JP6689178B2 - High pressure fuel supply pump - Google Patents

Description

  The present invention relates to a high-pressure fuel supply pump that pressure-feeds fuel to a fuel injection valve of an internal combustion engine, and more particularly to a method for fixing an electromagnetic coil of an electromagnetic intake valve mechanism.

  As a conventional technique of the high-pressure fuel pump of the present invention, there is one described in Patent Document 1. According to the patent document 1, a yoke (second yoke) which is a member forming the electromagnetic circuit is integrally formed with the electromagnetic coil by a resin of a connector mold.

Japanese Patent Application No. 2014-232398

  According to the background art described above, the yoke (second yoke), which is a member for forming the electromagnetic circuit, is injection-molded with the resin material forming the connector so as to be integrated with the electromagnetic coil. . However, there is a problem in that it is necessary to secure a resin thickness having sufficient strength, and as a result, the height of the electromagnetic coil becomes high and restrictions on mounting on the engine become large. There is also a problem that the cost increases due to the increased amount of engineering plastics used to form the connector.

  Therefore, it is an object of the present invention to supply a high-pressure fuel supply pump having an electromagnetic coil whose height is reduced and manufacturing cost is suppressed.

In order to achieve the above object, the present invention provides an intake valve mechanism 300 having an intake valve 30 for opening and closing a flow path on the upstream side of the pressurizing chamber 11, and an electromagnetic coil 43 for controlling the opening and closing of the intake valve 30. In the provided high-pressure fuel supply pump, a fixing member (annular member) for fixing the groove 39c formed in the intake valve mechanism 300 and the yoke (second yoke 44) constituting the magnetic circuit by being inserted and fixed in the groove 39c. 47), and the suction valve mechanism includes a fixed core that constitutes the magnetic circuit,
An anchor sucked by the fixed core is provided, and the groove is formed in the fixed core toward a radially inner side orthogonal to a moving direction of the anchor .

  According to the present invention, it is possible to provide a high-pressure fuel supply pump that suppresses an increase in size and an increase in manufacturing cost.

1 is a vertical sectional view of a high pressure fuel supply pump according to a first embodiment of the present invention. FIG. 3 is a horizontal cross-sectional view of the high-pressure fuel supply pump according to the first embodiment of the present invention as viewed from above. FIG. 2 is a vertical cross-sectional view of the high-pressure fuel supply pump according to the first embodiment of the present invention viewed from a direction different from that of FIG. FIG. 3 is an enlarged vertical cross-sectional view of the electromagnetic suction valve mechanism of the high-pressure fuel supply pump according to the first embodiment of the present invention, showing a state in which the electromagnetic suction valve mechanism is in a valve open state. 1 is a configuration diagram of an engine system to which a high-pressure fuel supply pump according to a first embodiment of the present invention is applied. FIG. 3 is an enlarged vertical cross-sectional view of the electromagnetic suction valve mechanism of the high-pressure fuel supply pump according to the first embodiment of the present invention, in which the electromagnetic suction valve mechanism opens when the pressurizing member is sandwiched between the annular member and the second yoke. Indicates a state of being in a state.

  Hereinafter, embodiments according to the present invention will be described in detail with reference to the drawings. In the following description, when describing the vertical direction or the vertical position without particular notice, the vertical direction or the vertical position is defined by the vertical direction or the vertical position on the paper surface of FIG. It does not mean the vertical direction or the position in the vertical direction when the supply pump is mounted.

First, a first embodiment of the present invention will be described in detail with reference to the drawings.
FIG. 5 shows an overall configuration diagram of the engine system. The part surrounded by the broken line is the main body of the high-pressure fuel supply pump (hereinafter referred to as the high-pressure pump), and the mechanism and parts shown in the broken line are integrally incorporated in the pump body 1.

  The fuel in the fuel tank 20 is pumped up by the feed pump 21 based on a signal from the engine control unit 27 (hereinafter referred to as ECU). This fuel is pressurized to an appropriate feed pressure and sent to the low-pressure fuel intake port 10a of the high-pressure fuel supply pump through the intake pipe 28. The fuel that has passed through the suction joint 51 from the low-pressure fuel suction port 10a reaches the suction port 31b of the electromagnetic suction valve mechanism 300 that constitutes the variable capacity mechanism via the pressure pulsation reducing mechanism 9 and the suction passage 10d.

  The fuel flowing into the electromagnetic suction valve mechanism 300 passes through a suction port opened and closed by the suction valve 30 and flows into the pressurizing chamber 11. Power for reciprocating motion is applied to the plunger 2 by the cam mechanism 93 of the engine. Due to the reciprocating motion of the plunger 2, fuel is sucked from the intake valve 30 in the descending stroke of the plunger 2 and pressurized in the ascending stroke. Fuel is pressure-fed through the discharge valve mechanism 8 to the common rail 23 to which the pressure sensor 26 is mounted. Then, based on the signal from the ECU 27, the injector 24 injects fuel into the engine. The present embodiment is a high pressure pump applied to a so-called direct injection engine system in which the injector 24 directly injects fuel into the cylinder of the engine. The high-pressure pump discharges a desired fuel flow rate of the supplied fuel in response to a signal from the ECU 27 to the electromagnetic suction valve mechanism 300.

Next, the configuration and operation of the high-pressure pump will be described with reference to FIGS. 1, 2, and 3.
FIG. 1 is a vertical cross-sectional view of the high-pressure pump of this embodiment, taken along a vertical cross-section, and FIG. 3 is a vertical cross-sectional view of the high-pressure pump taken in a vertical cross-section different from that of FIG.

  As shown in FIGS. 1 and 3, the high-pressure pump of this embodiment is fixed in close contact with the high-pressure pump mounting portion 90 of the internal combustion engine. Specifically, a screw hole 1b is formed in a mounting flange 1a provided on the pump body 1 of FIG. 2, and a plurality of bolts are inserted into the screw hole 1b, so that the mounting flange 1a becomes a high pressure pump mounting portion of an internal combustion engine. It adheres closely to 90 and is fixed.

  The O-ring 61 is fitted into the pump body 1 for a seal between the high-pressure pump mounting portion 90 and the pump body 1 to prevent engine oil from leaking to the outside.

  A cylinder 6 that guides the reciprocating movement of the plunger 2 and forms a pressurizing chamber 11 together with the pump body 1 is attached to the pump body 1. That is, the plunger 2 reciprocates inside the cylinder to change the volume of the pressurizing chamber. Further, an electromagnetic suction valve mechanism 300 for supplying fuel to the pressure chamber 11 and a discharge valve mechanism 8 for discharging fuel from the pressure chamber 11 to the discharge passage are provided.

  The cylinder 6 is press-fitted with the pump body 1 on the outer peripheral side thereof, and further, at the fixing portion 6a, the body is deformed toward the inner side to press the cylinder upward in the drawing, and the upper end surface of the cylinder 6 is inserted into the pressurizing chamber 11. It is sealed so that fuel pressurized under pressure does not leak to the low pressure side.

  At the lower end of the plunger 2, there is provided a tappet 92 that converts the rotational movement of a cam 93 attached to the camshaft of the internal combustion engine into vertical movement and transmits the vertical movement to the plunger 2. The plunger 2 is pressed against the tappet 92 by the spring 4 via the retainer 15. This allows the plunger 2 to reciprocate up and down with the rotational movement of the cam 93.

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

  As shown in FIGS. 2 and 3, a suction joint 51 is attached to the side surface of the pump body 1 of the high-pressure pump. The suction joint 51 is connected to a low-pressure pipe for supplying fuel from the fuel tank 20 of the vehicle, and the fuel is supplied from here to the inside of the high-pressure pump. The intake filter 52 has a role of preventing foreign matter existing between the fuel tank 20 and the low pressure fuel intake port 10a from being absorbed into the high pressure fuel supply pump by the flow of fuel.

  The fuel that has passed through the low-pressure fuel suction port 10a goes to the pressure pulsation reduction mechanism 9 through the low-pressure fuel suction port 10b that is vertically connected to the pump body 1. The pressure pulsation reducing mechanism 9 is arranged between the damper cover 14 and the upper end surface of the pump body 1, and is supported from below by a holding member 9 a arranged on the upper end surface of the pump body 1. Specifically, the pressure pulsation reducing mechanism 9 is configured by stacking two diaphragms, a gas of 0.3 MPa to 0.6 MPa is sealed inside, and the outer peripheral edge portion is fixed by welding. Therefore, the outer peripheral edge portion is thin and is configured to be thicker toward the inner peripheral side.

  A convex portion for fixing the outer peripheral edge portion of the pressure pulsation reducing mechanism 9 from below is formed on the upper surface of the holding member 9a. On the other hand, on the lower surface of the damper cover 14, a convex portion for fixing the outer peripheral edge portion of the pressure pulsation reducing mechanism 9 from above is formed. These convex portions are formed in a circular shape, and the pressure pulsation reducing mechanism 9 is fixed by being sandwiched by these convex portions. The damper cover 14 is press-fitted and fixed to the outer edge portion of the pump body 1. At this time, the holding member 9a elastically deforms to support the pressure pulsation reducing mechanism 9. In this way, the damper chamber 10c communicating with the low pressure fuel inlets 10a and 10b is formed on the upper and lower surfaces of the pressure pulsation reducing mechanism 9. Although not shown in the drawing, the holding member 9a is formed with a passage that communicates the upper side and the lower side of the pressure pulsation reducing mechanism 9, so that the damper chamber 10c is formed on the upper and lower surfaces of the pressure pulsation reducing mechanism 9. Is formed.

  The fuel that has passed through the damper chamber 10c then reaches the suction port 31b of the electromagnetic suction valve mechanism 300 through the low-pressure fuel flow path 10d that is formed by vertically communicating with the pump body. The suction port 31b is formed so as to vertically communicate with a suction valve seat member 31 forming the suction valve seat 31a.

  As shown in FIG. 2, the discharge valve mechanism 8 provided at the outlet of the pressurizing chamber 11 includes a discharge valve seat 8a, a discharge valve 8b that contacts and separates from the discharge valve seat 8a, and a discharge valve 8b that faces the discharge valve seat 8a. It is composed of a discharge valve spring 8c for urging and a discharge valve stopper 8d for determining the stroke (moving distance) of the discharge valve 8b. The discharge valve stopper 8d and the pump body 1 are welded to each other at the contact portion 8e to shut off the fuel from the outside.

  When there is no fuel pressure difference between the pressurizing chamber 11 and the discharge valve chamber 12a, the discharge valve 8b is pressed against the discharge valve seat 8a by the urging force of the discharge valve spring 8c and is in the closed state. Only when the fuel pressure in the pressurizing chamber 11 becomes larger than the fuel pressure in the discharge valve chamber 12a, the discharge valve 8b opens against the discharge valve spring 8c. Then, the high-pressure fuel in the pressurizing chamber 11 is discharged to the common rail 23 via the discharge valve chamber 12a, the fuel discharge passage 12b, and the fuel discharge port 12. When the discharge valve 8b opens, it contacts the discharge valve stopper 8d, and the stroke is limited. Therefore, the stroke of the discharge valve 8b is appropriately determined by the discharge valve stopper 8d. As a result, it is possible to prevent the fuel discharged at high pressure into the discharge valve chamber 12a from flowing back into the pressurizing chamber 11 again due to the stroke being too large and the delay in closing the discharge valve 8b. The decrease can be suppressed. The outer peripheral surface of the discharge valve stopper 8d guides the discharge valve 8b so that the discharge valve 8b moves only in the stroke direction when the discharge valve 8b repeatedly opens and closes. By doing so, the discharge valve mechanism 8 serves as a check valve that limits the flow direction of fuel.

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

  Further, the high pressure pump is provided with the relief valve mechanism 200 shown in FIGS. 1 and 2.

The relief valve mechanism 200 includes a relief body 201, a relief valve 202, a relief valve holder 203, a relief spring 204, and a spring stopper 205. The relief body 201 is provided with a tapered seat portion 201a. The valve 202 receives the load of the relief spring 204 via the valve holder 203, is pressed against the seat portion 201a, and cooperates with the seat portion 201a to shut off the fuel. The valve opening pressure of the relief valve 202 is determined by the load of the relief spring 204. The spring stopper 205 is press-fitted and fixed to the relief body 201, and serves as a mechanism for adjusting the load of the relief spring 204 depending on the press-fitted and fixed position. The relief valve mechanism 200 is externally assembled as a sub-assembly before being mounted on the pump body 1. After fixing the assembled relief valve mechanism 200 to the pump body 1 at the press-fitting portion 1c, the discharge joint 60 is welded and fixed to the pump body 1.
If the pressure of the fuel discharge port 12 becomes abnormally high due to a failure of the electromagnetic suction valve 300 of the high-pressure pump and becomes higher than the set pressure of the relief valve mechanism 200, the abnormal high-pressure fuel passes through the relief passage 213 and becomes a damper on the low pressure side. It will be relieved to the chamber 10c.
FIG. 4 is an enlarged view of the electromagnetic suction valve 300.
When the plunger 2 moves in the direction of the cam 93 and is in the suction stroke state due to the rotation of the cam 93, the volume of the pressurizing chamber 11 increases and the fuel pressure in the pressurizing chamber 11 decreases. When the fuel pressure in the pressurizing chamber 11 becomes lower than the pressure of the suction port 31b in this process, the suction valve 30 is opened. 30a indicates the maximum opening, and at this time, the suction valve 30 contacts the stopper 32. When the intake valve 30 is opened, the opening 30a formed in the seat member 31 is opened. The fuel passes through the opening 30a and flows into the pressurizing chamber 11 through the hole 1f formed in the pump body 1 in the lateral direction. The hole 1f also constitutes a part of the pressurizing chamber 11.

  After the plunger 2 completes the suction stroke, the plunger 2 starts to move upward. Here, the electromagnetic coil 43 remains in the non-energized state, and the magnetic biasing force does not act. The rod urging spring 40 urges the rod convex portion 35a which is convex toward the outer diameter side of the rod 35, and is set so as to have a necessary and sufficient urging force for keeping the intake valve 30 open in the non-energized state. There is. The volume of the pressurizing chamber 11 decreases as the plunger 2 moves upward. In this state, the fuel once sucked into the pressurizing chamber 11 is sucked again through the opening 30a of the intake valve 30 in the valve open state. Since it is returned to the passage 10d, the pressure in the pressurizing chamber does not rise. This process is called a return process.

  In this state, when a control signal from the ECU 27 is applied to the electromagnetic suction valve mechanism 300, a current flows through the electromagnetic coil 43 via the terminal 46. A magnetic attraction force acts between the magnetic core 39 and the anchor 36, and the magnetic core 39 and the anchor 36 come into contact with each other at the magnetic attraction surface S. The magnetic attraction force overcomes the urging force of the rod urging spring 40 to urge the anchor 36, and the anchor 36 engages with the rod convex portion 35a to move the rod 35 in the direction away from the suction valve 30.

  At this time, the suction valve 30 is closed by the urging force of the suction valve urging spring 33 and the fluid force of the fuel flowing into the suction passage 10d. After closing the valve, the fuel pressure in the pressurizing chamber 11 rises with the upward movement of the plunger 2, and when the pressure exceeds the pressure of the fuel discharge port 12, high-pressure fuel is discharged through the discharge valve mechanism 8 to the common rail 23. Supplied. This process is called a discharge process.

That is, the ascending stroke from the lower start point to the upper start point of the plunger 2 includes the return stroke and the discharge stroke. The amount of high-pressure fuel discharged can be controlled by controlling the timing of energizing the coil 43 of the electromagnetic suction valve mechanism 300. If the timing of energizing the electromagnetic coil 43 is advanced, the proportion of the return stroke and the proportion of the discharge stroke during the compression stroke are small. That is, less fuel is returned to the suction passage 10d, and more fuel is discharged under high pressure. On the other hand, if the timing of energization is delayed, the proportion of the return stroke during the compression stroke is large and the proportion of the discharge stroke is small. That is, much fuel is returned to the suction passage 10d, and less fuel is discharged under high pressure. The timing of energizing the electromagnetic coil 43 is controlled by a command from the ECU 27.
As described above, by controlling the power supply timing to the electromagnetic coil 43, the amount of fuel discharged at high pressure can be controlled to the amount required by the internal combustion engine.

  The low pressure fuel chamber 10 is provided with a pressure pulsation reducing mechanism 9 that reduces the pressure pulsation generated in the high pressure fuel supply pump from spreading to the fuel pipe 28. When the fuel once flowing into the pressurizing chamber 11 is returned to the suction passage 10d through the suction valve body 30 in the valve open state for the capacity control, the pressure of the low-pressure fuel chamber 10 is increased by the fuel returned to the suction passage 10d. Pulsation occurs. However, the pressure pulsation reducing mechanism 9 provided in the low-pressure fuel chamber 10 is formed by a metal diaphragm damper in which two corrugated disc-shaped metal plates are bonded together at their outer circumferences and an inert gas such as argon is injected into the inside. Therefore, the pressure pulsation is absorbed and reduced as the metal damper expands and contracts.

  The plunger 2 has a large diameter portion 2a and a small diameter portion 2b, and the volume of the sub chamber 7a increases or decreases due to the reciprocating movement of the plunger. The sub chamber 7a communicates with the low pressure fuel chamber 10 through the fuel passage 10e. When the plunger 2 descends, fuel flows from the sub chamber 7a to the low pressure fuel chamber 10, and when the plunger 2 rises, fuel flows from the low pressure fuel chamber 10 to the sub chamber 7a.

  As a result, the fuel flow rate into and out of the pump during the suction stroke or the return stroke of the pump can be reduced, and it has the function of reducing the pressure pulsation generated inside the high-pressure fuel supply pump.

Next, the configuration of the electromagnetic suction valve according to the present embodiment will be described in more detail. The electromagnetic suction valve is roughly composed of a suction valve portion, a solenoid mechanism portion and a coil portion, and this embodiment mainly relates to the structure of the solenoid mechanism portion and the coil portion therein.
First, the suction valve section will be described. The intake valve portion includes an intake valve 30, an intake valve seat 31, an intake valve stopper 32, an intake valve biasing spring 33, and an intake valve holder 34. In this embodiment, the suction valve holder 34 is functionally formed integrally with the suction valve stopper 32.

  The suction valve seat 31 has a cylindrical shape and has a seat portion 31a in the axial direction on the inner peripheral side and two or more suction passage portions 31b radially around the axis of the cylinder, and the pump body 1 has an outer peripheral cylindrical surface. Pressed and held.

  The suction valve holder 34 has claws radially extending in two or more directions, and the claw outer peripheral side is coaxially fitted and held on the inner peripheral side of the suction valve seat 31. Further, a suction valve stopper 32, which is cylindrical and has a brim at one end, is press-fitted and held on the inner circumferential cylindrical surface of the suction valve holder 34.

  The suction valve biasing spring 33 is provided on the inner peripheral side of the suction valve stopper 32, and a part thereof is arranged in a small diameter portion 32c (upstream side convex portion) for stabilizing one end of the spring 33 coaxially. The intake valve 30 is arranged between the intake valve seat portion 31a and the intake valve stopper 32, and the downstream convex portion is arranged and held on the inner diameter side of the intake valve biasing spring 33. The suction valve biasing spring 33 is arranged and held on the inner diameter side of the valve guide portion 30b. The suction valve biasing spring 33 is a compression coil spring and is installed so that the biasing force acts in the direction in which the suction valve 30 is pressed against the suction valve seat portion 31a. Not limited to the compression coil spring, any form may be used as long as it can obtain the biasing force, and a leaf spring having a biasing force integrated with the suction valve may be used.

  By configuring the intake valve portion in this way, in the intake process of the pump, the fuel that has passed through the intake passage 31b and enters the inside passes between the intake valve 30 and the seat portion 31a, and the outer periphery of the intake valve 30 The fuel flows into the pump pressurizing chamber 11 through the side and between the claws of the suction valve holder 34, the passage of the pump body 1 and the passage of the cylinder 6. Further, in the discharge process of the pump, the discharge valve 30 functions as a check valve for preventing backflow of the fuel to the inlet side by contacting and sealing the suction valve seat portion 31a.

  In order to make the movement of the suction valve 30 smooth, a passage 32a is provided in order to release the hydraulic pressure on the inner peripheral side of the suction valve stopper 32 according to the movement of the suction valve 30. The axial movement amount 30a of the suction valve 30 is limited by the suction valve stopper 32. This is because if the amount of movement is too large, the reverse flow rate increases due to the response delay when the intake valve 30 is closed, and the performance of the pump deteriorates. The regulation of the movement amount can be defined by the axial dimension and the press-fitting position of the intake valve seat 31a, the intake valve 30, and the intake valve stopper 32.

  The suction valve stopper 32 is provided with an annular protrusion 32b that is convex toward the upstream side of the small diameter portion 32c (upstream side convex portion), and when the suction valve 30 is open, the suction valve stopper 32 is provided. The contact area with is small. This is because the intake valve 30 is likely to be separated from the intake valve stopper 32 when the valve open state is changed to the valve closed state, that is, the valve closing response is improved. When there is no annular protrusion 32b, that is, when the contact area is large, a large squeeze force acts between the suction valve 30 and the suction valve stopper 32, and the suction valve 30 becomes difficult to separate from the suction valve stopper 32.

  The suction valve 30, the suction valve seat 31, and the suction valve stopper 32 are made of a heat-treated martensitic stainless steel, which has high strength, high hardness, and excellent corrosion resistance, because collisions occur repeatedly during operation. Austenitic stainless steel is used for the intake valve spring 33 and the intake valve holder 34 in consideration of corrosion resistance.

  Next, the solenoid mechanism section will be described. The solenoid mechanism portion includes a rod 35 that is a movable portion, an anchor 36, a spring seat member 37 that is a fixed portion, a first core 38, a second core 39, and a rod urging spring 40, an anchor urging spring 41, and a seal ring. It consists of 49.

  The rod 35, which is a movable part, and the anchor 36 are configured as separate members. The rod 35 is axially slidably retained on the inner peripheral side of the spring seat member 37, and the outer peripheral side of the anchor 36 is slidably retained on the inner peripheral side of the first core 38. That is, both the rod 35 and the anchor 36 are configured to be slidable in the axial direction within a geometrically restricted range.

  The anchor 36 has at least one through hole 36a penetrating in the axial direction of the component in order to freely and smoothly move in the fuel in the axial direction, and the movement limitation due to the pressure difference before and after the anchor is eliminated as much as possible. The spring seat member 37 is radially inserted into the inner peripheral side of the hole into which the intake valve of the pump body 1 is inserted, and axially abutted against one end of the intake valve seat 31 to allow the pump body 1 to move. It is arranged such that it is sandwiched between the first core 38 welded and fixed to the pump body 1 and the pump body 1. Similarly to the anchor 36, the spring seat member 37 is also provided with a through hole 37a penetrating in the axial direction so that the anchor can move freely and smoothly so that the pressure in the fuel chamber on the anchor side does not hinder the movement of the anchor. Is configured.

  The first core 38 has a thin-walled cylindrical shape on the side 38b opposite to the portion to be welded to the pump body, and is welded and fixed so that the seal ring 49 is inserted on the outer peripheral side thereof. Further, 49 a, which is the opposite side of the welded portion of the seal ring with the first core 38, is welded and fixed in a form of being inserted into the outer peripheral side of the second core 39. A rod urging spring 40 is arranged on the inner peripheral side of the second core 39 with the small diameter portion 39a as a guide, and the tip of the rod 35 comes into contact with the suction valve 30 to separate the suction valve 30 from the suction valve seat portion 31a. That is, a biasing force is applied in the valve opening direction of the intake valve. That is, the suction valve 30 is configured as a separate body from the rod 35, and is configured to be restricted from moving in the valve closing direction by contacting one end of the rod 35. The second core 39 has a magnetic attraction surface 39b facing the magnetic attraction surface 36c of the anchor 36. The magnetic attraction surface 39b of the second core 39 and the magnetic attraction surface 36c of the anchor 36 are parallel to each other, and a gap indicated by reference numeral 36e is provided between the two when the valve is open, and the coil 43 is energized. By doing so, a magnetic attraction force acts between the two companies, and the anchor 36 is attracted to the second core 39 side.

  The anchor urging spring 41 applies an urging force to the anchor 36 in the direction of the rod collar portion 35a while inserting one end into a cylindrical rod insertion portion 37b provided on the center side of the spring seat member 37 and keeping the same coaxial. It is arranged. A rod insertion hole 37c is provided in the rod insertion portion 37b, and the rod 35 is inserted therein. The rod collar portion 35a regulates relative displacement of the rod 35 with respect to the anchor 36 in the valve opening direction. That is, when the rod 35 is relatively displaced in the valve opening direction with respect to the anchor 36, the rod 35 engages with the anchor 36 to form an engaging portion that regulates the relative displacement. The rod 35 does not contact the rod insertion hole 37c, and a gap is provided between the outer peripheral surface of the rod 35 and the inner peripheral surface of the rod insertion hole 37c.

  The movement amount 36e of the anchor 36 is set to be larger than the movement amount 30a of the suction valve 30. This is because the suction valve 30 is surely closed.

  Since the rod 35 slides on the anchor 36, and the rod 35 repeatedly collides with the suction valve 30, martensitic stainless steel subjected to heat treatment is used in consideration of hardness and corrosion resistance. The anchor 36 and the second core 39 are made of magnetic stainless steel to form a magnetic circuit, and the collision surfaces of the anchor 36 and the second core are surface-treated to improve hardness. Further, the outer peripheral surface of the anchor 36 and the inner peripheral surface of the first core 38 may be surface-treated in order to improve hardness and corrosion resistance. In addition, the seal ring 49 uses a non-magnetic material in order to improve the attraction force generated on the magnetic attraction surface S. Hard Cr plating is used for the surface treatment, but it is not limited thereto. Austenitic stainless steel is used for the rod urging spring 40 and the anchor urging spring 41 in consideration of corrosion resistance.

  Since the intake valve portion is provided with one spring and the solenoid mechanism portion is provided with two springs, the electromagnetic intake valve 300 is configured with a total of three springs. That is, the electromagnetic suction valve 300 includes a suction valve biasing spring 33 that is a suction valve portion, a rod biasing spring 40 that is a solenoid mechanism portion, and an anchor biasing spring 41. In this embodiment, the coil springs are used as the springs, but any springs can be used as long as the biasing force can be obtained.

  Finally, the configuration of the coil section will be described. The structure of the coil portion of this embodiment includes a first yoke 42, an electromagnetic coil 43, a second yoke 44, a bobbin 45, a terminal 46, an annular member 47, and a connector 50. A coil 43 in which a copper wire is wound a plurality of times around the bobbin 45 is arranged so as to be surrounded by the first yoke 42 and the second yoke 44, and is molded and fixed integrally with the connector 50 which is a resin member. One ends of the two terminals 46 are electrically connected to both ends of the copper wire of the coil. The terminal 46 is molded integrally with the connector 50, and the other end is connected to the engine control unit side. In the coil portion, the hole portion at the center of the first yoke 42 is press-fitted and fixed to the first core 38. At that time, the inner diameter side of the second yoke 44 is in contact with the second core 39 or is in close proximity with a slight clearance.

  In the present invention, the groove 39c is formed in the second core 39 in a cylindrical shape, and the annular member 47 is inserted or press-fitted and fixed therein to restrict the movement of the second yoke 44 in the axial direction. There is.

  Both the first yoke 42 and the second yoke 44 are made of a magnetic stainless steel material in order to form a magnetic circuit and in consideration of corrosion resistance, and the bobbin 45 and the connector 50 are high in strength and heat resistance. It is made of strong heat resistant resin. The coil 43 is made of copper, and the terminal 46 is made of brass plated with metal.

  By configuring the solenoid mechanism section and the coil section as described above, a magnetic circuit is formed by the first core 38, the first yoke 42, the second yoke 44, the second core 39 and the anchor 36, and a current is supplied to the coil. When given, an electromagnetic force is generated between the second core 39 and the anchor 36, and a force that pulls the anchor 36 toward the second core 39 is generated.

  When the electromagnetic force exceeds the valve opening biasing force f1 obtained by subtracting the biasing force of the anchor biasing spring 41 and the biasing force of the suction valve biasing spring 33 from the biasing force of the rod biasing spring 40, the anchor that is the movable part It allows the movement of 36 with the rod 35 towards the second core 39 and also allows the second core 39 and the anchor 36 to come into contact and continue to be in contact.

  According to the conventional configuration, as described in Patent Document 1, the second yoke is restricted in the axial direction by integrating the first yoke 42, the second yoke 44, the electromagnetic coil 43, the bobbin 45, the terminal 46, and the connector 50 with a resin material. It was done by injection molding in. However, it is necessary to secure a large resin thickness in order to secure sufficient strength in consideration of the harsh usage conditions in the actual vehicle, and as a result, the height of the electromagnetic coil becomes high and The problem was that the restrictions on mounting became large. There is also a problem that the cost increases due to the increased amount of engineering plastics used to form the connector.

  Therefore, in this embodiment, as described above, the groove is formed in the second core 39, and the second yoke 44 is fixed by inserting and fixing the annular member 47 into the groove. Specifically, in a high-pressure fuel supply pump including an intake valve mechanism 300 having an intake valve 30 for opening and closing a flow path on the upstream side of the pressurizing chamber 11 and an electromagnetic coil 43 for controlling the opening and closing of the intake valve 30. The suction valve mechanism 300 is provided with a groove 39c and a fixing member (annular member 47) for fixing the yoke (second yoke 44) constituting the magnetic circuit by being inserted and fixed in the groove 39c.

  Further, as shown in FIG. 4, the intake valve mechanism 300 preferably includes a fixed core 39 that constitutes a magnetic circuit, and the groove 39c is preferably formed in the fixed core 39. The suction valve mechanism 300 includes a fixed core 39 that constitutes a magnetic circuit, and an anchor 36 that is attracted to the fixed core 39. The groove 39c has a groove 39c that extends inward in the radial direction orthogonal to the moving direction of the anchor 36. It is desirable to be formed in.

  The fixed member (annular member 47) is arranged on the side opposite to the electromagnetic coil 43 with respect to the yoke (second yoke 44), and the yoke (second yoke 44) is moved toward the fixed member (annular member 47). Regulation is desirable. The groove 39c is formed in an annular shape with respect to the fixed core 39, and the fixing member (annular member 47) is preferably formed in a substantially annular shape corresponding to the groove 39c. Further, it is desirable that the fixing member (annular member 47) is made of a metal member and the pressurizing member 48 has elasticity. In addition, it is desirable to use a stainless spring material such as SUS631 for the fixing member (annular member 47) and the pressurizing member 48.

  Thereby, it is possible to secure a sufficient axial fixing strength of the second yoke 44 without increasing the resin thickness. Further, by using, for example, a C-ring as the annular member 47, it is possible to reduce the cost of the annular member 47 itself and to make the groove of the second core 39 easy to process.

  In addition, although the groove shape of the groove processing portion 39c of the second core 39 is described as the cylindrical shape and the annular member 47 is described as the fixing member in the present embodiment, the present invention is not limited to this. That is, since the feature of the present embodiment is that the fixing member is inserted into the groove shape, it is possible to adopt a structure other than the cylindrical groove and the annular fixing member. For example, a configuration may be considered in which the groove has a quadrangular shape instead of a cylindrical shape, and the fixing member has a U shape instead of an annular shape.

  Further, as shown in FIG. 6, a pressurizing member 48 capable of pressurizing in the axial direction is sandwiched between the annular member 47 and the second yoke 44. That is, it is desirable to provide the pressurizing member 48 that applies pressure to both the fixing member (annular member 47) and the yoke (second yoke 44) forming the magnetic circuit. As a result, it is possible to absorb the play caused by the gap between the second yoke 44 and the annular member 47 and to make the attachment more reliable.

  By adopting the structure of the present embodiment as described above, it is possible to provide a high-pressure pump that is more inexpensive and inexpensive.

1 pump body 1a mounting flange 1b screw hole 1c press-fitted portion 1f of relief body into pump body 1 hole laterally formed in pump body 2 plunger 2a large diameter portion 2b small plunger portion 4 plunger spring 6 cylinder 6a cylinder and pump Body fixing part 7 Seal holder 7a Sub chamber 8 Discharge valve mechanism 8a Discharge valve seat 8b Discharge valve 8c Discharge valve spring 8d Discharge valve stopper 8e Discharge valve stopper and pump body abutment 9 Pressure pulsation reduction mechanism 9a Pressure pulsation reduction mechanism Holding member 10a Low-pressure fuel inlet 10b Low-pressure fuel inlet 10c Damper chamber 10d Suction passage 10e Fuel passage 11 Pressurizing chamber 12 Fuel discharge port 12a Discharge valve chamber 12b Fuel discharge passage 13 Plunger seal 14 Damper cover 15 Retainer 20 Fuel tank 21 Feed pump 23 common 24 Injector 26 Pressure sensor 27 Engine control unit 28 Intake piping 30 Intake valve 30a Intake valve opening 30b Intake valve biasing spring guide 31 Intake valve seat member 31a Intake valve seat 31b Intake port 32 Intake valve Stopper 32a passage 32b suction valve stopper annular protrusion 32c suction valve stopper small diameter portion 33 suction valve biasing spring 35 rod 35a rod protrusion 36 anchor 36a anchor through hole 36c anchor magnetic attraction surface 36e between anchor and second core Gap 37 Spring seat member 37a Spring seat member through hole 37b Spring seat member rod insertion portion 37c Spring seat member rod insertion hole 38 First core 38b First core 38b opposite side of pump body fixing portion 39 Second core 39a Two core small inner diameter portion 39b Second core magnetic attraction surface 39c Second Grooved portion 40 a Rod urging spring 41 Anchor urging spring 42 First yoke 43 Electromagnetic coil 44 Second yoke 45 Bobbin 46 Terminal 47 Annular member 48 Pressurizing member 49 Seal ring 49a Joint of seal ring with first core 50 connector 51 suction joint 52 suction filter 60 discharge joint 61 O-ring 90 high pressure pump mounting portion 92 tappet 93 cam mechanism 200 relief valve 201 relief body 201a relief body seat portion 202 valve holder 203 relief spring 204 spring stopper 213 relief Passage 300 Electromagnetic suction valve mechanism

Claims (5)

In a high-pressure fuel supply pump having an intake valve mechanism having an intake valve for opening and closing a flow path on the upstream side of the pressurizing chamber and an electromagnetic coil for controlling the opening and closing of the intake valve,
A groove formed in the suction valve mechanism; and a fixing member for fixing the yoke constituting the magnetic circuit by being inserted and fixed in the groove ,
The suction valve mechanism has a fixed core that constitutes the magnetic circuit,
An anchor sucked to the fixed core,
A high-pressure fuel supply pump, wherein the groove is formed in the fixed core inward in a radial direction orthogonal to a moving direction of the anchor . The high-pressure fuel supply pump according to claim 1,
A high-pressure fuel supply pump comprising a pressurizing member for applying pressure to both the fixing member and the yoke forming the magnetic circuit. The high-pressure fuel supply pump according to claim 1,
The high-pressure fuel supply pump, wherein the fixing member is arranged on the side opposite to the electromagnetic coil with respect to the yoke, and restricts movement of the yoke toward the fixing member. The high-pressure fuel supply pump according to claim 1 ,
The high pressure fuel supply pump according to claim 1, wherein the groove is formed in an annular shape with respect to the fixed core, and the fixing member is formed in an approximately annular shape corresponding to the groove. The high-pressure fuel supply pump according to claim 2,
The high-pressure fuel supply pump, wherein the fixing member is a metal member and the pressurizing member has elasticity.

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