[0001]The present invention relates to a high pressure fuel pump provided with a suction valve mechanism.
Background technology
[0002]
　As a background technique in the present technical field, a high-pressure fuel supply pump described in Japanese Patent Application Laid-Open No. 2017-96216 (Patent Document 1) is known. The high-pressure fuel supply pump of Patent Document 1 includes an electromagnetically driven suction valve mechanism, and paragraph 0018-0021 of Patent Document 1 describes the following configuration. The electromagnetically driven suction valve mechanism comprises an electromagnetically driven plunger rod. A valve is provided at the tip of the plunger rod, and the valve faces the valve seat formed in the valve housing. A plunger rod urging spring is provided at the other end of the plunger rod to urge the plunger rod in the direction away from the valve seat (valve opening direction). A valve stopper is fixed to the outer peripheral portion on the tip side of the valve housing.
The valve stopper is a member that regulates the movement of the valve 203 in the valve opening direction. A valve urging spring is arranged between the valve and the valve stopper, and the valve is urged by the valve urging spring in a direction away from the valve stopper (valve closing direction). The tip of the valve and the plunger rod are urged by their respective springs in opposite directions, but since the plunger rod urging spring is composed of a stronger spring, the plunger rod exerts the force of the valve urging spring. Against this, the valve is pushed away from the valve seat, and as a result, the valve is pressed against the valve stopper.
[0003]
　The plunger rod and valve are not fixed and the tips of the plunger rod are sized so that they can be separated from the valve (paragraph 0045). The valve stopper has a protruding portion having a cylindrical surface portion protruding toward the bottomed tubular portion of the valve in the central portion, and the cylindrical surface portion functions as a guide portion for guiding the axial stroke of the valve. (Paragraph 0047).
Prior art literature
Patent documents
[0004]
Patent Document 1: Japanese Unexamined Patent Publication No. 2017-96216
Outline of the invention
Problems to be solved by the invention
[0005]
　In the high-pressure fuel supply pump of Patent Document 1, the plunger rod of the electromagnetically driven suction valve mechanism and the valve are not fixed, and the valve is guided by an axial stroke by a cylindrical surface portion provided on the protruding portion of the valve stopper. It is a configuration to be done. In this case, in order to stabilize the operation of the valve in the axial direction, it is necessary to lengthen the axial length of the cylindrical surface portion, but if the axial length of the cylindrical surface portion is lengthened, the size of the suction valve mechanism becomes larger. I will invite you. In other words, if the axial length of the cylindrical surface portion is shortened, the linear operation of the valve in the axial direction becomes unstable, and the valve comes into contact with the valve seat in a tilted state. In this case, the seat portion of the valve (suction valve) or the valve seat (suction valve seat) becomes severely worn, the durability of the suction valve mechanism is lowered, and the oiltightness performance is deteriorated at an early stage.
[0006]
　An object of the present invention is to stabilize the operation of the suction valve to suppress deterioration of the durability or oiltightness of the suction valve mechanism.
Means to solve problems
[0007]
　In order to solve the above problems, the high-pressure fuel pump of the present invention includes
　an electromagnetic suction valve mechanism having a suction valve, and the
　suction valve includes a
　rod portion and
　a valve body portion integrally formed with the rod portion. A first guide portion for guiding the outer peripheral portion of
　the rod portion and a
　second guide portion for guiding the outer peripheral portion of the valve body portion are provided.
The invention's effect
[0008]
　According to the present invention, by stabilizing the operation of the suction valve, it is possible to suppress a decrease in the durability or oiltightness of the suction valve mechanism. Other configurations, actions and effects of the present invention will be described in detail in the following examples.
A brief description of the drawing
[0009]
FIG. 1 is an overall configuration diagram of an engine system to which the high-pressure fuel pump according to the present invention is applied.
FIG. 2 is a cross-sectional view showing a vertical cross section (a cross section parallel to the axial direction of the plunger) of a high-pressure fuel pump to which the present invention is applied.
FIG. 3 is a cross-sectional view showing a horizontal cross section (a cross section orthogonal to the axial direction of the plunger) when the high-pressure fuel pump of FIG. 2 is viewed from above.
FIG. 4 is a cross-sectional view showing a vertical cross section (cross section parallel to the axial direction of the plunger) when the high pressure fuel pump of FIG. 2 is viewed from a direction different from that of FIG.
5 is an enlarged cross-sectional view showing the electromagnetic suction valve mechanism of FIG. 2. FIG.
[Fig. 6] Fig. 6 is a diagram for explaining the operation of the intake valve.
FIG. 7 is a diagram showing an example of variations in the configuration of a valve body portion and a guide portion that guides the valve body portion.
FIG. 8 is a diagram showing an example of variations in the configuration of a valve body portion and a guide portion that guides the valve body portion.
Embodiment for carrying out the invention
[0010]
　Hereinafter, examples according to the present invention will be described.
[0011]
　FIG. 1 is an overall configuration diagram of an engine system to which the high-pressure fuel pump 100 according to the present invention is applied. The portion surrounded by the broken line indicates the main body of the high-pressure fuel pump 100 (see FIG. 2), and the mechanism and parts shown in the broken line indicate that the pump body 1 is integrated. Note that FIG. 1 is a drawing schematically showing the operation of the engine system.
[0012]
　In the following description, the vertical direction may be specified, but this vertical direction is based on the vertical direction in FIGS. 2 and 4, and is not necessarily the vertical direction when the high-pressure fuel pump 100 is mounted on the engine. It does not match. Further, in the following description, the axial direction is defined by the central axis 2A of the plunger 2 (see FIG. 2), and this axial direction is parallel to the central axis 2A of the plunger 2 and coincides with the longitudinal direction of the plunger 2.
[0013]
　The fuel in the fuel tank 20 is pumped by the feed pump 21 based on a signal from the engine control unit 27 (hereinafter referred to as an ECU). This fuel is pressurized to an appropriate feed pressure and sent to the low pressure fuel suction port 10a of the high pressure fuel pump 100 through the suction pipe 28. The low pressure fuel suction port 10a is composed of a suction joint 51 (see FIGS. 3 and 4).
[0014]
　The fuel that has passed through the low-pressure fuel suction port 10a reaches the suction port 31b of the electromagnetic suction valve mechanism 300 that constitutes the capacity variable mechanism via the damper chamber (10b, 10c) in which the pressure pulsation reduction mechanism 9 is arranged.
[0015]
　The fuel that has flowed into the electromagnetic suction valve mechanism 300 passes through the suction port (suction passage) that is opened and closed by the suction valve 30 and flows into the pressurizing chamber 11. The engine cam mechanism 93 (see FIGS. 2 and 4) gives the plunger 2 reciprocating power. Due to the reciprocating motion of the plunger 2, fuel is sucked into the pressurizing chamber 11 from the suction port opened and closed by the suction valve 30 in the descending stroke of the plunger 2. The fuel sucked into the pressurizing chamber 11 is pressurized in the ascending stroke. The pressurized fuel is pressure-fed to the common rail 23 to which the pressure sensor 26 is mounted via the discharge valve mechanism 8.
The injector 24 connected to the common rail 23 injects fuel into the engine based on a signal from the ECU 27. The high-pressure fuel pump of this embodiment is a high-pressure fuel pump applied to a so-called direct injection engine system in which the injector 24 injects fuel directly into the cylinder cylinder of the engine. In the high-pressure fuel pump 100, the electromagnetic suction valve mechanism 300 is controlled by a signal sent from the ECU 27, and a desired fuel flow rate is discharged through the fuel discharge port 12.
[0016]
　FIG. 2 is a cross-sectional view showing a vertical cross section (cross section parallel to the axial direction of the plunger 2) of the high pressure fuel pump 100 to which the present invention is applied. FIG. 3 is a cross-sectional view showing a horizontal cross section (a cross section orthogonal to the axial direction of the plunger 2) when the high pressure fuel pump 100 of FIG. 2 is viewed from above. FIG. 4 is a cross-sectional view showing a vertical cross section (cross section parallel to the axial direction of the plunger 2) when the high pressure fuel pump 100 of FIG. 2 is viewed from a direction different from that of FIG.
[0017]
　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 6 to change the volume of the pressurizing chamber 11. Further, the pump body 1 is provided with 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. .. The cylinder 6 is press-fitted with the pump body 1 on the outer peripheral side thereof.
[0018]
　A tappet 92 is provided at the lower end of the plunger 2 to convert the rotational motion of the cam 93 attached to the camshaft of the internal combustion engine into a vertical motion and transmit it to the plunger 2. The plunger 2 is crimped to the tappet 92 by the plunger urging spring 4 via the retainer 15. As a result, the plunger 2 can be reciprocated up and down with the rotational movement of the cam 93.
[0019]
　A suction joint 51 is attached to the side surface of the pump body 1 of the high-pressure fuel pump 100. The suction joint 51 is connected to a low pressure pipe that supplies fuel from the fuel tank 20 to the high pressure fuel pump 100, and the fuel is supplied from the suction joint 51 to the inside of the high pressure fuel pump 100. The suction filter 52 prevents foreign matter existing between the fuel tank 20 and the low pressure fuel suction port 10a from being absorbed into the inside of the high pressure fuel pump 100 by the flow of fuel.
[0020]
　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 passage extending in the vertical direction in the pump body 1. The pressure pulsation reducing mechanism 9 is arranged in the damper chambers 10b and 10c between the damper cover 14 and the upper end surface of the pump body 1.
[0021]
　The fuel that has passed through the damper chambers 10b and 10c then reaches the suction port 31b of the electromagnetic suction valve mechanism 300 via the low pressure fuel suction passage 10d formed by extending in the vertical direction in the pump body 1. The suction port 31b is formed on the suction valve seat member 31 that forms the suction valve seat 31a.
[0022]
　The electromagnetic suction valve mechanism 300 is provided with a terminal 46a. The terminal 46a is integrally molded with the connector 46, and the unmolded end portion can be connected to the engine control unit 27 side.
[0023]
　The electromagnetic suction valve mechanism 300 will be described in detail with reference to FIG.
[0024]
　When in the suction stroke state, 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 stroke, the suction valve 30 is opened. When the suction valve 30 is in the maximum lift state, the suction valve 30 comes into contact with the stopper 32. When the suction valve 30 is lifted, the suction port between the suction valve seat 31a and the suction valve 30 is opened, and the electromagnetic suction valve mechanism 300 is opened. The fuel passes through the suction port between the suction valve seat 31a and the suction valve 30, and flows into the pressurizing chamber 11 through a hole (fuel passage) formed laterally (horizontally) in the pump body 1.
[0025]
　After completing the inhalation stroke, the plunger 2 shifts to the ascending movement and shifts to the ascending stroke. Here, the electromagnetic coil 43 remains in a non-energized state, and no magnetic urging force acts on it. The anchor urging spring 40 urges the anchor 36 in the right direction (valve opening direction) in the figure, and urges the suction valve 30 in the valve opening direction via the anchor 36. The urging force of the anchor urging spring 40 is set so as to have a urging force necessary and sufficient to keep the suction valve 30 open in a state where the electromagnetic coil 43 is not energized. The volume of the pressurizing chamber 11 decreases with the ascending movement of the plunger 2, but in this state, the fuel once sucked into the pressurizing chamber 11 passes through the suction port of the suction valve 30 in the opened state again to the suction passage. Since it is returned to 10d, the pressure in the pressurizing chamber 11 does not increase. This process is called a return process.
[0026]
　In this state, when a control signal from the ECU 27 is applied to the solenoid valve mechanism 300, a current flows through the solenoid coil 43 via the terminal 46 (see FIG. 2). As a result, 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 on the magnetic attraction surface. The magnetic attraction overcomes the urging force of the anchor urging spring 40 to urge the anchor 36 and move the anchor 36 away from the suction valve 30.
[0027]
　At this time, the suction valve 30 is closed by the urging force of the suction valve urging 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 ascending motion of the plunger 2, and when the pressure exceeds the pressure of the fuel discharge port 12, high-pressure fuel is discharged via the discharge valve mechanism 8, and the high-pressure fuel is a common rail. It is supplied to 23. This process is referred to as a discharge process.
[0028]
　That is, the ascending stroke from the lower start point to the upper start point of the plunger 2 consists of a return stroke and a discharge stroke. Then, by controlling the energization timing of the electromagnetic suction valve mechanism 300 to the coil 43, the amount of high-pressure fuel discharged can be controlled.
[0029]
　As shown in FIG. 3, the discharge valve mechanism 8 provided at the outlet of the pressurizing chamber 11 directs the discharge valve seat 8a, the discharge valve 8b that comes into contact with and separates from the discharge valve seat 8a, and the discharge valve 8b toward the discharge valve seat 8a. It is composed of a discharge valve spring 8c for urging and a discharge valve stopper 8d for determining a stroke (moving 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 flow path through which fuel flows from the outside.
[0030]
　When there is no fuel differential pressure between the pressurizing chamber 11 and the discharge valve chamber 12a, the discharge valve 8b is crimped to the discharge valve seat 8a by the urging force of the discharge valve spring 8c, and is in a closed state. 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 fuel discharge port 12 is formed in the discharge joint 60, and the discharge joint 60 is welded and fixed to the pump body 1 by a welded portion 60a.
[0031]
　Next, the relief valve mechanism 200 will be described with reference to FIG.
[0032]
　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. In the relief valve 202, the load of the relief spring 204 is applied via the relief valve holder 203, is pressed against the seat portion of the relief body 201, and shuts off the fuel in cooperation with the seat portion.
[0033]
　When the pressure of the fuel discharge port 12 becomes abnormally high pressure due to a failure of the electromagnetic suction valve mechanism 300 of the high pressure fuel pump 100 and becomes larger than the set pressure of the relief valve mechanism 200, the abnormally high pressure fuel becomes low pressure through the relief passage 213. It is relieved to the damper chamber 10c on the side. In this embodiment, the relief destination of the relief valve mechanism 200 is the damper chamber 10c, but the relief valve mechanism 200 may be configured to be relieved in the pressurizing chamber 11.
[0034]
　The electromagnetic suction valve mechanism 300 will be described in more detail with reference to FIG. FIG. 5 is an enlarged cross-sectional view showing the electromagnetic suction valve mechanism 300 of FIG.
[0035]
　The suction valve 30 is composed of a valve body portion 30A, a rod portion 30B, and a guided portion (convex portion) 30C. In this embodiment, the guided portion 30C is regarded as a part of the valve body portion 30A, and the guided portion 30C is configured as the valve body portion 30A. The outer diameter φ30A of the valve body portion 30A is larger than the outer diameter of the rod portion 30B, the valve body portion 30A constitutes a large diameter portion with respect to the rod portion 30B, and the rod portion 30B has a small diameter portion with respect to the valve body portion 30A. To configure.
[0036]
　The rod portion 30B has a rod shape (round bar shape or columnar shape) having a circular cross section. The valve body portion 30A has a disk shape or a columnar shape in which the thickness dimension D30A in the axial direction (longitudinal direction) of the rod portion 30B is smaller than the outermost diameter φ30A. The axial direction of the rod portion 30B is integrally configured with the valve body portion 30A so as to be orthogonal to the end surface 30A1 of the valve body portion 30A. The rod portion 30B and the valve body portion 30A may be integrally formed, or the member constituting the rod portion 30B and the member constituting the valve body portion 30A may be joined to each other. ..
[0037]
　The end face 30A1 of the valve body portion 30A constitutes a seat portion facing the seat portion 31a formed on the suction valve seat member 31, and is used for the fuel seal portion. Therefore, the seat portion 30A1 of the valve body portion 30A is finished with high surface accuracy (that is, small surface roughness).
[0038]
　The outer cylindrical surface (outer peripheral surface) 30B1 of the rod portion 30B is guided by the guide portion (first guide portion) 31B formed on the suction valve seat member 31 to move the rod portion 30B in the axial direction (longitudinal direction). It constitutes a guide portion (first guided portion). The guide portion 31B is configured as an inner cylindrical surface (inner peripheral surface) formed on the suction valve seat member 31. The outer peripheral surface 30B1 of the rod portion 30B and the inner peripheral surface 31B of the suction valve seat member 31 are finished with high surface accuracy (that is, small surface roughness). As a result, when the rod portion 30B slides on the guide portion 31B, it is possible to prevent the rod portion 30B from sticking to or wearing the inner cylindrical portion of the guide portion 31B.
[0039]
　A convex portion 30C is formed on the surface (end surface) 30A2 of the valve body portion 30A opposite to the seat portion 30A1. A valve stopper 34 is provided on the end surface 30A2 and the convex portion 30C side of the valve body portion 30A. The valve stopper 34 surrounds the valve body portion 30A by the side wall (peripheral wall) 34A2 of the large-diameter recess 34A, and constitutes a valve body housing for accommodating the valve body portion 30A. Further, the valve stopper 34 has at least two stepped recesses when viewed from the suction valve seat member 31 side so as to accommodate the valve body portion 30A and the convex portion 30C.
[0040]
　The bottom surface (opening side recess bottom surface) 34A1 of the large-diameter recess (opening side recess) 34A of the valve stopper 34 abuts on the end surface 30A2 of the valve body portion 30A to limit the movement of the valve body portion 30A in the valve opening direction. It constitutes a stopper portion (stopper surface). The bottom surface (back side recess bottom surface) 34B2 of the small diameter recess (back side recess) 34B of the valve stopper 34 constitutes the spring seat of the suction valve urging spring 33.
[0041]
　The suction valve urging spring 33 is arranged between the small diameter concave bottom surface 34B2 and the end surface 30C1 of the convex portion 30C, and urges the entire suction valve 30 in the valve closing direction via the valve body portion 30A. The suction valve urging spring 33 is in direct contact with the bottom surface 34B2 of the valve stopper 34. The bottom surface 34B2 of the valve stopper 34 is orthogonal to the central axis LA of the guide portion 31B formed on the suction valve seat member 31, and prevents the suction valve urging spring 33 from being tilted and attached.
[0042]
　The valve stopper 34 has one or a plurality of openings (notches) 34D for forming the fuel flow path. The opening (notch) 34D for forming the fuel flow path provided in the valve stopper 34 may have a hole shape or a groove shape.
[0043]
　The inner diameter of the small diameter concave portion 34B of the valve stopper 34 is slightly larger than the outer diameter φ30C of the convex portion 30C, and the outer peripheral surface (guided portion) 30C2 of the convex portion 30C is on the inner cylindrical portion (inner peripheral surface) 34B1 of the small diameter concave portion 34B. Sliding. That is, the outer peripheral surface 30C2 of the convex portion 30C constitutes a guided portion (second guided portion), and the inner peripheral surface 34B1 constitutes a guide portion (guide surface) for guiding the guided portion 30C2. As described above, in the suction valve 30, the guided portion 30C2 of the convex portion 30C provided at one end thereof is guided to move in the axial direction by the guide portion (second guide portion) 34B1 of the valve stopper 34.
[0044]
　The suction valve 30 has a rod portion 30B and a convex portion 30C, which are supported at both ends by a guide portion 31B formed on the suction valve seat member 31 and a guide portion 34B1 formed on the valve stopper 34, respectively, in the radial direction. The movement and tilt range are limited. The guide portion 31B formed on the suction valve seat member 31 and the guide portion 34B1 formed on the valve stopper 34 are provided with clearances for the guided portion 30B1 of the rod portion 30B and the guided portion 30C2 of the convex portion 30C, respectively. The suction valve 30 can slide with respect to the guide portion 31B and the guide portion 34B1 in an environment where the sliding resistance is low.
[0045]
　The suction valve seat member 31 is provided with a fuel seal portion 31a orthogonal to the central axis LA of the guide portion 31B, and is finished with low surface accuracy.
[0046]
　The valve stopper 34 will be described again. The valve stopper 34 has a stopper surface 34A1 and a surface 34E in contact with the suction valve seat member 31, and a valve body portion 30A including a convex portion 30C is housed between these surfaces 34A1 and 34E. Let ΔL be the distance between the surface 34A1 and the surface 34E. Assuming that the thickness of only the valve body portion 30A excluding the convex portion 30C is t30A, the value g1 of ΔL−t30A (see FIG. 6) can be adjusted as the stroke length of the suction valve 30. A tapered portion 34A3 is provided on the valve stopper 34 side of the suction valve 30, and by reducing the contact area between the valve stopper 34 and the valve body portion 30A, the suction valve 30 is prevented from sticking to the valve stopper 34. ing. Further, the fuel passage area is increased by providing the tapered portion 34A3. Further, by providing the tapered portion 34A3, the fluid resistance at the time of valve opening is reduced and the valve opening behavior is stabilized.
[0047]
　The suction valve seat member 31 is press-fitted or inserted into the inner cylindrical portion 1H2 (see FIG. 3) provided in the pump body 1. The valve stopper 34 is press-fitted or inserted into the inner cylindrical portion 1H1 provided in the pump body 1. The inner cylindrical portions 1H1 and 1H2 provided on the pump body 1 are made coaxially, and the better the coaxial accuracy, the higher the coaxial accuracy between the suction valve 30 and the guide portion 31B and the guide portion 34B1.
[0048]
　The smaller the axial length of the guide portion 31B of the suction valve seat member 31, the smaller the sliding area with the suction valve 30 can be suppressed. Further, the smaller the axial length of the guide portion 34B1 of the valve stopper 34, the smaller the sliding area with the suction valve 30 can be suppressed. Further, by making the convex portion 30C spherical, when the suction valve 30 and the seat portion 31a are closed, the suction valve is adjusted to the relative positional deviation between the suction valve 30 and the seat portion 31a after assembly of the parts. The 30 can be tilted, and wear due to one-sided contact of the suction valve 30 and an increase in contact pressure between the corner portion of the guide portion 31B of the suction valve seat member 31 and the rod portion 30B can be suppressed.
[0049]
　FIG. 6 is a diagram for explaining the operation of the suction valve 30. FIG. 6A shows a state at the time of valve opening. FIG. 6B shows a state in which the valve is in the process of transitioning from the opened state to the closed state. FIG. 6C shows a state when the valve is closed.
[0050]
　In the state of FIG. 6A, the gap G1 between the seat portion 30A1 of the valve body portion 30A and the seat portion 31a is the size of g1, and is between the end surface 36A of the anchor 36 and the end surface 39A of the magnetic core 39. The gap G3 of is the size of g2. In this case, g2 is larger than g1 (g2> g1). The end portion 30B2 of the rod portion and the end surface 36B of the anchor 36 are in contact with each other, and the gap G2 between the end portion 30B2 and the end surface 36B is 0 (G2 = 0).
[0051]
　In the state of FIG. 6B, the gap G1 between the seat portion 30A1 of the valve body portion 30A and the seat portion 31a is 0 (G1 = 0), and the end surface 36A of the anchor 36 and the end surface 39A of the magnetic core 39 The gap G3 between them is the size of g3. In this case, g3 is the size obtained by subtracting g1 from g2 (g3 = g2-g1). The end portion 30B2 of the rod portion and the end surface 36B of the anchor 36 are in contact with each other, and the gap G2 between the end portion 30B2 and the end surface 36B is 0 (G2 = 0).
[0052]
　In the state of FIG. 6C, the gap G1 between the seat portion 30A1 of the valve body portion 30A and the seat portion 31a is 0 (G1 = 0), and the end surface 36A of the anchor 36 and the end surface 39A of the magnetic core 39 The gap G3 between them is also 0 (G3 = 0). In this case, the end portion 30B2 of the rod portion and the end surface 36B of the anchor 36 are separated from each other in the direction along the central axis LA, a gap is formed between the end portion 30B2 of the rod portion and the end surface 36B of the anchor 36, and the end portion 30B2. The gap G2 between and the end surface 36B is g3.
[0053]
　A variation in the configuration of the valve body 30A and the guide portion for guiding the valve body 30A will be described. FIGS. 7 and 8 are diagrams showing an example of variations in the configuration of the valve body 30A and the guide portion that guides the valve body 30A.
[0054]
　In FIG. 7, the convex portion 31C is not provided, and the outermost peripheral portion (outer peripheral surface having the largest outer diameter) of the valve body portion 30A is the guided portion 30C2. In this case, 30C2 is not the outer peripheral surface of the convex portion 31C.
In this example, both the first guide portion 31B and the second guide portion 34B1 are composed of the suction valve seat member 31. For example, the portion of the side wall (peripheral wall) 34A2 of the valve stopper 34 may be formed of the suction valve seat member 31. Also in this case, the rod portion 31B is configured with the first guided portion 31B1, and the valve body portion 30A is configured with the second guided portion 30C2. Also in this example, the coaxiality of the first guide portion 31B and the second guide portion 34B1 is maintained. If the coaxiality of the first guide portion 31B and the second guide portion 34B1 is maintained, it is not necessary to provide the first guide portion 31B on the suction valve seat member 31, and other members constituting the first guide portion 31B. May be provided.
[0055]
　In FIG. 8, in FIG. 7, the first guide portion 31B formed on the suction valve seat member 31 is provided on the valve stopper (valve housing) 34 in the same manner as in the embodiment of FIG. In this case, the second guided portion 30C2 is configured in the same manner as in FIG. 7.
[0056]
　In the example described with reference to FIG. 7 or 8, the second guide portion 34B1 provided on the suction valve seat member 31 or the valve stopper (valve housing) 34 may be formed on the pump body 1. In this case, by forming the shape of the valve stopper 34 directly on the pump body 1, it is not necessary to prepare a separate part for the valve stopper 34 and assemble it on the pump body 1. As a result, the efficiency of the assembly work can be increased and the material cost can be reduced.
[0057]
　The features of the high-pressure fuel pump 100 according to this embodiment are listed, for example, the following features.
[0058]
　(1) An electromagnetic suction valve mechanism 300 having a suction valve 30 is provided, and the suction valve 30 guides the rod portion 30B, the valve body portion 30A integrally formed with the rod portion 30B, and the outer peripheral portion 30B1 of the rod portion 30B. A first guide portion 31B and a second guide portion 34B1 for guiding the outer periphery of the valve body portion 30A are provided.
[0059]
　(2) In (1), the second guide portion 34B1 guides the outer circumference of the convex portion 30C formed on the tip end side of the valve body portion 30A.
[0060]
　(3) In (1), the first guide portion 31B and the second guide portion 34B1 are coaxially configured.
[0061]
　(4) In (3), the suction valve seat member 31 on which the valve body portion 30A is seated is provided, and the first guide portion 31B is composed of the suction valve seat member 31.
[0062]
　(5) In (4), a valve body housing portion 34 formed of a suction valve seat member 31 and a separate member is provided, and the second guide portion 34B1 is configured by the valve body housing portion 34.
[0063]
　(6) In (2), the outer diameter φ30C of the convex portion 30C is configured to be smaller than the outermost diameter φ30A of the valve body portion 30A.
[0064]
　(7) In (3), the second guide portion 34B1 is formed on the pump body 1 to which the electromagnetic suction valve mechanism 300 is attached.
[0065]
　(8) In (1), the electromagnetic suction valve mechanism 300 includes an anchor 36 and a magnetic core 39 that mutually generate magnetic attraction, and the anchor 36 and the rod portion 30B come into contact with each other when the valve is opened, and the anchor is anchored when the valve is closed. The 39 and the rod portion 30B are separated from each other, and a gap g3 is generated between the contact portions 36B and 30B2 between the anchor 36 and the rod portion 30B at the time of valve opening.
[0066]
　(9) An electromagnetic suction valve mechanism 300 having an anchor 36, a magnetic core 39, a suction valve 30, and a suction valve seat member 31 is provided, and the suction valve 30 is in contact with the suction valve seat member 31 to seat fuel. A first guide portion 31B that guides the outer peripheral portion 30B1 of the rod portion 30B by fixing the 30A and the rod portion 30B extending from the valve body portion 30A toward the anchor 36 side so as to always operate integrally. A second guide portion 34B1 for guiding the outer periphery of the valve body portion 30A is provided.
[0067]
　In the embodiment according to the present invention, the valve body portion 30A and the rod portion 30B are integrated, and both ends of the seat portion 30A1 of the suction valve 30 are supported, whereby the suction valve 30 at the time of the on-off valve of the suction valve 30 is supported. The inclination of can be limited to a small size. As a result, it is possible to reduce the possibility that the suction valve 30 or the corner portion of the suction valve seat 30A1 comes into contact with the seat portion 31a of the suction valve seat member 31 and damages the seat portion 31a, resulting in deterioration of oiltightness.
[0068]
　According to the present invention, by reducing the inclination of the suction valve 30 in the electromagnetic suction valve mechanism 300, it is possible to suppress a decrease in oiltightness performance, and by reducing the number of components, a high-pressure fuel pump that realizes cost reduction is realized. 100 can be provided.
Description of the sign
[0069]
　30 ... Suction valve, 30A ... Valve body part, 30B ... Rod part, 30B1 ... Outer peripheral part of rod part 30B, 30C ... Convex part, 31 ... Suction valve seat member, 31B ... First guide part, 34 ... Valve stopper (valve) Body housing part), 34B1 ... 2nd guide part, 36 ... anchor, 39 ... magnetic core, 100 ... high pressure fuel pump, 300 ... electromagnetic suction valve mechanism.

WE CLAIMS

The suction valve is provided with an electromagnetic suction valve mechanism having a suction valve, and the
　suction valve includes a
　rod portion,
　a valve body portion integrally formed with the
　rod portion, a first guide portion for guiding an outer peripheral portion of the rod portion, and the
　above -mentioned. A high-pressure fuel pump equipped with a second guide section that guides the outer circumference of the valve body section.
[Claim 2]
　In the high-pressure fuel pump according to claim 1,
　the second guide portion is a high-
　pressure fuel pump that guides the outer periphery of a convex portion formed on the tip end side of the valve body portion.
[Claim 3]
　The high-pressure fuel pump according to claim 1,
　wherein the first guide portion and the second guide portion are coaxially configured.
[Claim 4]
　The high-pressure fuel pump according to claim 3, further
　comprising a suction valve seat member on which the valve body portion is seated, and
　the first guide portion is a high-pressure fuel pump configured by the suction valve seat member.
[Claim 5]
　The high-pressure fuel pump according to claim 4, further
　comprising a valve body housing portion formed of a member different from the suction valve seat member, and
　the second guide portion is a high-pressure fuel pump configured by the valve body housing portion.
[Claim 6]
　The high-pressure fuel pump according to claim 2, wherein the outer diameter of the 　convex portion is smaller than
　the outermost diameter of the valve body portion .
[Claim 7]
　In the high-pressure fuel pump according to claim 3,
　the second guide portion is a high-pressure fuel pump formed in a pump body to which the electromagnetic suction valve mechanism is attached.
[Claim 8]
　In the high-pressure fuel pump according to claim 1, the
　electromagnetic suction valve mechanism includes an anchor and a magnetic core that mutually generate magnetic attraction, and the
　anchor and the rod portion come into contact with each other when the valve is opened, and when the valve is closed. A high-pressure fuel pump in which the anchor and the rod portion are separated from each other and a gap is created between the anchor and the rod portion.
[Claim 9]

　The suction valve is 　provided with an electromagnetic suction valve mechanism having an anchor, a magnetic core, a suction valve and a suction valve seat member, and the suction valve has
　a valve body portion that abuts on the suction valve seat member to seat fuel, and the valve body portion to the above. The rod portion extended toward the anchor side is fixed so as to always operate integrally, and
　the first guide portion that guides the outer peripheral portion of the rod portion and the second guide portion that guides the outer peripheral portion of the
　valve body portion. A high-pressure fuel pump equipped with a part.