JP2018087548A - High-pressure fuel supply pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a high-pressure fuel supply pump reduced in height and suppressed in increase of manufacturing costs.SOLUTION: A high-pressure fuel supply pump including an intake valve mechanism 300 having an intake valve 30 for opening and closing a flow channel at an upstream side of a pressurizing chamber 11, and an electromagnetic coil 43 controlling opening/closing of the intake valve 30, further includes a groove 39c formed on the intake valve mechanism 300, and a fixing member (annular member 47) for fixing a yoke (second yoke 44) configuring a magnetic circuit, by being inserted and fixed in the groove 39c.SELECTED DRAWING: Figure 1

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 an electromagnetic coil fixing method of an electromagnetic intake valve mechanism.

  There exists a thing of patent document 1 as a prior art of the high-pressure fuel pump of this invention. According to Patent Document 1, a yoke (second yoke) that is a member constituting an electromagnetic circuit is formed integrally with an 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 constituting an electromagnetic circuit, is injection-molded with a resin material that forms a connector so as to be integrated with the electromagnetic coil. . However, it is necessary to secure a resin thickness with sufficient strength, and as a result, there is a problem that the height of the electromagnetic coil becomes high and restrictions on attachment to the engine increase. In addition, there is a problem that the cost increases due to an increase in the amount of engineering plastic used to form the connector.

  Therefore, an object of the present invention is to supply a high-pressure fuel supply pump having an electromagnetic coil that can suppress a reduction in height and an increase in manufacturing cost.

  In order to achieve the above object, the present invention includes a suction valve mechanism 300 having a suction valve 30 for opening and closing a flow path upstream of the pressurizing chamber 11 and an electromagnetic coil 43 for controlling the opening and closing of the suction valve 30. In the high-pressure fuel supply pump provided, a groove 39c formed in the suction valve mechanism 300 and a fixing member (annular member) for fixing the yoke (second yoke 44) constituting the magnetic circuit by being inserted and fixed in the groove 39c 47).

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

1 is a longitudinal sectional view of a high-pressure fuel supply pump according to a first embodiment of the present invention. It is the horizontal direction sectional view seen from the upper direction of the high-pressure fuel supply pump by the first example of the present invention. It is the longitudinal cross-sectional view seen from FIG. 1 of the high-pressure fuel supply pump by 1st Example of this invention from another direction. 1 is an enlarged longitudinal sectional view of an electromagnetic suction valve mechanism of a high-pressure fuel supply pump according to a first embodiment of the present invention, showing a state where the electromagnetic suction valve mechanism is in a valve open state. 1 shows 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. FIG. 3 is an enlarged longitudinal sectional view of an 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 is opened when a pressurizing member is sandwiched between the annular member and the second yoke. Indicates a state that is in a state.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the following description, when the position in the vertical direction or the vertical direction is described 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 vertical position in the state where 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. A portion surrounded by a broken line is a main body of a high-pressure fuel supply pump (hereinafter referred to as a high-pressure pump), and mechanisms and parts shown in the broken line are integrated into the pump body 1.

  The fuel in the fuel tank 20 is pumped up by the feed pump 21 based on a signal from an 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 inlet 10a of the high-pressure fuel supply pump through the suction 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 constituting the variable capacity mechanism via the pressure pulsation reducing mechanism 9 and the suction passage 10d.

  The fuel that has flowed into the electromagnetic suction valve mechanism 300 passes through the suction port that is opened and closed by the suction valve 30 and flows into the pressurizing chamber 11. The reciprocating power is applied to the plunger 2 by the cam mechanism 93 of the engine. The reciprocating motion of the plunger 2 sucks fuel from the suction valve 30 during the downward stroke of the plunger 2 and pressurizes the fuel during the upward stroke. Through the discharge valve mechanism 8, the fuel is pumped to the common rail 23 to which the pressure sensor 26 is attached. The injector 24 injects fuel into the engine based on a signal from the ECU 27. The present embodiment is a high pressure pump applied to a so-called direct injection engine system in which an injector 24 directly injects fuel into a cylinder cylinder of an engine. The high-pressure pump discharges a desired fuel flow rate of the supplied fuel by 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 longitudinal sectional view taken along a vertical section of the high-pressure pump of this embodiment, and FIG. 2 is a horizontal sectional view of the high-pressure pump as viewed from above. FIG. 3 is a longitudinal sectional view of the high-pressure pump cut along a vertical 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 in the pump body 1 of FIG. 2, and a plurality of bolts are inserted into the mounting flange 1a so that the mounting flange 1a becomes a high-pressure pump mounting portion of the internal combustion engine. It adheres to 90 and is fixed.

  An O-ring 61 is fitted into the pump body 1 for sealing 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 motion 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 pressurizing chamber 11 and a discharge valve mechanism 8 for discharging fuel from the pressurizing chamber 11 to the discharge passage are provided.

  The cylinder 6 is press-fitted into the pump body 1 on the outer peripheral side thereof, and further, in the fixed portion 6a, the body is deformed to the inner week side to press the cylinder upward in the figure, and the cylinder 6 is brought into the pressurizing chamber 11 at the upper end surface. The pressurized fuel is sealed so that it does not leak to the low pressure side.

  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. Thereby, 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) for lubricating the sliding portion 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 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. The suction filter 52 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 by the flow of fuel.

  The fuel that has passed through the low-pressure fuel suction port 10a travels to the pressure pulsation reduction mechanism 9 through the low-pressure fuel suction port 10b that communicates with the pump body 1 in the vertical direction. The pressure pulsation reducing mechanism 9 is disposed 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 disposed on the upper end surface of the pump body 1. Specifically, the pressure pulsation reducing mechanism 9 is configured by overlapping two diaphragms, and 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 is thin and is configured to become thicker toward the inner peripheral side.

  And the convex part for fixing the outer-periphery edge part of the pressure pulsation reduction mechanism 9 from the lower side is formed in the upper surface of the holding member 9a. On the other hand, the lower surface of the damper cover 14 is formed with a convex portion for fixing the outer peripheral edge portion of the pressure pulsation reducing mechanism 9 from above. These convex portions are formed in a circular shape, and the pressure pulsation reducing mechanism 9 is fixed by being sandwiched between these convex portions. The damper cover 14 is press-fitted and fixed to the outer edge of the pump body 1. At this time, the holding member 9 a is elastically deformed to support the pressure pulsation reducing mechanism 9. In this way, damper chambers 10c communicating with the low-pressure fuel inlets 10a and 10b are 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 has the upper and lower surfaces of the pressure pulsation reducing mechanism 9. Formed.

  The fuel that has passed through the damper chamber 10c then reaches the intake port 31b of the electromagnetic intake valve mechanism 300 via the low-pressure fuel passage 10d formed in communication with the pump body in the vertical direction. The suction port 31b is formed to communicate with the suction valve seat member 31 forming the suction valve seat 31a in the vertical direction.

  As shown in FIG. 2, the discharge valve mechanism 8 provided at the outlet of the pressurizing chamber 11 has a discharge valve sheet 8a, a discharge valve 8b contacting and separating from the discharge valve sheet 8a, and a discharge valve 8b toward the discharge valve sheet 8a. A discharge valve spring 8c to be energized and a discharge valve stopper 8d for determining a stroke (movement distance) of the discharge valve 8b. The discharge valve stopper 8d and the pump body 1 are joined by welding at the contact portion 8e to block the fuel and the outside.

  In a state where there is no fuel differential pressure in 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 closed. Only when the fuel pressure in the pressurizing chamber 11 becomes higher than the fuel pressure in the discharge valve chamber 12a, the discharge valve 8b opens against the discharge valve spring 8c. The high-pressure fuel in the pressurizing chamber 11 is discharged to the common rail 23 through the discharge valve chamber 12a, the fuel discharge passage 12b, and the fuel discharge port 12. When the discharge valve 8b is opened, the discharge valve 8b comes into contact with the discharge valve stopper 8d, 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 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 due to the delay in closing the discharge valve 8b. Reduction can be suppressed. Further, when the discharge valve 8b repeats opening and closing movements, the discharge valve 8b is guided by the outer peripheral surface of the discharge valve stopper 8d so that the discharge valve 8b moves 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 body 1, the electromagnetic suction valve mechanism 300, the plunger 2, the cylinder 6, and the discharge valve mechanism 8.

  The high pressure pump is provided with the relief valve mechanism 200 shown in FIGS.

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 sheet portion 201a. The valve 202 is loaded with the load of the relief spring 204 via the valve holder 203, pressed against the seat portion 201a, and shuts off the fuel in cooperation with the seat portion 201a. 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 has a mechanism for adjusting the load of the relief spring 204 depending on the press-fitting and fixing position. The relief valve mechanism 200 is assembled outside as a subassembly before being mounted on the pump body 1. After the assembled relief valve mechanism 200 is fixed to the pump body 1 by the press-fit portion 1c, the discharge joint 60 is fixed to the pump body 1 by welding.
When 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 the 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 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 port 31b, the suction valve 30 is opened. Reference numeral 30 a denotes the maximum opening, and at this time, the intake 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 a hole 1f formed in the pump body 1 in the lateral direction. The hole 1 f 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 a non-energized state and no magnetic biasing force acts. The rod biasing spring 40 biases the rod convex portion 35a convex toward the outer diameter side of the rod 35, and is set to have a biasing force necessary and sufficient to keep the intake valve 30 open in a non-energized state. Yes. 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 again sucked through the opening 30a of the intake valve 30 in the valve open state. Since the pressure is returned to the passage 10d, 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 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 attractive 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 attractive surface S. The magnetic attraction force overcomes the urging force of the rod urging spring 40 and urges the anchor 36. The anchor 36 engages with the rod convex portion 35a and moves the rod 35 away from the intake valve 30.

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

That is, the ascending stroke from the lower starting point to the upper starting point of the plunger 2 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 43 of the electromagnetic suction valve mechanism 300. If the timing of energizing the electromagnetic coil 43 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, the amount of fuel returned to the suction passage 10d is small and the amount of fuel discharged at high pressure is large. On the other hand, if the energization timing is delayed, the ratio of the return stroke during the compression stroke is large and the ratio of the discharge stroke is small. That is, the amount of fuel returned to the suction passage 10d is large, and the amount of fuel discharged at high pressure is small. The energization timing to the electromagnetic coil 43 is controlled by a command from the ECU 27.
As described above, by controlling the energization 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 reduction mechanism 9 that reduces and reduces the pressure pulsation generated in the high pressure fuel supply pump from spreading to the fuel pipe 28. When the fuel that has once flowed into the pressurizing chamber 11 is returned to the suction passage 10d through the intake valve body 30 that is opened again for capacity control, the fuel returned to the suction passage 10d causes the pressure in the low-pressure fuel chamber 10 to be reduced. Pulsation occurs. However, the pressure pulsation reducing mechanism 9 provided in the low-pressure fuel chamber 10 is formed of a metal diaphragm damper in which two corrugated disk-shaped metal plates are bonded together on the outer periphery and an inert gas such as argon is injected inside. The pressure pulsation is absorbed and reduced by expansion and contraction of the metal damper.

  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 as the plunger reciprocates. The sub chamber 7a communicates with the low pressure fuel chamber 10 through a fuel passage 10e. When the plunger 2 descends, fuel flows from the sub chamber 7a to the low pressure fuel chamber 10, and when it rises, fuel flows from the low pressure fuel chamber 10 to the sub chamber 7a.

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

Next, the details of the configuration of the electromagnetic suction valve according to the present embodiment will be described. The electromagnetic suction valve is roughly divided into 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 intake valve portion will be described. The intake valve section 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 about the cylindrical shaft. Press-fitted and held.

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

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

  By configuring the suction valve portion in this way, in the pump suction process, the fuel that has passed through the suction passage 31b and entered the interior passes between the suction valve 30 and the seat portion 31a, and the outer periphery of the suction valve 30 The fuel flows into the pump pressurizing chamber 11 through the passages of the pump body 1 and the cylinder 6 through the side and the claw of the suction valve holder 34. In the discharge process of the pump, the discharge valve 30 is in contact with the suction valve seat portion 31a to perform a check valve function for preventing the reverse flow of fuel to the inlet side.

  In order to smooth the movement of the suction valve 30, a passage 32 a 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 30 a 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 a response delay when the intake valve 30 is closed, and the performance as a pump decreases. The movement amount can be regulated by the axial dimensions and the press-fitting positions of the suction valve seat 31a, the suction valve 30 and the suction valve stopper 32.

  The intake valve stopper 32 is provided with an annular protrusion 32b that protrudes further upstream than the small-diameter portion 32c (upstream convex portion), and the intake valve stopper 32 is in a state where the intake valve 30 is open. The contact area with is reduced. This is because the intake valve 30 is easily separated from the intake valve stopper 32 during the transition from the open state to the 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 intake valve 30 and the intake valve stopper 32, and the intake valve 30 is difficult to separate from the intake valve stopper 32.

  The suction valve 30, the suction valve seat 31, and the suction valve stopper 32 are made of a material obtained by heat-treating martensitic stainless steel having high strength, high hardness, and excellent corrosion resistance in order to repeatedly collide with each other. The suction valve spring 33 and the suction valve holder 34 are made of austenitic stainless steel in consideration of corrosion resistance.

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

  The rod 35 and the anchor 36 which are movable parts are configured as separate members. The rod 35 is slidably held in the axial direction on the inner peripheral side of the spring seat member 37, and the outer peripheral side of the anchor 36 is slidably held 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 regulated range.

  The anchor 36 has one or more through holes 36a penetrating in the axial direction of the component in order to move smoothly and freely in the axial direction in the fuel, and eliminates the restriction of movement due to the pressure difference before and after the anchor as much as possible. The spring seat member 37 is inserted in the radial direction on the inner peripheral side of the hole into which the suction valve of the pump body 1 is inserted, and in the axial direction, is abutted against one end of the suction valve seat 31. It is set as the structure arrange | positioned in the form inserted | pinched between the 1st core 38 and the pump body 1 which are weld-fixed to. Similarly to the anchor 36, the spring seat member 37 is provided with a through-hole 37a penetrating in the axial direction so that the anchor can move freely and smoothly so that the pressure of the fuel chamber on the anchor side does not hinder the movement of the anchor. It is configured.

  The first core 38 has a thin cylindrical shape on the side 38b opposite to the portion to be welded to the pump body, and is fixed by welding in such a manner that a seal ring 49 is inserted on the outer peripheral side thereof. Further, 49a, which is the opposite side of the welded portion with the first core 38 of the seal ring, is welded and fixed in such a manner that it is inserted into the outer peripheral side of the second core 39. A rod biasing spring 40 is disposed on the inner peripheral side of the second core 39 with the small diameter portion 39a as a guide, the tip of the rod 35 contacts the suction valve 30, and the suction valve 30 is pulled away from the suction valve seat portion 31a. That is, an urging force is applied in the opening direction of the intake valve. That is, the intake 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 is formed with a magnetic attraction surface 39 b that faces the magnetic attraction surface 36 c 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 in an open state. By doing so, a magnetic attractive force acts between the two companies, and the anchor 36 is attracted to the second core 39 side.

  The anchor biasing spring 41 applies a biasing force to the anchor 36 in the direction of the rod collar 35a while inserting one end into a cylindrical rod insertion portion 37b provided on the center side of the spring seat member 37 and maintaining the same axis. It is arranged. The rod insertion portion 37b is provided with a rod insertion hole 37c, and the rod 35 is inserted therethrough. The rod collar portion 35a restricts relative displacement of the rod 35 in the valve opening direction with respect to the anchor 36. That is, when the rod 35 is relatively displaced in the valve opening direction with respect to the anchor 36, an engaging portion that engages with the anchor 36 and restricts the relative displacement is configured. The rod 35 is not in contact with 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 intake valve 30 is surely closed.

  Since the rod 35 slides with 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 respective collision surfaces of the anchor 36 and the second core are subjected to a surface treatment for improving the hardness. Further, the outer peripheral surface of the anchor 36 and the inner peripheral surface of the first core 38 may be subjected to a surface treatment in order to improve hardness and corrosion resistance. The seal ring 49 uses a non-magnetic material in order to improve the attractive force generated on the magnetic attractive surface S. The surface treatment includes hard Cr plating, but is not limited thereto. Austenitic stainless steel is used for the rod biasing spring 40 and the anchor biasing spring 41 in consideration of corrosion resistance.

  The intake valve portion is provided with one spring, and the solenoid mechanism portion is provided with two springs, so that 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 configured as a suction valve unit, a rod biasing spring 40 and an anchor biasing spring 41 configured as a solenoid mechanism unit. In this embodiment, any spring uses a coil spring, but any spring can be used as long as it can obtain an urging force.

  Finally, the configuration of the coil portion will be described. The configuration 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 around a bobbin 45 is disposed so as to be surrounded by a first yoke 42 and a second yoke 44, and is molded and fixed integrally with a connector 50 that is a resin member. One end of each of the two terminals 46 is connected to both ends of the copper wire of the coil so as to be energized. The terminal 46 is molded integrally with the connector 50, and the other end is connected to the engine control unit side. The coil portion is fixed by press-fitting a hole at the center of the first yoke 42 into the first core 38. At that time, the inner diameter side of the second yoke 44 is configured to come into contact with the second core 39 or close with a slight clearance.

  In the present invention, the second core 39 is formed with a cylindrical groove 39c, and an annular member 47 is inserted into the second core 39 or fixed by press-fitting to restrict the movement of the second yoke 44 in the axial direction. Yes.

  Both the first yoke 42 and the second yoke 44 are made of a magnetic stainless 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 consideration of strength characteristics and heat resistance characteristics. It is constructed using a 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 and the coil 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 current is supplied to the coil. When applied, 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 which is a movable part The movement in which 36 is attracted to the second core 39 together with the rod 35, and the second core 39 and the anchor 36 are brought into contact with each other, and the contact can be continued.

  In the conventional configuration, as described in Patent Document 1, the first yoke 42, the second yoke 44, the electromagnetic coil 43, the bobbin 45, the terminal 46, and the connector 50 are integrally formed of a resin material. It was done by injection molding. However, in consideration of the severe usage conditions in the actual vehicle, it is necessary to ensure a large resin thickness in order to ensure sufficient strength. As a result, the height of the electromagnetic coil increases, The problem was that the mounting restrictions would be large. In addition, there is a problem that the cost increases due to an increase in the amount of engineering plastic used to form the connector.

  Therefore, in this embodiment, as described above, a 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 a suction valve mechanism 300 having a suction valve 30 that opens and closes a flow path upstream of the pressurizing chamber 11 and an electromagnetic coil 43 that controls the opening and closing of the suction valve 30. And a groove 39c formed in the suction valve mechanism 300 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.

  As shown in FIG. 4, the suction valve mechanism 300 includes a fixed core 39 that constitutes a magnetic circuit, and the groove 39 c is preferably formed in the fixed core 39. The intake 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, and a groove 39 c is formed on the fixed core 39 inward in the radial direction perpendicular to the moving direction of the anchor 36. It is desirable to be formed.

  The fixing member (annular member 47) is disposed on the opposite side of the electromagnetic coil 43 with respect to the yoke (second yoke 44), and the yoke (second yoke 44) moves toward the fixing member (annular member 47). It is desirable to regulate. 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. The fixing member (annular member 47) is preferably made of a metal member, and the pressurizing member 48 preferably has elasticity. The fixing member (annular member 47) and the pressurizing member 48 are preferably made of a stainless spring material such as SUS631.

  Thereby, it is possible to ensure 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 the present embodiment, the groove shape of the groove processing portion 39c of the second core 39 has been described as a cylindrical shape, and the annular member 47 is described as a fixed member, but 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 in which the groove is rectangular instead of cylindrical and the fixing member is U-shaped instead of annular may be considered.

  Further, as shown in FIG. 6, a pressurizing member 48 that can be pressurized in the axial direction is sandwiched between the annular member 47 and the second yoke 44. That is, it is desirable to provide a pressurizing member 48 that applies pressure to both the fixed member (annular member 47) and the yoke (second yoke 44) constituting the magnetic circuit. As a result, it is possible to absorb the play caused by the gap generated 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 an inexpensive high-pressure pump while further downsizing.

DESCRIPTION OF SYMBOLS 1 Pump body 1a Mounting flange 1b Screw hole 1c Press-fit part 1f of relief body to pump body Hole 2 formed in the pump body transversely 2 Plunger 2a Plunger large diameter part 2b Plunger small diameter part 4 Plunger spring 6 Cylinder 6a Cylinder and pump Body fixing portion 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 Contact portion 9 between discharge valve stopper and pump body Pressure pulsation reduction mechanism 9a Pressure pulsation reduction mechanism Holding member 10a Low pressure fuel suction port 10b Low pressure fuel suction port 10c Damper chamber 10d Suction passage 10e Fuel passage 11 Pressurization 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 Suction piping 30 Suction valve 30a Suction valve opening 30b Suction valve biasing spring guide 31 Suction valve seat member 31a Suction valve seat 31b Suction port 32 Suction valve Stopper 32a Passage 32b Suction valve stopper annular projection 32c Suction valve stopper small diameter portion 33 Suction valve biasing spring 35 Rod 35a Rod convex portion 36 Anchor 36a Anchor through hole 36c Anchor magnetic suction surface 36e Between the anchor and the second core Gap 37 Spring seat member 37a Through hole 37b of spring seat member Rod insertion portion 37c of spring seat member Rod insertion hole 38 of spring seat member First core 38b Reverse side 39 of first body pump body fixing portion Second core 39a First Two-core small inner diameter portion 39b Second core magnetic attraction surface 39c Second Groove processing part 40 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 Joining of seal ring to first core Reverse side 50 Connector 51 Suction joint 52 Suction filter 60 Discharge joint 61 O-ring 90 High pressure pump mounting part 92 Tappet 93 Cam mechanism 200 Relief valve 201 Relief body 201a Relief body seat part 202 Valve holder 203 Relief spring 204 Spring stopper 213 Relief Passage 300 Electromagnetic intake valve mechanism

Claims (7)

In a high-pressure fuel supply pump comprising a suction valve mechanism having a suction valve for opening and closing a flow path upstream of the pressurizing chamber and an electromagnetic coil for controlling the opening and closing of the suction valve,
A high-pressure fuel supply pump comprising: a groove formed in the intake valve mechanism; and a fixing member for fixing a yoke constituting a magnetic circuit by being inserted and fixed in the groove. The high-pressure fuel supply pump according to claim 1,
A high-pressure fuel supply pump comprising a pressurizing member that applies pressure to both the fixing member and the yoke constituting the magnetic circuit. The high-pressure fuel supply pump according to claim 1,
The intake valve mechanism includes a fixed core constituting the magnetic circuit,
The high-pressure fuel supply pump, wherein the groove is formed in the fixed core. The high-pressure fuel supply pump according to claim 1,
The suction valve mechanism includes a fixed core constituting the magnetic circuit;
An anchor sucked by the fixed core,
The high-pressure fuel supply pump, wherein the groove is formed in the fixed core toward a radially inner side perpendicular to the moving direction of the anchor. The high-pressure fuel supply pump according to claim 1,
The high-pressure fuel supply pump is characterized in that the fixing member is disposed on the opposite side to the electromagnetic coil with respect to the yoke and restricts the movement of the yoke toward the fixing member. The high-pressure fuel supply pump according to claim 4,
The high-pressure fuel supply pump, wherein the groove is formed in an annular shape with respect to the fixed core, and the fixing member is formed in a substantially 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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