and the plunger rod 201 are smoothly displaced toward 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 attracted to the fixed core 206 and the urging force that presses the valve 203 to the valve stopper S0 side disappears, the valve 203 is urged away from the valve stopper S0 by the urging force of the valve urging spring S4. Then, the valve 203 starts a valve closing motion. At this time, the pressure in the annular gap SGP located on the outer peripheral side of the annular protrusion 203S becomes higher than the pressure on the low pressure fuel chamber 10A side as the pressure in the pressurizing chamber 12 increases, and thus the valve 203 is closed. Help exercise. The valve 203 comes into contact with the valve seat 214S, and the valve is closed. This state is shown in FIG. 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 becomes the discharge valve. The fuel is discharged in the direction along the arrows R6 and R7 through the discharge joint 11 from the discharge passage 11A 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. Only the valve urging spring S4 has a problem that the valve closing motion is not stable because the closing force of the suction valve is too small, but this problem can be solved in the embodiment.

  At the moment when the valve 203 comes into contact with the valve seat 214S and 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 end surface of the valve 203 on the low pressure fuel chamber 10A side. The gap 201G is formed. As a result, the valve 203 is not subjected to force in the valve opening direction by the plunger rod 201 during the valve closing operation of the valve 203, so that the valve closing operation is accelerated. Further, since the valve 203 does not collide with the plunger rod 201 during the 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 rises and high pressure discharge is started, the energization to the coil 204 is cut off. The magnetic attractive 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 side by the biasing force of the plunger rod biasing spring 202. When 201 comes into contact with the bottom flat part 203F of the valve 203, the movement is stopped. Since the valve closing force due to the pressure in the pressurizing chamber 12 is already sufficiently larger than the acting force of the plunger rod urging spring 202, the valve 203 does not move even if the plunger rod 201 presses the surface of the valve 203 on the low pressure fuel chamber 10A side. It will not open. This state is a preparatory operation in which the plunger rod 201 biases the valve 203 in the valve opening direction at the moment when the piston plunger 2 turns from the top dead center in the downward direction Q2. The gap 201G is a slight gap on the order of several tens to several hundreds of microns, and the valve 203 is urged by the pressure in the pressurizing chamber 12 to make the valve 203 a rigid body. The collision sound when colliding with 203 does not become noise because its frequency is higher than the audible frequency and its energy is small.

  Hereinafter, the silent control of the first embodiment will be described in detail with reference to FIG.

  When the piston plunger 2 descends, the volume of the pressurizing chamber 12 increases and the pressure decreases, and when the pressure in the pressurizing chamber 12 becomes smaller than the pressure in the low pressure fuel chamber 10a, The valve closing force disappears, and a valve opening force due to the pressure in the low pressure fuel chamber 10a is generated. When this valve opening force becomes larger than the valve urging spring S4, the valve 203 starts the valve opening movement and collides with the valve stopper S0 to stop the valve opening movement. Even after the piston plunger 2 turns from the top dead center in the descending direction Q2, the state where the silent current is applied to the coil 204 is maintained, but the magnetic attractive force generated by the silent current is generated by the plunger rod biasing spring 202. Weaker than energizing force. Therefore, when the pressure in the pressurizing chamber 12 becomes smaller than the pressure in the low pressure fuel chamber 10 a and the valve closing force of the valve 203 due to the pressure in the pressurizing chamber 12 disappears, the anchor 207 and the plunger rod 201 are similar to the valve 203. The valve opening movement is started to the right in the figure. At this time, because of the magnetic attractive force due to the silent current, the opening movement of the anchor 207 and the plunger rod 201 is slower than the opening movement of the valve 203. Therefore, during the opening movement, the valve 203 and the plunger rod 201 are separated and independent. After the valve 203 collides with the valve stopper S0 and stops the valve opening movement, the plunger rod 201 and the valve 203 come into contact with each other, and the anchor 207 and the plunger rod 201 also stop moving. After the three members of the valve 203, the anchor 207, and the plunger rod 201 stop moving, the coil energization is completely turned off to eliminate the silent current.

  The control device of this embodiment controls an electromagnetically driven suction valve of a high-pressure fuel supply pump. The high-pressure fuel supply pump is supported by a pump housing having a pressurizing chamber and the pump housing. By reciprocating in the pressurizing chamber, fluid is sucked into the pressurizing chamber, pressurized and discharged from the pressurizing chamber. And an electromagnetically driven suction valve attached to the pump housing. The electromagnetically driven suction valve is composed of a suction valve provided at the inlet of the pressurizing chamber and an electromagnetic drive mechanism for controlling the opening / closing timing of the suction valve. The electromagnetically driven suction valve is controlled such that when the electromagnetic drive mechanism is energized, the suction valve moves to the closed position and starts to discharge fluid from the pressurizing chamber.

  Even after the piston plunger passes through the top dead center and moves toward the bottom dead center, the energized state for generating an electromagnetic force that slows down the operation of the intake valve in the valve opening direction is maintained for a certain period. .

  The energized state in a certain section is controlled so as to continue until the intake valve is fully opened.

  After energizing the electromagnetic drive mechanism, before the piston plunger passes through the top dead center and goes to the bottom dead center, the current value to the electromagnetic drive mechanism is weakened, and the piston plunger passes through the top dead center and goes down to the bottom dead center. After entering the operation toward the point, control is performed so as to shift to the energized state in a certain section.

  Control is performed so that the weakened energization current value and the current value in the energization state in a certain section are the same value. The weakened energization current value may be controlled to be larger than the current value in the energization state in a certain section and smaller than the peak current value.

  In the prior art, the urging force of the plunger rod urging spring 202 causes the valve 203, the anchor 207, and the plunger rod 201 to integrally open, and the valve 203 collides with the valve stopper S0 to open. The valve movement was stopped. For this reason, there is a problem that the sound generated at the time of a collision also increases. In this embodiment, the valve 203 collides with the valve stopper S0 and stops, and then the anchor 207 and the plunger rod 201 collide with the valve 203 and stop. By separating the collision twice, the sound generated in each collision can be reduced. Furthermore, since the valve opening force of the anchor 207 and the plunger rod 201 can be reduced by the silent current, there is an effect that the sound due to the collision can be further reduced.

  The above-described silent current is particularly effective in the idling state of a vehicle in which quietness is particularly required, and may be applied only under specific conditions such as an idling state.

  By controlling the timing of energizing the coil 204 based on a command from the engine control unit ECU, the fuel pressurized to a high pressure can be adjusted. If the energization timing is controlled so that the valve 203 is closed immediately after the piston plunger 2 starts to move upward from the bottom dead center to the top dead center, the fuel to be spilled is reduced and the fuel to be discharged at a high pressure is increased. If the energization timing is controlled so that the valve 203 is closed immediately before the piston plunger 2 starts to move downward from the top dead center to the bottom dead center, more fuel is spilled and less fuel is discharged at high pressure.

  A procedure for assembling the intake valve portion INV will be described with reference to FIGS.

  The partial cross-sectional perspective views of FIGS. 5 to 6 show a cross section cut by 90 degrees toward the central axis. A bottomed cylindrical fixed core 206 is inserted into the cylindrical space 205H at the center of the bottomed cylindrical yoke 205 from the bottomed side, and the outer periphery thereof is press-fitted and fixed to the inner peripheral surface of the cylindrical space 205H. A through hole 206H that functions as an air vent during press-fitting is formed in the bottomed portion of the fixed core 206, and a cylindrical space 206K is formed inside. The open side end portion of the fixed core 206 is positioned inside the magnetic diaphragm 205 </ b> S formed on the outer periphery of the yoke 205.

  The anchor 207 and the plunger rod 201 are fixed by press-fitting in advance. A partition 207 </ b> J is provided inside the anchor 207, and a cylindrical space 207 </ b> K and a plunger rod 201 are formed in the anchor 207 at the center of the partition 207 </ b> J to form a part of the accommodation space of the plunger biasing spring 202. Is provided with an opening 207H that communicates with the fuel passage 201K formed at the center. 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 inserted into the cylindrical space portion 207K on the side opposite to the plunger rod 201 of the anchor 207 into 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 into the cylindrical space 205H of the yoke 205 so that the half of 202 is accommodated. The end of the anchor 207 on the side opposite to the plunger rod 201 faces the end surface of the fixed core 206 with the magnetic gap GR interposed between the yoke 205 and the magnetic diaphragm 205S.

  The annular flange portion 205F of the yoke 205 is provided with a peripheral surface 205Y that is press-fitted into the open end side inner peripheral surface of the side yoke 204Y shown in FIG. 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 match the radial width of the coil 204. A stepped portion 205K having a joining end surface 205J (smaller diameter than the annular flange portion 205F) that contacts 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 cylindrical projection 205N having a small diameter protruding from the center is provided. The cylindrical protrusion 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 joining end surface 205J contacts the mounting surface of the pump housing 1. Inserted.

  The intake valve portion INV is formed in advance by assembling the valve housing 214, the valve 203, the valve urging 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 valve 203 annular surface portion 203R 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-fitting surface portions SP1-SP3 of the valve stopper S0 are press-fitted into the annular stepped portion 214D of the valve housing. Together, this constitutes the intake valve portion INV.

  The outer periphery of the bearing portion 214B of the valve housing 214 is press-fitted into the inner periphery of the cylindrical protrusion 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 portion INV and the electromagnetic drive mechanism portion EMD are assembled together. In this state, the end of the plunger rod 201 on the side opposite to the anchor 207 is inserted into the bearing hole 214H at the center of the bearing 214B, and is supported so as to be able to reciprocate.

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

[Second Embodiment]
FIG. 9 shows a second embodiment. The configuration of the high-pressure fuel supply pump is the same as that of the first embodiment. In the first embodiment, the current was a two-stage current of a peak current and a silent current. In the second embodiment, the three-stage current is a peak current, a holding current, and a silent current.

  The set value of the peak current is the same as in the first embodiment. That is, the peak current is set so that the magnetic attractive force generated between the opposing surfaces of the fixed core 206 and the anchor 207 in the magnetic gap GL is larger than the biasing force of the plunger rod biasing spring 202, and the anchor 207 is fixed. After contacting the core 206 and stopping the valve closing motion, the current is switched to the holding current. The holding current is set so that the magnetic holding force generated when the fixed core 206 and the anchor 207 are in contact with each other is larger than the biasing force of the plunger rod biasing spring 202, but the holding current is smaller than the peak current. It can be set. This is because the magnetic gap GL does not exist at the time of holding current, so that a magnetic holding force larger than the biasing force of the plunger rod biasing spring 202 can be obtained with a smaller current. Then, when the pressure in the pressurizing chamber 12 rises and high-pressure pumping is started, the current is switched to the silent current. The silent current is even smaller than the holding current. By controlling as described above, the amount of heat generated in the coil can be further reduced, so that a problem such as burning of the coil can be eliminated.

  The embodiments of this example are listed as follows.

Embodiment 1
A pump housing with a pressure chamber,
A piston plunger that is supported by the pump housing and sucks fluid into the pressurizing chamber by repeating reciprocating operation in the pressurizing chamber, pressurizes and discharges the fluid from the pressurizing chamber, and is attached to the pump housing Equipped with an electromagnetically driven suction valve,
The electromagnetically driven suction valve is composed of a suction valve provided at the inlet of the pressurizing chamber and an electromagnetic drive mechanism that controls the opening and closing timing of the suction valve;
The suction valve is a valve disposed on the pressure chamber side with respect to a valve seat provided in a valve housing; and
In what comprises a valve biasing spring that biases the valve toward the valve seat,
The valve includes an annular contact surface that contacts the valve seat and blocks the fuel intake passage, and a bottomed cylindrical portion provided on the inner peripheral side of the annular contact surface,
The bottomed cylindrical portion is inserted into a fuel introduction hole formed in the valve housing inside the valve seat, and an outer surface of an end portion of the bottomed cylindrical portion is a low-pressure fuel upstream of the fuel introduction hole. A high-pressure fuel supply pump equipped with an electromagnetically driven suction valve exposed to the fuel in the chamber.

Embodiment 2
In what is described in Embodiment 1,
The electromagnetic drive mechanism includes a plunger rod that is electromagnetically controlled to reciprocate,
A high-pressure fuel supply pump comprising an electromagnetically driven suction valve that has a tip of the plunger rod in contact with an outer surface of an end of the bottomed cylindrical portion of the valve protruding into the low-pressure fuel chamber.

Embodiment 3
In the embodiment described in Embodiment 1,
The electromagnetic drive mechanism includes a plunger rod that is electromagnetically controlled to reciprocate,
A high-pressure fuel supply pump comprising an electromagnetically driven suction valve in which the plunger rod and the valve are integrally formed.

Embodiment 4
In any one of Embodiments 2 and 3,
The electromagnetic drive mechanism is a high-pressure fuel supply pump including an electromagnetically driven suction valve having a plunger rod biasing spring that biases the plunger rod toward the valve.

Embodiment 5
In the embodiment described in Embodiment 1,
The valve is a high-pressure fuel supply pump provided with an electromagnetically driven intake valve disposed between the valve seat and a valve stopper provided on the pressure chamber side of the valve seat.

Embodiment 6
In what is described in Embodiment 5,
The valve stopper has a protruding portion with a cylindrical surface protruding toward the bottomed cylindrical portion of the valve at the center, and the cylindrical surface functions as a guide portion for guiding the stroke of the valve in the axial direction. High-pressure fuel supply pump equipped with an electromagnetically driven suction valve.

Embodiment 7
In what is described in Embodiment 6,
A high-pressure fuel supply pump including an electromagnetically driven intake valve including a valve biasing spring that biases the valve in a valve closing direction between the valve and the valve stopper.

Embodiment 8
In what is described in Embodiment 7,
A high pressure fuel supply pump comprising an electromagnetically driven intake valve in which the valve biasing spring is held between a valve side end surface of the protruding portion of the valve stopper and a bottom surface of the bottomed cylindrical portion of the valve.

Embodiment 9
In what is described in Embodiment 7,
The protruding portion of the valve stopper is formed of a bottomed cylindrical portion having an opening on the valve side,
High-pressure fuel supply in which the valve biasing spring includes an electromagnetically driven intake valve disposed between the valve and the valve stopper inside the bottomed cylindrical portion of the protruding portion of the valve stopper pump.

Embodiment 10
In the device according to Embodiment 5,
The valve stopper includes press-fitting surface portions formed at a plurality of positions on the outer peripheral surface of the valve stopper at a specific interval, and extends in the circumferential direction between one of the press-fitting surface portions and another press-fitting surface portion adjacent thereto. With notches,
A plurality of press-fitting surface portions of the valve stopper are press-fitted to a cylindrical inner peripheral surface of the valve housing formed on the valve seat downstream side of the valve housing;
A plurality of valve seats extending in a circumferential direction between the peripheral surface of the valve stopper and the inner peripheral surface of the valve housing between the one press-fit fitting portion and the other press-fit fitting portion adjacent thereto. A high-pressure fuel supply pump having an electromagnetically driven intake valve in which a downstream fuel passage is formed.

Embodiment 11
In the device according to Embodiment 5,
A high-pressure fuel supply pump provided with an electromagnetically driven suction valve in which a contact surface and a gap are formed between the valve stopper and the valve so as to contact each other when the valve moves to a fully open position.

Embodiment 12
In what is described in Embodiment 11
The contact surface is formed in an annular shape inside the valve seat,
A high pressure fuel supply pump comprising an electromagnetically driven suction valve in which a gap between the valve stopper and the valve is formed in an annular shape outside the annular contact surface.

Embodiment 13
In what is described in Embodiment 10
The high-pressure fuel supply pump including an electromagnetically driven intake valve in which the plurality of fuel passages on the downstream side of the valve seat are formed in an outer peripheral portion of the annular gap.

Embodiment 14
In the embodiment described in Embodiment 1,
The electromagnetically driven suction valve is inserted into a through hole penetrating from the side surface of the pump housing into the pressurizing chamber, and the inside is sealed by welding at the side surface contact surface side of the pump housing of the through hole. A high-pressure fuel supply pump comprising an electromagnetically driven suction valve that seals the pressurizing chamber and the low-pressure fuel chamber by press-fitting the peripheral surface of the valve housing into the inner peripheral surface of the through hole of the pump housing.

Embodiment 15
The thing of Claim 14 WHEREIN:
High-pressure fuel having an electromagnetically driven intake valve in which the through hole has the same diameter from the inlet to the pressurizing chamber side end, and the end of the through hole forms the fuel inlet opening of the pressurizing chamber having the same diameter Supply pump.

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 Pressure 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 Part 214 Valve Housing 214S Valve Seat 214P Opening 250 Fuel Subchamber 600 Engine Control Unit (ECU)
EMD Electromagnetic drive mechanism INV Suction valve part S0 Valve stopper SG Cylindrical surface part (valve guide)

Claims (12)

A pump housing with a pressure chamber,
A piston plunger which is supported by the pump housing and sucks fluid into the pressurizing chamber by repeating reciprocating motion in the pressurizing chamber, pressurizes and discharges the fluid from the pressurizing chamber;
Comprising an electromagnetically driven suction valve attached to the pump housing;
The electromagnetically driven intake valve is an electromagnetically driven intake valve of a high-pressure fuel supply pump that includes an intake valve provided at the inlet of the pressurizing chamber and an electromagnetic drive mechanism that controls the opening and closing timing of the intake valve. A controller for energizing the electromagnetic drive mechanism to start discharging the fluid from the pressurizing chamber,
The intake valve has an anchor and a plunger rod, and a valve separate from the plunger rod,
An electromagnetically driven type of high pressure fuel supply pump that maintains a silent current state for generating an electromagnetic force that slows down the operation of the intake valve in the valve opening direction, before and after the piston plunger passes through the top dead center. Inlet valve control device. In the control apparatus of the solenoid valve of the high-pressure fuel supply pump according to claim 1,
A control device for an electromagnetically driven intake valve of a high pressure fuel supply pump that controls the silent current state of the predetermined section to continue until the intake valve is fully opened. In the control apparatus of the solenoid valve of the high-pressure fuel supply pump according to claim 1,
After energizing the electromagnetic drive mechanism, before the piston plunger passes through the top dead center and moves toward the bottom dead center, the energization current value to the electromagnetic drive mechanism is weakened and the piston plunger passes through the top dead center. Then, after entering the operation toward the bottom dead center, the control device for the electromagnetically driven intake valve of the high-pressure fuel supply pump that controls to shift to the silent current state of the predetermined section. In the control apparatus of the solenoid valve of the high pressure fuel supply pump according to claim 3,
A control device for an electromagnetically driven intake valve of a high-pressure fuel supply pump that controls the weakened energization current value and the current value in the silent current state of the constant section to be the same value. In the control apparatus of the solenoid valve of the high pressure fuel supply pump according to claim 3,
A control device for an electromagnetically driven intake valve of a high-pressure fuel supply pump, wherein the weakened energization current value is controlled to be larger than a current value in a silent current state of the certain section and smaller than a peak current value. A pump housing with a pressure chamber,
A piston plunger which is supported by the pump housing and sucks fluid into the pressurizing chamber by repeating reciprocating motion in the pressurizing chamber, pressurizes and discharges the fluid from the pressurizing chamber;
Comprising an electromagnetically driven suction valve attached to the pump housing;
The intake valve has an anchor and a plunger rod, and a valve separate from the plunger rod,
The electromagnetically driven suction valve is composed of a suction valve provided at the inlet of the pressurizing chamber and an electromagnetic drive mechanism that controls the opening and closing timing of the suction valve.
In order to close the suction valve, the electromagnetic drive mechanism is energized to start discharging the fluid from the pressurizing chamber. Even after the discharge is completed, the suction valve is opened during the silent control period of the suction valve. A high-pressure fuel supply pump characterized by maintaining a silent current state for generating an electromagnetic force that slows the operation in a valve direction . What is described in claim 6,
A high-pressure fuel supply pump characterized in that a current supplied to the electromagnetic drive mechanism has a plurality of stages. What is described in claim 7,
A high-pressure fuel supply pump characterized in that the value of the first stage is larger than the value of the last stage. What is described in claim 8,
The high-pressure fuel supply pump according to claim 1, wherein the switching timing to the final stage is before the discharge of the fluid from the pressurization ends. In any of claims 7 or 8,
The high-pressure fuel supply pump is characterized in that the current supplied to the electromagnetic drive mechanism has two stages. What is described in claim 6,
A high-pressure fuel supply pump having a stopper with which the suction valve abuts at the end of the silent control section. What is described in claim 6,
The suction valve is biased to a valve open position by a spring, and the electromagnetic drive mechanism is a high-pressure fuel supply pump that generates a biasing force against the spring.