JP2016191367A - High pressure fuel supply pump and process of assembling high pressure fuel supply pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent assembling characteristic of a valve stopper of a high pressure fuel supply pump from being deteriorated and prevent a size of suction valve from being increased.SOLUTION: This invention relates to a high pressure fuel supply pump comprising a pump housing 1, a plunger 2 and a solenoid suction valve 300 in which the solenoid valve 300 includes a valve 301c, a valve seat 302a where a fuel passage is opened or closed by moving the valve 301c toward it or away from it, and a valve stopper 313 to which the valve 301c abuts when the valve is opened, the solenoid suction valve 300 is fixed to a solenoid suction valve insertion hole 1k formed at the pump housing 1, and the solenoid suction valve 300 is controlled to control an amount of discharged fuel, and the solenoid suction valve insertion hole 1k is provided with a bottom part 1ka abutted against the valve stopper 313 and a fuel passage hole 1a passing through the bottom part 1ka to communicate both sides of the bottom part 1ka.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a high-pressure fuel supply pump that pumps fuel to a fuel injection valve of an internal combustion engine, and more particularly, to a high-pressure fuel pump that includes an electromagnetic suction valve that adjusts the amount of fuel to be discharged.

  High-pressure fuel supply pumps are widely used in direct injection types in which fuel is directly injected into the combustion chamber of an internal combustion engine such as an automobile. The high-pressure fuel supply pump increases the pressure of the fuel and discharges a desired amount of fuel. In order to adjust the amount of fuel to be discharged, the high-pressure fuel supply pump includes an electromagnetic suction valve.

  Japanese Patent Laying-Open No. 2014-136966 (Patent Document 1) describes a high-pressure fuel supply pump provided with an electromagnetic intake valve (electromagnetically driven intake valve mechanism). The electromagnetic intake valve includes an intake valve portion and an electromagnetic drive mechanism portion. A cylindrical hole is formed in the pump housing from its peripheral wall toward the pressurizing chamber. In the electromagnetic intake valve, the entire intake valve portion and a part of the electromagnetic drive mechanism are inserted into a cylindrical hole formed in the pump housing and attached to the pump housing (paragraph 0014).

  The intake valve portion includes a valve housing, a valve, a valve biasing spring, and a valve stopper. In the valve housing, an annular stepped portion is formed in the opening, and a valve seat is formed on the back side of the annular stepped portion. The press stopper surface of the valve stopper is press-fitted into an annular stepped portion of the valve housing. The valve is provided between the valve seat and the valve stopper so as to be displaceable in the radial valve closing direction (paragraph 0017).

JP 2014-136966 A

  In the high-pressure fuel supply pump of Patent Document 1, a valve stopper that regulates the valve opening amount is inserted into the valve housing from an opening provided on the pressurizing chamber side of the valve housing, and the valve housing has an annular step. It is press-fitted and fixed to the part. A cylindrical hole into which the electromagnetic suction valve is inserted and fixed opens in the pressurizing chamber. The valve stopper is exposed to the pressurizing chamber without the end on the pressurizing chamber side being supported by the valve housing.

  For this reason, when the valve repeatedly collides with the valve stopper, the valve stopper may be displaced in the direction opposite to the press-fitting direction. If the valve stopper is displaced, the stroke of the valve may change, and fuel flow control may not be possible. In order to prevent the valve stroke from changing, it is necessary to increase the press-fit holding force of the valve stopper with respect to the valve housing. However, when the press-fitting holding force is increased, there is a concern that the assembling property such as poor press-fitting is deteriorated. Further, the intake valve portion that constitutes the valve stopper is increased in size.

  An object of the present invention is to prevent deterioration in assembling performance of a valve stopper and prevent an intake valve portion from becoming large in a high-pressure fuel supply pump.

  In order to solve the above problems, a high pressure fuel supply pump according to the present invention has a configuration in which an electromagnetic suction valve is inserted and attached to an electromagnetic suction valve insertion hole formed in a pump housing. A support portion is provided that contacts the valve stopper and supports the valve stopper from the pressurizing chamber side.

  In the method of assembling the high-pressure fuel supply pump, a first assembly is produced in which the valve housing containing the valve and the valve stopper are press-fitted and fixed so that the end of the valve stopper protrudes from the end of the valve housing. When the first assembly is press-fitted into the electromagnetic suction valve insertion hole, the end of the valve stopper is brought into contact with the bottom of the electromagnetic suction valve insertion hole, and the end of the valve stopper is brought into contact with the bottom of the electromagnetic suction valve insertion hole. From the contact state, the first assembly is further pushed into the electromagnetic suction valve insertion hole and fixed.

  According to the present invention, since the valve stopper is supported by the support portion from the pressurizing chamber side, there is no need to increase the press-fit holding force. Therefore, it is possible to prevent the assembly of the valve stopper from being deteriorated and to prevent the intake valve portion from becoming large.

  Problems, configurations, and effects other than those described above will be clarified by the following description of embodiments.

1 is a system diagram showing an outline of an embodiment of a fuel supply system including a high-pressure fuel supply pump according to the present invention. It is a longitudinal cross-sectional view which concerns on one Example of the high pressure fuel supply pump of this invention. It is another longitudinal cross-sectional view which concerns on one Example of the high pressure fuel supply pump of this invention. FIG. 3 is an enlarged longitudinal sectional view of an electromagnetic suction valve of the high-pressure fuel supply pump of the present invention, showing a state where the electromagnetic suction valve is in an open state. It is VV sectional drawing of FIG. It is a disassembled perspective view which shows the assembly state of an electromagnetic suction valve, and the assembly | attachment state to a pump main body. It is a top view which shows a valve stopper fixing member.

  An embodiment according to the present invention will be described below with reference to the drawings.

  A fuel supply system including a high-pressure fuel supply pump according to the present invention will be described with reference to FIG. FIG. 1 is a system diagram showing an outline of an embodiment of a fuel supply system including a high-pressure fuel supply pump according to the present invention.

  A portion 100 surrounded by a broken line indicates a high-pressure fuel supply pump (hereinafter referred to as a high-pressure pump). The mechanisms and components shown in the broken line are integrated into the high-pressure pump 100.

  The fuel in the fuel tank 20 is pumped up by the feed pump 21 based on a signal 21DS from an engine control unit 27 (hereinafter referred to as ECU). The fuel pumped up by the feed pump 21 is pressurized to an appropriate feed pressure and sent to the low-pressure fuel inlet 10 a of the high-pressure pump 100 through the suction pipe 28.

  The fuel that has passed through the suction joint 10a passes through the pressure pulsation reducing mechanism 9 and the suction passage 10d, and reaches the suction port 31b of the electromagnetic suction valve 300 that constitutes the variable capacity mechanism.

  The fuel flowing into the electromagnetic suction valve 300 passes through the suction valve (suction valve) 301 c and flows into the pressurizing chamber 11. The plunger 2 is given reciprocating power by a cam mechanism 93 (see FIG. 2) of the engine. Due to the reciprocating motion of the plunger 2, fuel is sucked into the pressurizing chamber 11 from the suction valve 301 c in the downward stroke of the plunger 2. In the upward stroke of the plunger 2, the fuel is pressurized and discharged from the discharge valve 8. The discharged fuel is pumped to the common rail 23. The fuel in the common rail 23 is injected into the combustion chamber of the engine by an injector 24 that is driven based on a signal 24DS from the ECU 27. A pressure sensor 26 is attached to the common rail 23, and the fuel pressure in the common rail 23 detected by the pressure sensor 26 is sent to the ECU 27 as a detection signal 26DS. The ECU 27 generates a drive signal 300DS for the electromagnetic suction valve 300 provided in the high-pressure pump 100 based on the fuel pressure in the common rail 23.

  In the high-pressure pump 100, the electromagnetic suction valve 300 is controlled by a drive signal 300DS from the ECU 27, and the discharged fuel flow rate is adjusted.

  The overall configuration of the high-pressure pump 100 will be described with reference to FIGS. 2 and 3.

  FIG. 2 is a longitudinal sectional view according to an embodiment of the high-pressure fuel supply pump of the present invention. FIG. 3 is another longitudinal sectional view according to an embodiment of the high-pressure fuel supply pump of the present invention.

  The high-pressure pump 100 is fixed with a plurality of bolts 91 such that a flange 1e provided on a pump body (pump housing) 1 is brought into close contact with a plane of a cylinder head 90 of the internal combustion engine. The mounting flange 1e is welded and joined to the pump body 1 at the welded portion 1f to form an annular fixed portion. In this embodiment, laser welding is used for welding the mounting flange 1e and the pump body 1.

  An O-ring 61 is fitted in the annular groove 1 g of the pump body 1 for sealing between the cylinder head 90 and the pump body 1. The seal formed by the O-ring 61 prevents engine oil from leaking from between the cylinder head 90 and the pump body 1 to the outside.

  The pump body 1 is formed with a through hole 1 h that penetrates the plunger 2 in the axial direction. The through hole 1h constitutes an insertion hole into which the cylinder 6 is inserted and attached. The cylinder 6 guides the reciprocating motion of the plunger 2 and forms a pressurizing chamber 11 therein. The cylinder 6 is formed in a bottomed cylindrical shape with one end closed so as to form the pressurizing chamber 11.

  Further, an annular groove 6 a is provided on the outer peripheral surface of the cylinder 6. The annular groove 6a and the pressurizing chamber 11 are communicated with each other through a plurality of communication holes 6b. The pressurizing chamber 11 communicates with the electromagnetic suction valve 300 and the discharge valve mechanism 8 through the annular groove 6a and the communication hole 6b.

  The cylinder 6 is press-fitted and fixed to the inner peripheral surface of the cylinder insertion hole 1h of the pump body 1 at its outer diameter. The cylinder surface 6e of the press-fitting part of the cylinder 6 is sealed so that fuel pressurized from the gap with the pump body 1 does not leak to the low pressure side. Further, the cylinder 6 has a small diameter portion 6c with a small outer diameter at the end on the pressurizing chamber 11 side, and a stepped surface 6f is formed. In the cylinder insertion hole 1h of the pump body 1, an end 1i on the side communicating with the low pressure fuel chamber 10c side is formed with a small diameter, and a stepped surface 1j is formed. When the fuel in the pressurizing chamber 11 is pressurized, the cylinder 6 receives a force toward the low-pressure fuel chamber 10c. Under this force, the stepped surface 6f of the cylinder 6 comes into contact with the stepped surface 1j of the cylinder insertion hole 1h. The stepped surface 6f and the stepped surface 1j prevent the cylinder 6 from coming out to the low pressure fuel chamber 10c side.

  The pump body 1 and the cylinder 6 constitute a seal that prevents fuel leakage by bringing the stepped surface 6f and the stepped surface 1j into contact with each other in the axial direction. In this embodiment, in addition to the seal at the press-fitting portion between the pump body 1 and the cylinder 6, a seal is provided by the stepped surface 6f and the stepped surface 1j, and the seal is configured in a double manner.

  In this embodiment, the pump body (pump body) 1 and the cylinder 6 are formed as separate members. However, the cylinder 6 is a member that forms the pump body 1 and may be formed integrally with the pump body 1. good.

  At the lower end of the plunger 2 is provided a tappet 92 that converts the rotational motion of the cam 93 attached to the camshaft of the internal combustion engine into vertical motion and transmits it to the plunger 2. The plunger 2 is pressure-bonded to the tappet 92 by the spring 4 through the retainer 15. Thereby, the plunger 2 can be reciprocated up and down with the rotational movement of the cam 93.

  A plunger seal 13 held at the lower end of the inner periphery of the seal holder 7 is installed in a slidable contact with the outer periphery of the plunger 2 at the lower part of the cylinder 6 in the figure. The plunger seal 13 seals the fuel in the sub chamber 7a when the plunger 2 slides and prevents the fuel from flowing into the internal combustion engine. At the same time, lubricating oil (including engine oil) for lubricating the sliding portion in the internal combustion engine is prevented from flowing into the pump body 1.

  A suction joint 51 is attached to the pump body 1. The suction joint 51 is connected to a low-pressure pipe that supplies fuel from the fuel tank 20 of the vehicle, and the fuel is supplied from here to the inside of the high-pressure pump 100. The suction filter 52 in the suction joint 51 serves to prevent foreign matter existing between the fuel tank 20 and the low-pressure fuel inlet 10a from being absorbed into the high-pressure fuel supply pump 100 by the flow of fuel.

  The fuel that has passed through the low pressure fuel suction port 10a reaches the suction port 31b of the electromagnetic suction valve 300 through the pressure pulsation reducing mechanism 9 and the low pressure fuel flow path 10d.

  A discharge valve mechanism 8 is provided at the outlet of the pressurizing chamber 11. The discharge valve mechanism 8 includes a discharge valve sheet member 8a, a discharge valve 8b that contacts and separates from the discharge valve sheet member 8a, a discharge valve spring 8c that biases the discharge valve 8b toward the discharge valve sheet member 8a, a discharge valve 8b, and a discharge valve. It is comprised from the discharge valve holder 8d which accommodates the sheet | seat 8a. The discharge valve seat 8a and the discharge valve holder 8d are joined by welding at the contact portion 8e to form an integral discharge valve mechanism 8.

  A stepped portion 8f that forms a stopper that restricts the stroke of the discharge valve 8b is provided inside the discharge valve holder 8d.

  In a state where there is no fuel differential pressure in the pressurizing chamber 11 and the fuel discharge port 12, the discharge valve 8b is pressed against the discharge valve seat 8a by the urging force of the discharge valve spring 8c and is closed. Only when the fuel pressure in the pressurizing chamber 11 becomes higher than the fuel pressure in the fuel discharge port 12, the discharge valve 8 b opens against the discharge valve spring 8 c, and the fuel in the pressurization chamber 11 is discharged from the fuel discharge port. 12 is discharged to the common rail 23 through a high pressure. When the discharge valve 8b is opened, it comes into contact with the discharge valve stopper 8f, and the stroke is limited. Accordingly, the stroke of the discharge valve 8b is appropriately determined by the discharge valve stopper 8d. As a result, the stroke is too large, and the fuel discharged at high pressure to the fuel discharge port 12 due to the delay in closing the discharge valve 8b can be prevented from flowing back into the pressurizing chamber 11, and the efficiency of the high pressure pump is reduced. Can be suppressed. In addition, when the discharge valve 8b repeats opening and closing movements, the discharge valve 8b is guided on the inner peripheral surface of the discharge valve holder 8d so as to move only in the stroke direction. By doing so, the discharge valve mechanism 8 becomes a check valve that restricts the flow direction of fuel.

  As described above, the pressurizing chamber 11 includes the pump housing 1, the electromagnetic suction valve 300, the plunger 2, the cylinder 6, and the discharge valve mechanism 8.

  Next, the electromagnetic suction valve 300 will be described in detail with reference to FIGS. 4 and 5. FIG. 4 is an enlarged longitudinal sectional view of the electromagnetic intake valve of the high-pressure fuel supply pump of the present invention, and shows a state where the electromagnetic intake valve is in an open state. 5 is a cross-sectional view taken along the line VV in FIG.

  The electromagnetic intake valve 300 is configured by an electromagnetically driven intake valve mechanism, and includes an electromagnetically driven mechanism portion 300A and an intake valve portion 300B. A cylindrical hole 1k is formed in the pump housing 1 from the peripheral wall toward the pressurizing chamber 11. The electromagnetic intake valve 300 is attached to the pump housing 1 by inserting the entire intake valve portion 300B and a part of the electromagnetic drive mechanism 300A into the cylindrical electromagnetic intake valve insertion hole 1k.

  The electromagnetic drive mechanism 300A includes a mover 301 that is electromagnetically driven. The mover 301 includes a plunger rod 301a and an anchor 301b. A valve 301 c is provided at the tip of the plunger rod 301 a and faces a valve seat 302 a formed in a valve housing 302 provided at the end of the electromagnetic suction valve 300. The plunger rod 301a and the valve 301c are configured separately, and the tip end surface 301aa of the plunger rod 301a and the end surface 301ca of the valve 301c are configured to be able to contact and separate. Although the plunger rod 301 a and the valve 301 c are configured separately, the valve 301 c may be regarded as a part of the mover 301.

  The electromagnetic drive mechanism section 300A includes a yoke 305 formed of a stepped cylindrical member that also serves as the body of the electromagnetic drive mechanism section 300A on the inner peripheral side of the annularly formed coil 304. A fixed core 306 and an anchor 301b are provided on the inner periphery of the yoke 305. A plunger rod biasing spring (mover biasing spring) 307 is provided between the fixed core 306 and the plunger rod 301a. The fixed core 306 is fixed to the small diameter portion 305a side of the yoke 305 by welding. A plunger rod biasing spring (movable element biasing spring) 307 is a spring that biases the movable element 301 in the valve opening direction.

  The fixed core 306 is formed with a non-through hole 306c from the end surface 306a toward the opposite end surface 306b. A bottom portion 306ca of the hole 306c constitutes a seating portion (spring seat) of the plunger rod biasing spring 307. The end surface 306a faces the end surface 301ba of the anchor 301b. The end surface 306a and the end surface 301ba constitute a magnetic attractive surface S on which a magnetic attractive force acts. When the valve 301c is in the opened state as shown in FIG. 4, the end surface 306a and the end surface 301ba face each other via the magnetic gap GP1.

  The anchor 301b is formed with a through hole 301bb that penetrates the central portion thereof in the axial direction of the plunger rod 301a. The plunger rod 301a is inserted into the through hole 301bb and assembled to the anchor 301b. An enlarged diameter portion 301ab is formed at the end of the plunger rod 301a on the fixed core 306 side, and the end surface of the enlarged diameter portion 301ab on the fixed core 306 side constitutes a spring seat with which the plunger rod biasing spring 307 abuts. . As a result, the plunger rod 301a is biased toward the valve 301c by the plunger rod biasing spring 307.

  A guide member 311 is press-fitted to the end of the yoke 305 on the large diameter portion 305b side, and the yoke 305 and the guide member 311 are fixed. The guide member 311 is provided with a guide portion 311b that guides the reciprocating motion of the plunger rod 301a. The guide portion 311b is configured by a plunger rod insertion hole through which the plunger rod 301a is inserted. The guide member 311 is provided with a flange portion 311a. The flange portion 311a has a through hole 311b through which fuel enters and exits the chamber in which the anchor 301b is accommodated. Further, the flange portion 311 a constitutes a spring seat of the anchor biasing spring 312.

  The anchor 301b is biased by an anchor biasing spring 312 in a direction in which the valve 301c is opened. The urging force by the anchor urging spring 312 is weaker than the urging force by the plunger rod urging spring 307, and the anchor 301b is stopped at a position where it engages with the enlarged diameter portion 301ab of the plunger rod 301a. When the anchor 301b is attracted in the valve closing direction and contacts the fixed core 306, and when the magnetic attraction force to the anchor 301b is released and the valve 301c contacts the valve stopper 313, the plunger rod 301a and the anchor 301b are It is configured to allow relative displacement. The enlarged diameter portion 301ab of the plunger rod 301a functions as a restricting portion that restricts the movable range of the anchor 301b in the valve closing direction.

  The coil 304 is wound around the bobbin 318 and assembled to the outer peripheral side of the fixed core 306 and the anchor 301b. The coil 304 is covered with a side yoke 308 at an end and a side on the pressurizing chamber 11 side, and is covered with a back yoke 309 at an end opposite to the pressurizing chamber 11 side. The side yoke 308 is press-fitted to the outer peripheral side of the intermediate portion between the small diameter portion 305a and the large diameter portion 305b of the yoke 305, and the side yoke 308 and the yoke 305 are fixed. The back yoke 309 is press-fitted to the inner peripheral side of the side yoke 308, and the back yoke 309 and the side yoke 308 are fixed. A closed magnetic path 310 including a magnetic gap GP1 is formed around the coil 304 by the yoke 305, the side yoke 308, the back yoke 309, the fixed core 306, and the anchor 301b.

  The coil 304 is connected to a terminal (connector pin) 320 of the connector 319. Two terminals 320 are provided and are connected to both ends of the coil 304. The connector 319 is a connection part for electrically connecting with external apparatuses, such as ECU27, for example.

  A portion of the yoke 305 facing the periphery of the magnetic gap GP1 is provided with a magnetic diaphragm (not shown) formed by reducing the thickness or demagnetizing it. The magnetic aperture reduces the magnetic flux that leaks through the yoke 305.

  A suction valve portion 300B is provided at the end of the electromagnetic suction valve 300 on the pressurizing chamber 11 side. The intake valve portion 300B includes a valve housing 302, a valve 301c, a valve stopper 313, a valve stopper fixing member 314, and a valve biasing spring 315.

  The valve housing 302 is press-fitted and fixed to the electromagnetic suction valve insertion hole 1 k of the pump housing 1. A valve seat 302a is formed toward the pressurizing chamber 11 at an intermediate portion of the valve housing 302 in the axial direction of the plunger rod 301a. The valve seat 302 a is formed in an annular shape on the inner peripheral side of the valve housing 302. A through hole 302b through which the plunger rod 301a is inserted is formed on the inner peripheral side of the valve seat 302a.

  A valve stopper 313 is fixed to the end of the valve housing 302 on the pressurizing chamber 11 side by a valve stopper fixing member 314. One end of the valve stopper 313 is closed by a bottom 313a, and a contact portion 313b with the valve 301c is provided at the other end. A concave portion 313 c is formed at the center of the valve stopper 313, and the concave portion 313 c constitutes a housing portion for the valve biasing spring 315.

  One end of the valve urging spring 315 is in contact with the bottom 313a of the valve stopper 313, and the other end is in contact with a surface 301cb of the valve 301c opposite to the surface 301ca facing the valve seat 302a. The valve urging spring 315 is disposed between the valve 301c and the valve stopper 313, and urges the valve 301c in the valve closing direction. The resultant force of the urging force of the anchor urging spring 312 and the urging force of the valve urging spring 315 is smaller than the urging force of the plunger rod urging spring 307. For this reason, in a state where only the urging force of the anchor urging spring 312, the valve urging spring 315 and the plunger rod urging spring 307 is acting on the valve 301 c, the valve 301 c maintains the valve open state.

  The valve 301c is closed when the end surface 301ca comes into contact with the valve seat 302a. When the valve 301c is opened, the end surface 301cb comes into contact with a contact portion 313b formed on the valve stopper 313. That is, the distance (gap) GP2 between the valve seat 302a and the contact portion 313b of the valve stopper 313 is a stroke for moving the valve 301c when the valve is opened and closed.

  The valve 301c has a protruding portion 301cc formed on the end surface 301cb side, and the protruding portion 301cc is fitted in the central portion of the valve biasing spring 315. Thereby, the relative position of the valve 301c and the valve biasing spring 315 in the radial direction is determined. Further, in a state where the valve 301c is stationary in the valve open state or the valve closed state, the distal end portion 301aa of the plunger rod 301a and the end surface 301ca of the valve 301c are in contact with each other.

  A gap is provided between the outer periphery of the valve 301c and the valve stopper 313 and the inner peripheral surface of the valve housing 302, and a fuel passage 316 is formed by this gap. The valve stopper fixing member 314 is provided with a notch 314a in the circumferential direction, and a fuel passage 317 is formed by the notch 314a.

  The electromagnetic suction valve insertion hole 1k does not penetrate the valve housing 1 toward the pressurizing chamber 11 and the cylinder 6, and has a bottom 1ka. A communication hole 1 a is formed in the bottom 1 ka to communicate the electromagnetic suction valve insertion hole 1 k and an annular groove 6 a formed on the outer periphery of the cylinder 6.

  In the valve 301c, an end surface 313aa formed on the bottom portion 313a is in contact with a bottom portion (bottom surface) 1ka of the electromagnetic suction valve insertion hole 1k.

  The fuel passage 316, the fuel passage 317, and the communication hole 1a constitute a fuel passage that communicates from the valve seat 302a to the annular groove 6a formed on the outer peripheral surface of the cylinder 6.

  Next, the operation of the high pressure pump 100 will be described. Although there are cases in which the vertical direction is designated for explanation, the vertical direction is defined based on FIGS. This vertical direction has nothing to do with the vertical direction when the high-pressure pump 100 is mounted.

  When the plunger 2 moves in the direction of the cam 93 due to the rotation of the cam 93 and is in the suction stroke state, the volume of the pressurizing chamber 11 increases and the fuel pressure in the pressurizing chamber 11 decreases. In this process, when the fuel pressure in the pressurizing chamber 11 becomes lower than the pressure in the suction passage 10d, the valve (suction valve) 301c is in an open state, so that the pump passes through the gap GP2 between the valve 301c and the valve seat 302a. It passes through a communication hole (fuel passage) 1 a provided in the main body 1, a cylinder outer peripheral passage (annular groove) 6 a and a communication hole (fuel passage) 6 b provided in the cylinder 6 and flows into the pressurizing chamber 11. A plurality of communication holes 1 a are formed around an extension line of the central axis of the electromagnetic suction valve 300.

  After the plunger 2 completes the suction stroke, the plunger 2 starts to move upward from the bottom dead center and moves to the compression stroke. Here, the electromagnetic coil 304 remains in a non-energized state, and no magnetic biasing force acts on the plunger rod 301a. The plunger rod biasing spring 307 is set to have a biasing force necessary and sufficient to keep the valve 301c open in a non-energized state. The volume of the pressurizing chamber 11 decreases as the plunger 2 compresses. In this state, the fuel once sucked into the pressurizing chamber 11 passes through the gap GP2 between the valve 301c and the valve seat 302a in the valve-opened state. It is returned to the suction passage 10d. For this reason, in this state, the pressure in the pressurizing chamber does not increase. This process is called a return process.

  In this state, when a control signal from the engine control unit 27 is applied to the electromagnetic suction valve 300, a current flows through the electromagnetic coil 43 via the terminal 320, and a magnetic attractive force is generated between the fixed core 306 and the anchor 301b. Works. This magnetic attractive force acts on the plunger rod 301a as an urging force (magnetic urging force). When this magnetic biasing force overcomes the biasing force of the plunger rod biasing spring 307, the plunger rod 301a moves in the direction away from the valve 301c (the valve opening direction). Then, the valve 301c is closed by the urging force of the valve urging spring 315 and the fluid force caused by the fuel flowing into the suction passage 10d. After closing the valve, the fuel pressure in the pressurizing chamber 11 increases with the upward movement of the plunger 2. When the fuel pressure becomes equal to or higher than the pressure at the fuel discharge port 12, high-pressure fuel is discharged through the discharge valve mechanism 8 and supplied to the common rail 23. This stroke is called a discharge stroke.

  That is, the compression stroke of the plunger 2 (the upward stroke from the bottom dead center to the top dead center) includes a return stroke and a discharge stroke. And the quantity of the high-pressure fuel discharged can be controlled by controlling the energization timing to the coil 304 of the electromagnetic suction valve 300. If the timing of energizing the electromagnetic coil 304 is advanced, the ratio of the return stroke during the compression stroke is small and the ratio of the discharge stroke is large. That is, less fuel is returned to the suction passage 10d and more fuel is discharged at high pressure. On the other hand, if the energization timing is delayed, the ratio of the return stroke in the compression stroke increases and the ratio of the discharge stroke decreases. That is, more fuel is returned to the suction passage 10d and less fuel is discharged at high pressure. The energization timing to the electromagnetic coil 304 is controlled by a command from the ECU 27.

  With the configuration described above, the amount of fuel discharged at a high pressure can be controlled to the amount required by the internal combustion engine by controlling the energization timing to the electromagnetic coil 304.

  The stroke GP2 of the valve 301c can secure a passage area that does not resist the flow of fuel into the pressurizing chamber 11 in the suction process of the plunger 2 and can be long enough to suck the anchor 301b when the electromagnetic coil 304 is energized. It is regulated by a valve stopper 313. Further, the distance GP1 between the fixed core 306 and the anchor 301b having a large influence on the suction force is also regulated by the valve stopper 313 because the anchor 301b and the valve 301c are connected via the plunger rod 301a in the valve open state. .

  If the valve stopper 313 is moved in the opening direction of the valve 301c during operation, the distance GP1 between the fixed core 306 and the anchor 301b increases, and the anchor 301b cannot be attracted even if the electromagnetic coil 304 is energized. . That is, since the valve 301c is always open, fuel cannot be discharged. Even if the anchor 301b can be attracted, the magnetic force decreases and the moving distance of the valve 301c increases due to the increase in the distance GP1, so that the time until the valve 301c is closed becomes longer. This means that it becomes difficult to control the amount of fuel discharged from the high-pressure pump 100 with high accuracy.

  In this embodiment, the end surface 313aa formed on the bottom portion 313a of the valve 301c is in contact with the bottom portion (bottom surface) 1ka of the electromagnetic suction valve insertion hole 1k so that the valve stopper 313 does not move during the operation of the valve 301c. In order to leave the electromagnetic suction valve insertion hole 1k in the non-penetrating state and leave the bottom (bottom surface) 1ka, a communication hole 1a that penetrates the bottom 1ka and communicates the electromagnetic suction valve insertion hole 1k and the annular groove 6a is provided. The communication hole 1a is divided into two in the radial direction of the cylinder 6 with respect to the axial center of the valve 301c. By providing the communication hole 1a, the bottom 1ka can be left so that the central portion of the valve 301c does not penetrate to the pressurizing chamber 11 side.

  Thereby, the valve stopper 313 can be brought into contact with the bottom surface 1ka of the electromagnetic suction valve insertion hole 1k, and the valve stopper 313 can be prevented from coming off and displaced. For this reason, the stroke of the valve 301c is kept constant without changing, and the controllability of the valve 301c does not change.

  Since the fuel flows on the outer periphery of the valve 301c, even if the central portion of the bottom surface 1ka of the electromagnetic intake valve insertion hole 1k is not communicated with the pressurizing chamber 11, there is no resistance. In this embodiment, the opening surface of the communication hole 1a on the side of the electromagnetic suction valve insertion hole 1k is disposed near the inner peripheral wall surface, avoiding the central portion of the bottom surface 1ka of the electromagnetic suction valve insertion hole 1k. For this reason, the opening surface of the communication hole 1a is not blocked by the valve stopper 313, and the flow path resistance can be reduced.

  Next, assembly of the electromagnetic suction valve 300 will be described with reference to FIGS. 6 and 7. FIG. 6 is an exploded perspective view showing the assembled state of the electromagnetic suction valve and the assembled state to the pump body. FIG. 7 is a plan view showing the valve stopper fixing member.

  The electromagnetic suction valve 300 has one end side in the axial direction of the plunger rod 301a in an assembly 300II in which a fixed core 306, a plunger rod biasing spring 307, a mover 301, an anchor biasing spring 312 and a guide member 311 are assembled to a yoke 305. The assembly 300III in which the coil 304, the side yoke 308, the back yoke 309 and the connector terminal 320 are assembled is assembled, and the assembly 300I of the intake valve portion 300B is assembled from the other axial end of the plunger rod 301a. .

  The assembly 300I of the intake valve portion 300B fixes the valve stopper fixing member 314 and the valve stopper 313 by press fitting. Next, the assembly of the valve stopper fixing member 314 and the valve stopper 313 is press-fitted and fixed to the valve housing 302. During the press-fitting process, the valve 301 c and the valve biasing spring 315 are assembled to the valve housing 302. Then, the assembly 300I in which the assembly of each part is completed is assembled to the assembly 300II.

  After the assembly of the assembly 300I, the assembly 300II, and the assembly 300III is completed, the electromagnetic suction valve 300 is press-fitted into the electromagnetic suction valve insertion hole 1k of the pump housing 1 and fixed. In this step, it is necessary to bring the end surface 313aa of the valve stopper 313 into contact with the bottom surface 1ka of the electromagnetic suction valve insertion hole 1k. At the same time, it is necessary to position the valve housing 302 and the valve stopper 313 so that the gap GP2 between the valve seat 302a and the end surface 301ca of the valve 301c has a predetermined dimension.

  In this embodiment, when the assembly of the valve stopper fixing member 314 and the valve stopper 313 is press-fitted into the valve housing 302, the amount of insertion of the assembly of the valve stopper fixing member 314 and the valve stopper 313 into the valve housing 302 is set. Keep it low. That is, the end surface 313aa of the valve stopper 313 is projected from the end of the valve housing 302 with a dimension larger than the final projecting dimension. When the electromagnetic suction valve 300 is press-fitted into the electromagnetic suction valve insertion hole 1k, the end surface 313aa of the valve stopper 313 is brought into contact with the bottom surface 1ka of the electromagnetic suction valve insertion hole 1k, and the electromagnetic suction valve 300 is further electromagnetically sucked therefrom. Push into the valve insertion hole 1k.

  According to this assembling method, the end surface 313aa of the valve stopper 313 can be reliably brought into contact with the bottom surface 1ka of the electromagnetic suction valve insertion hole 1k. Further, the gap GP2 between the valve seat 302a and the end surface 301ca of the valve 301c can be managed by the component accuracy of the assembly 300I.

  In addition to the assembly method described above, the assembly 300I of the suction valve portion 300B may be assembled in advance to the pump housing 1, and then the assembly 300II and the assembly 300III may be assembled to the assembly 300I and the pump housing 1. The end surface 313aa of the valve stopper 313 is protruded greatly from the end of the valve housing 302, and the assembly 300I is assembled to the pump housing 1 as described above, whereby the end surface 313aa of the valve stopper 313 is inserted into the electromagnetic intake valve insertion hole 1k. It is possible to reliably contact the bottom surface 1ka.

  In the assembly method described above, the assembly of the valve stopper fixing member 314 and the valve stopper 313 is used as the valve housing 302 when the electromagnetic suction valve 300 or the assembly 300I of the suction valve portion 300B is press-fitted into the electromagnetic suction valve insertion hole 1k. It is necessary to be able to be displaced (displacement) with respect to. For this reason, it is necessary to reduce the fixing force by press-fitting the assembly of the valve stopper fixing member 314 and the valve stopper 313 and the valve housing 302. In this embodiment, since the end surface 313aa of the valve stopper 313 is in contact with the bottom surface 1ka of the electromagnetic suction valve insertion hole 1k, it is not necessary to increase the fixing force of the valve stopper 313 that receives the collision force of the valve 301c. Therefore, the assembly method described above is possible.

  The valve stopper fixing member 314 can be formed of a press-processed product as shown in FIG. The valve stopper fixing member 314 is provided with a plurality of claw portions 314a that are press-fitted into the valve housing 302 at the outer peripheral portion with a gap in the circumferential direction. Further, an annular cylindrical fixing portion 314b is provided on the inner peripheral side of the valve stopper fixing member 314. The cylindrical portion 314b is bent in the same direction as the claw portion 314a. The cylindrical fixing portion 314b is press-fitted and fixed to the outer peripheral portion of the valve stopper 313.

  In this embodiment, the claw portion 314a is composed of three, but is not limited to three. It is preferable to enlarge the notch part 314c formed between the adjacent claw parts 314a and to increase the cross-sectional area of the fuel passage formed by the notch part 314c. Further, as described above, it is not necessary to increase the fixing force of the valve stopper 313 by the valve stopper fixing member 314, and it is preferable to appropriately reduce the fixing force in order to implement the above-described assembly method. Therefore, about 3-4 claw parts 314a are preferable. Further, since the valve stopper fixing member 314 does not need to increase the fixing force, the valve stopper fixing member 314 can have a simple structure, and can be manufactured by pressing using a thin plate material.

  In the present embodiment, the valve stopper fixing member 314 can be downsized, the assembly 300I of the intake valve portion 300B and the electromagnetic intake valve 300 can be downsized, and the high pressure pump 100 can be downsized.

  In addition, this invention is not limited to an above-described Example, Various modifications are included. For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations. In addition, it is possible to add, delete, and replace other configurations for a part of the configuration of the embodiment.

DESCRIPTION OF SYMBOLS 1 Pump main body (pump housing), 1k ... Electromagnetic suction valve insertion hole, 1ka ... Bottom part of electromagnetic suction valve insertion hole 1k, 2 ... Plunger, 6 ... Cylinder, 6a ... Circular groove of cylinder 6, 6b ... Communication hole, 7 ... Seal holder, 8 ... discharge valve mechanism, 10a ... low pressure fuel intake port, 10d ... intake passage, 11 ... pressurizing chamber, 11a ... communication hole, 12 ... fuel discharge port, 13 ... plunger seal, 27 ... engine control unit (ECU) ), 93 ... Cam, 100 ... High-pressure fuel supply pump (high-pressure pump), 300 ... Electromagnetic suction valve, 300 A ... Electromagnetic drive mechanism, 300 B ... Suction valve, 301 ... Movable element, 301 a ... Plunger rod, 301 b ... Anchor, 301c ... Valve (suction valve), 302 ... Valve housing, 302a ... Valve seat, 304 ... Electromagnetic coil, 305 ... Yoke, 306 ... Constant core, 307 ... plunger rod biasing spring (mover biasing spring), 308 ... side yoke, 309 ... back yoke, 310 ... closed magnetic path, 311 ... guide member, 311b ... guide portion, 312 ... anchor biasing spring, 313 ... Valve stopper, 313a ... Bottom of valve stopper 313, 314 ... Valve stopper fixing member, 314a ... Notch of valve stopper fixing member 314, 315 ... Valve biasing spring, 318 ... Bobbin, 319 ... Connector, 320 ... Terminal ( Connector pin), 300I, assembly 300II, 300III ... assembly.

Claims (13)

A pump housing having a cylinder in which a pressurizing chamber is formed; a plunger which is guided by the cylinder to reciprocate; an electromagnetic suction valve which is provided at an inlet of the pressurizing chamber and is driven by electromagnetic force; A discharge valve provided at the outlet of the pressure chamber, wherein the electromagnetic intake valve includes a valve, a valve seat that opens and closes a fuel passage when the valve is separated from and connected to the valve, and a valve stopper that contacts the valve when the valve is opened A high-pressure fuel supply pump that attaches the electromagnetic suction valve to an electromagnetic suction valve insertion hole formed in the pump housing and controls the electromagnetic suction valve to control the amount of fuel discharged from the discharge valve. ,
The high-pressure fuel supply pump, wherein the electromagnetic suction valve insertion hole is provided with a bottom portion that contacts the valve stopper, and a fuel passage hole that penetrates the bottom portion and communicates with both sides of the bottom portion. The high-pressure fuel supply pump according to claim 1,
The high-pressure fuel supply pump, wherein the valve stopper is disposed on the pressure chamber side with respect to the valve seat and the valve. The high-pressure fuel supply pump according to claim 2,
The high-pressure fuel supply pump, wherein a plurality of the fuel passage holes are formed around an extension line of a central axis of the electromagnetic suction valve. The high-pressure fuel supply pump according to claim 3,
The high-pressure fuel supply pump, wherein the fuel passage hole communicates with a fuel passage formed between the valve and the valve seat. The high-pressure fuel supply pump according to claim 4,
The cylinder is formed as a separate member from the pump housing, and is attached to a cylinder insertion hole formed in the pump housing.
The cylinder has an annular groove formed in an outer peripheral portion, and a communication hole that communicates the annular groove and the pressurizing chamber formed on an inner peripheral side. The high-pressure fuel supply pump according to claim 5,
The valve seat is formed and includes a valve housing containing the valve;
The high-pressure fuel supply pump, wherein the valve stopper is press-fitted and fixed to the valve housing by a fixing member formed by pressing a plate material. The high-pressure fuel supply pump according to claim 6,
The fixing member has an annular fixing portion that is press-fitted and fixed to the valve stopper on the inner peripheral side, and a claw portion that is press-fitted and fixed to the valve housing on the outer peripheral side,
A high-pressure fuel supply pump, wherein a plurality of the claw portions are provided at intervals in the circumferential direction of the fixing member, and a fuel passage is formed between adjacent claw portions. A pump housing having a cylinder in which a pressurizing chamber is formed; a plunger which is guided by the cylinder to reciprocate; an electromagnetic suction valve which is provided at an inlet of the pressurizing chamber and is driven by electromagnetic force; A discharge valve provided at the outlet of the pressure chamber, wherein the electromagnetic intake valve includes a valve, a valve seat that opens and closes a fuel passage when the valve is separated from and connected to the valve, and a valve stopper that contacts the valve when the valve is opened A high-pressure fuel supply pump that attaches the electromagnetic suction valve to an electromagnetic suction valve insertion hole formed in the pump housing and controls the electromagnetic suction valve to control the amount of fuel discharged from the discharge valve. ,
A high-pressure fuel supply pump, wherein the electromagnetic suction valve insertion hole is provided with a support portion that contacts the valve stopper and supports the valve stopper from the pressurizing chamber side. The high-pressure fuel supply pump according to claim 8,
The high-pressure fuel supply pump, wherein the valve stopper is disposed on the pressure chamber side with respect to the valve seat and the valve. The high-pressure fuel supply pump according to claim 9,
A high-pressure fuel supply pump having a fuel passage communicating the electromagnetic suction valve insertion hole and the pressurizing chamber. A pump housing having a cylinder in which a pressurizing chamber is formed; a plunger which is guided by the cylinder to reciprocate; an electromagnetic suction valve which is provided at an inlet of the pressurizing chamber and is driven by electromagnetic force; A discharge valve provided at the outlet of the pressure chamber, wherein the electromagnetic intake valve includes a valve, a valve seat that opens and closes a fuel passage when the valve is separated from and connected to the valve, and a valve stopper that contacts the valve when the valve is opened A high-pressure fuel supply pump that attaches the electromagnetic suction valve to an electromagnetic suction valve insertion hole formed in the pump housing and controls the electromagnetic suction valve to control the amount of fuel discharged from the discharge valve. In the assembly method,
Making a first assembly in which the valve housing containing the valve and the valve stopper are fixed so that the end of the valve stopper protrudes from the end of the valve housing;
When the first assembly is inserted into the electromagnetic suction valve insertion hole and press-fitted and fixed, the end portion of the valve stopper is brought into contact with the bottom portion of the electromagnetic suction valve insertion hole, and the end portion is the bottom portion. A method of assembling the high-pressure fuel supply pump, wherein the first assembly is further pushed into the electromagnetic suction valve insertion hole and fixed by press-fitting from a state where the first assembly is in contact with the electromagnetic suction valve. The method for assembling a high-pressure fuel supply pump according to claim 11,
An assembly method for a high-pressure fuel supply pump, wherein the valve stopper is press-fitted and fixed to the valve housing using a fixing member obtained by pressing a plate material. The method for assembling the high-pressure fuel supply pump according to claim 12,
The fixing member has an annular fixing portion that is press-fitted and fixed to the valve stopper on the inner peripheral side, and a claw portion that is press-fitted and fixed to the valve housing on the outer peripheral side,
A method of assembling a high-pressure fuel supply pump, wherein a plurality of the claw portions are provided at intervals in the circumferential direction of the fixing member, and a fuel passage is formed between adjacent claw portions.

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