JP7180230B2 - high pressure pump - Google Patents

Description

The present invention relates to high pressure pumps.

2. Description of the Related Art Conventionally, a high-pressure pump that pressurizes fuel and supplies it to an internal combustion engine is known. High-pressure pumps generally include a valve member on the low-pressure side of the pressurization chamber. When the valve member is separated from the valve seat, the valve opens to allow the flow of fuel sucked into the pressurizing chamber. do. For example, in the high-pressure pump disclosed in Patent Document 1, when the plunger descends so as to increase the volume of the pressurizing chamber, the valve member opens to suck fuel into the pressurizing chamber. When the plunger rises to reduce the volume of the pressurizing chamber while the valve member is open, the fuel is returned from the pressurizing chamber to the low pressure side, and the fuel pressurized in the pressurizing chamber is metered. be. Further, when the plunger is raised to reduce the volume of the pressurization chamber with the valve member closed, the fuel in the pressurization chamber is pressurized.

Japanese Patent Application Laid-Open No. 2016-133010

In the high-pressure pump of Patent Document 1, the valve member has a plurality of communication holes on a virtual circle centered on the axis. Further, Patent Literature 1 discloses a valve member having a guide portion capable of guiding axial movement of the valve member by sliding on a member forming a suction passage. In this valve member, three guide portions are formed in the circumferential direction of the valve member. In addition, three inclined surfaces inclined with respect to the axis of the valve member are formed in the circumferential direction on the outer edge of the surface of the valve member facing the pressure chamber. This inclined surface is formed between the guide portions.

In the high-pressure pump of Patent Document 1, the inclined surface is formed linearly at the shaft-side edge of the valve member. Therefore, the distance between both ends of the rim and the communication hole is large, and there is a risk that the both ends of the rim will act as resistance to the fuel flowing on the surface of the valve member. As a result, there is a risk that a sufficient flow rate of fuel sucked into the pressurization chamber or fuel returned from the pressurization chamber to the low pressure side cannot be ensured.

SUMMARY OF THE INVENTION An object of the present invention is to provide a high-pressure pump capable of ensuring a sufficient flow rate of fuel sucked into a pressurizing chamber.

<A> A high-pressure pump (10) according to the present invention includes a pressure chamber forming portion (23), suction passage forming portions (21, 35), a seat member (31), and a valve member (40). The pressurization chamber forming portion forms a pressurization chamber (200) in which fuel is pressurized. The suction passage forming portion forms a suction passage (216) through which fuel sucked into the pressurization chamber flows. The seat member includes an inner communicating passage (32) provided in the suction passage and positioned radially inward of the suction passage and communicating between one surface and the other surface of the suction passage; An outer communication passage (33) is provided that communicates between the surface and the other surface. The valve member is provided on the pressurizing chamber side of the seat member, and can allow or restrict the flow of fuel in the communication passage by separating from the seat member to open the valve or by contacting the seat member to close the valve.

The valve member includes a plate-like valve body (41), a plurality of communication holes (44, 441, 442, 443), a tapered portion provided on the radially outer side of the valve body and formed in a tapered shape so that the surface on the pressure chamber side tapers toward the axis (Ax2) of the valve body as it goes from the seat member side toward the pressure chamber side. (42), and a plurality of guide portions (43) protruding radially outward from the valve body so as to divide the tapered portion into a plurality of pieces in the circumferential direction and sliding on the suction passage forming portion to guide the movement of the valve member. have.

A plurality of communication holes are arranged on a virtual circle (VC1) centered on the axis of the valve body. A boundary line (B1) between the inner edge of the tapered portion and the outer edge of the valve body is formed along a concentric circle (CC1) with respect to the virtual circle. Therefore, the distance between both ends of each boundary line and the communication hole can be reduced. As a result, it is possible to suppress the portions in the vicinity of both ends of each boundary line from acting as resistance to the fuel flowing on the surface of the valve member. Therefore, a sufficient flow rate of the fuel sucked into the pressurization chamber can be ensured.
A boundary line between the guide portion and the tapered portion is formed in a curved shape.

1 is a schematic diagram showing a fuel supply system to which a high-pressure pump according to a first embodiment is applied; FIG. Sectional drawing which shows the high pressure pump by 1st Embodiment. Sectional drawing which shows the high pressure pump by 1st Embodiment. FIG. 3 is a sectional view taken along line IV-IV of FIG. 2; FIG. 2 is a cross-sectional view showing the suction valve section and the electromagnetic drive section of the high-pressure pump according to the first embodiment; Sectional drawing which shows the discharge passage part of the high pressure pump by 1st Embodiment. The front view which shows the cylinder of the high-pressure pump by 1st Embodiment. The figure which looked at FIG. 7 from the arrow VIII direction. Sectional drawing which shows the cylinder of the high pressure pump by 1st Embodiment. Sectional drawing which shows the suction-valve part of the high-pressure pump by 1st Embodiment. The figure which shows the seat member of the high-pressure pump by 1st Embodiment. The figure which shows the stopper of the high-pressure pump by 1st Embodiment. The figure which looked at the valve member of the high-pressure pump by 1st Embodiment from the pressurization chamber side. The figure which looked at the valve member of the high-pressure pump by 1st Embodiment from the seat member side. FIG. 13 is a cross-sectional view taken along line XV-XV of FIG. The figure which looked at FIG. 13 from the arrow XVI direction. 5 is a graph showing the relationship between the plate thickness ratio t/D of the valve member of the high-pressure pump according to the first embodiment, the seal surface pressure, and the limit pressure; A cross-sectional view along the line XVIII-XVIII of FIG. FIG. 2 is a schematic cross-sectional view showing the coil of the high-pressure pump according to the first embodiment; FIG. 4 is a schematic cross-sectional view showing a coil according to a first comparative embodiment; FIG. 5 is a schematic cross-sectional view showing a coil according to a second comparative embodiment; The figure which shows the coil of the high pressure pump by 1st Embodiment. The figure which looked at FIG. 22 from the arrow XXIII direction. FIG. 4 is a development view and a cross-sectional view of the outer peripheral wall of the winding forming portion of the high-pressure pump according to the first embodiment; Sectional drawing which shows the discharge joint of the high pressure pump by 1st Embodiment. The figure which looked at FIG. 25 from the arrow XXVI direction. The figure which looked at FIG. 25 from the arrow XXVII direction. Sectional drawing which shows the discharge sheet|seat member of the high-pressure pump by 1st Embodiment. The figure which looked at FIG. 28 from the arrow XXIX direction. The figure which looked at FIG. 28 from the arrow XXX direction. Sectional drawing which shows the intermediate member of the high pressure pump by 1st Embodiment. The figure which looked at FIG. 31 from the arrow XXXII direction. The figure which looked at FIG. 31 from the arrow XXXIII direction. Sectional drawing which shows the relief sheet member of the high-pressure pump by 1st Embodiment. The figure which looked at FIG. 34 from the arrow XXXV direction. The figure which looked at FIG. 34 from the arrow XXXVI direction. Sectional drawing which shows the discharge valve of the high pressure pump by 1st Embodiment. The figure which looked at FIG. 37 from the arrow XXXVIII direction. The figure which looked at FIG. 37 from the arrow XXXIX direction. The figure which shows the relief valve of the high pressure pump by 1st Embodiment. The figure which looked at FIG. 40 from the arrow XLI direction. The figure which looked at FIG. 40 from the arrow XLII direction. The figure which shows the spring which urges the discharge valve of the high pressure pump by 1st Embodiment. The figure which looked at FIG. 43 from the arrow XLIV direction. The figure which shows the spring which urges the relief valve of the high pressure pump by 1st Embodiment. The figure which looked at FIG. 45 from the arrow XLVI direction. The figure which looked at the valve member of the high-pressure pump by 2nd Embodiment from the pressurization chamber side. The figure which looked at the valve member of the high-pressure pump by 2nd Embodiment from the seat member side. The figure which looked at the valve member of the high-pressure pump by 3rd Embodiment from the pressurization chamber side. The figure which looked at the valve member of the high-pressure pump by 3rd Embodiment from the seat member side. The figure which looked at the valve member of the high-pressure pump by 4th Embodiment from the pressurization chamber side. The figure which looked at the valve member of the high-pressure pump by 4th Embodiment from the seat member side. Sectional drawing which shows the discharge passage part of the high pressure pump by 5th Embodiment. Sectional drawing which shows the suction-valve part of the high-pressure pump by 6th Embodiment. Sectional drawing which shows the suction-valve part of the high-pressure pump by 7th Embodiment. Sectional drawing which shows the suction-valve part of the high-pressure pump by 8th Embodiment. Sectional drawing which shows the suction-valve part of the high-pressure pump by 9th Embodiment. Sectional drawing which shows the suction-valve part of the high-pressure pump by 10th Embodiment. Sectional drawing which shows the suction-valve part of the high-pressure pump by 11th Embodiment. The front view which shows the cylinder of the high-pressure pump by 12th Embodiment. The figure which looked at FIG. 60 from the arrow LXI direction. FIG. 21 is a cross-sectional view showing a suction valve portion of a high-pressure pump according to a thirteenth embodiment; The figure which shows the stopper of the high-pressure pump by 14th Embodiment. FIG. 21 is a cross-sectional view showing a suction valve portion and an electromagnetic drive portion of a high-pressure pump according to a fifteenth embodiment; FIG. 21 is a cross-sectional view showing a suction valve portion and an electromagnetic drive portion of a high-pressure pump according to a sixteenth embodiment; FIG. 21 is a cross-sectional view showing a suction valve portion and an electromagnetic drive portion of a high-pressure pump according to a seventeenth embodiment; FIG. 21 is a cross-sectional view showing a suction valve portion and an electromagnetic drive portion of a high-pressure pump according to an eighteenth embodiment; FIG. 21 is a cross-sectional view showing a discharge passage portion of a high-pressure pump according to a nineteenth embodiment; FIG. 11 is a cross-sectional view showing a high-pressure pump according to a twentieth embodiment; FIG. 21 is a front view showing a cylinder of a high-pressure pump according to a twentieth embodiment; The figure which looked at FIG. 70 from the arrow LXXI direction. LXXII-LXXII line sectional view of FIG. Sectional drawing which shows the high pressure pump by a comparative form. FIG. 12 is a cross-sectional view showing a high-pressure pump according to a twenty-first embodiment; FIG. 12 is a cross-sectional view showing a high-pressure pump according to a twenty-second embodiment; FIG. 14 is a cross-sectional view showing a high-pressure pump according to a twenty-third embodiment; FIG. 12 is a cross-sectional view showing a high-pressure pump according to a twenty-fourth embodiment; FIG. 12 is a cross-sectional view showing a high-pressure pump according to a twenty-fifth embodiment; FIG. 21 is a cross-sectional view showing a high-pressure pump according to a twenty-sixth embodiment; FIG. 21 is a cross-sectional view showing a high-pressure pump according to a twenty-seventh embodiment; FIG. 21 is a cross-sectional view showing a high-pressure pump according to a twenty-eighth embodiment; LXXXII-LXXXII line sectional view of FIG. FIG. 21 is a cross-sectional view showing a high-pressure pump according to a twenty-ninth embodiment; FIG. 21 is a cross-sectional view showing a high-pressure pump according to a thirtieth embodiment; FIG. 22 is a front view showing the cylinder of the high-pressure pump according to the 31st embodiment; FIG. 85 is a view of FIG. 85 viewed from the direction of arrow LXXXVI. FIG. 21 is a cross-sectional view showing a high-pressure pump according to a thirty-second embodiment; FIG. 21 is a cross-sectional view showing a high-pressure pump according to a thirty-third embodiment; FIG. 22 is a cross-sectional view showing the supply passage portion of the high-pressure pump according to the thirty-fourth embodiment; The figure which looked at FIG. 89 from the arrow XC direction.

Hereinafter, high-pressure pumps according to multiple embodiments will be described based on the drawings. In addition, the same code|symbol is attached|subjected to the substantially same structural part in several embodiment, and description is abbreviate|omitted. In addition, substantially the same components in multiple embodiments have the same or similar effects.

(First embodiment)
A high pressure pump according to a first embodiment is shown in FIGS.

A high-pressure pump 10 of the present embodiment is applied to a fuel supply system 9 having a fuel injection valve 138 that supplies fuel to an internal combustion engine (hereinafter referred to as "engine") 1 of a vehicle (not shown). The high-pressure pump 10 is attached to the engine head 2 of the engine 1 or to a housing that can be driven by the crankshaft.

As shown in FIG. 1, a fuel tank 132 mounted on a vehicle stores gasoline or the like as fuel. The fuel pump 133 pumps up and discharges the fuel in the fuel tank 132 . A supply fuel pipe 7 connects the fuel pump 133 and the high-pressure pump 10 . As a result, the fuel pumped and discharged by the fuel pump 133 flows into the high-pressure pump 10 via the fuel supply pipe 7 .

The engine 1 is provided with a fuel rail 137 together with the high pressure pump 10 . The engine 1 is, for example, a four-cylinder gasoline engine. A fuel rail 137 is provided on the engine head 2 of the engine 1 . The fuel injection valve 138 is provided such that an injection hole is exposed inside the combustion chamber of the engine 1 . For example, four fuel injection valves 138 are provided according to the number of cylinders of the engine 1 . Four fuel injection valves 138 are connected to the fuel rail 137 .

High pressure pump 10 and fuel rail 137 are connected by high pressure fuel pipe 8 . Fuel flowing into the high-pressure pump 10 from the supply fuel pipe 7 is pressurized by the high-pressure pump 10 and supplied to the fuel rail 137 via the high-pressure fuel pipe 8 . This keeps the fuel in the fuel rail 137 at a relatively high pressure. The fuel injection valve 138 opens and closes according to a command from an ECU (not shown) as a control device, and injects the fuel in the fuel rail 137 into the combustion chamber of the engine 1 . Thus, the fuel injection valve 138 is a so-called direct injection (DI) fuel injection valve.

A sensor 130 is provided on the fuel tank 132 side with respect to the high-pressure pump 10 of the supply fuel pipe 7 . The sensor 130 is capable of detecting the pressure of the fuel in the supply fuel line 7, i.e. the fuel pressure, and the temperature of the fuel, i.e. the fuel temperature, and sending corresponding signals to the ECU. The ECU determines the target pressure of the fuel to be discharged from the fuel pump 133 based on the fuel pressure and the fuel temperature in the supply fuel pipe 7 detected by the sensor 130, and adjusts the fuel so that the fuel at the target pressure is discharged from the fuel pump 133. Controls the operation of the pump 133 motor.

As shown in FIG. 2, the high-pressure pump 10 includes an upper housing 21, a lower housing 22, a fixed portion 25, a cylinder 23, a holder support portion 24, a cover 26, a plunger 11, an intake valve portion 300, an electromagnetic drive portion 500, a discharge A passage portion 700 and the like are provided.

The upper housing 21, the lower housing 22, the fixed portion 25, the cylinder 23, and the holder support portion 24 are made of metal such as stainless steel. Here, the upper housing 21 and the lower housing 22 correspond to "housing".

The upper housing 21 is formed in a substantially octagonal prism shape. The upper housing 21 has an octagonal housing outer peripheral wall 270 . The housing outer peripheral wall 270 has a planar portion 271 . Eight flat portions 271 are formed in the circumferential direction of the housing outer peripheral wall 270 (see FIG. 4).

The upper housing 21 has a hole portion 211 , a suction hole portion 212 , a suction hole portion 213 , a discharge hole portion 214 and a discharge hole portion 215 . The hole 211 is formed to penetrate through the center of the upper housing 21 along the axis of the upper housing 21 in a cylindrical shape.

Suction hole portion 212 is formed in a substantially cylindrical shape so as to extend from one plane portion 271 of housing outer peripheral wall 270 of upper housing 21 toward hole portion 211 . The suction hole portion 213 is formed in a substantially cylindrical shape so as to connect the suction hole portion 212 and the hole portion 211 . The suction hole portion 212 and the suction hole portion 213 are formed coaxially. Also, the axes of the suction hole portions 212 and 213 are perpendicular to the axis of the hole portion 211 . The inner diameter of the suction hole portion 213 is smaller than the inner diameter of the suction hole portion 212 (see FIG. 5). A suction passage 216 is formed inside the suction holes 212 and 213 of the upper housing 21 . Here, the upper housing 21 corresponds to the "intake passage forming portion".

The discharge hole portion 214 is formed in a substantially cylindrical shape so as to extend toward the hole portion 211 from a flat portion 271 on the opposite side of the flat portion 271 in which the suction hole portion 212 is formed in the housing outer peripheral wall 270 of the upper housing 21 . there is The discharge hole portion 215 is formed in a substantially cylindrical shape so as to connect the discharge hole portion 214 and the hole portion 211 . The discharge hole portion 214 and the discharge hole portion 215 are formed coaxially. Also, the axes of the discharge hole portions 214 and 215 are perpendicular to the axis of the hole portion 211 . The inner diameter of the discharge hole portion 215 is smaller than the inner diameter of the discharge hole portion 214 (see FIG. 6). A discharge passage 217 is formed inside the discharge hole portion 214 and the discharge hole portion 215 . Here, the discharge hole portion 214 and the discharge hole portion 215 of the upper housing 21 correspond to the "discharge passage forming portion". Also, the discharge hole portion 215 is smaller than the discharge hole 233 , and the central axis of the discharge hole portion 215 is arranged below the central axis of the discharge hole 233 in the vertical direction.

The suction hole portion 212, the suction hole portion 213, the discharge hole portion 214, and the discharge hole portion 215 are formed coaxially. That is, the suction hole portion 212, the suction hole portion 213, the discharge hole portion 214, and the discharge hole portion 215 have axes on the same plane (see FIGS. 2 to 4).

A housing recess 210 is formed below the upper housing 21 . The housing recessed portion 210 is formed to be recessed in a substantially cylindrical shape from one end surface of the upper housing 21 in the axial direction.

The lower housing 22 is formed in a substantially disc shape. The lower housing 22 has holes 221 and 222 . A housing protrusion 220 is formed above the lower housing 22 . The housing protrusion 220 is formed to protrude in a substantially cylindrical shape from the center of one surface of the lower housing 22 .

The hole portion 221 is formed so as to penetrate through the center of the lower housing 22 and the housing convex portion 220 in a substantially cylindrical shape in the plate thickness direction. Note that the inner diameter of the hole portion 221 is slightly larger than the inner diameter of the hole portion 211 . One hole portion 222 is formed radially outside the hole portion 221 so as to connect the radially outer portion of the housing convex portion 220 on one surface of the lower housing 22 to the other surface.

The lower housing 22 is provided integrally with the upper housing 21 so that the housing convex portion 220 fits into the housing concave portion 210 . The outer diameter of housing protrusion 220 is greater than the inner diameter of housing recess 210 . Therefore, the upper housing 21 and the lower housing 22 are fixed by press-fitting the housing protrusions 220 into the housing recesses 210 . Here, the upper housing 21 and the lower housing 22 are in axial contact with each other at the surface of the upper housing 21 on the lower housing 22 side and the surface of the lower housing 22 on the upper housing 21 side (contact portion 203 shown in FIG. 2). ing.

At the outer edge of the surface of the upper housing 21 on the lower housing 22 side, a relief portion 218 is formed with a tapered surface so as not to block the opening of the hole portion 222 on the upper housing 21 side. are compatible.

The fixed portion 25 is formed integrally with the lower housing 22 so as to extend radially outward in a plate-like shape from the outer edge portion of the lower housing 22 . That is, the fixed portion 25 is connected to the lower housing 22 and the upper housing 21 . In this embodiment, two fixed portions 25 are formed at equal intervals in the circumferential direction of the lower housing 22 . Each of the two fixed portions 25 has one bolt hole 250 . The bolt hole 250 is formed in a substantially cylindrical shape so as to pass through the fixed portion 25 in the plate thickness direction.

When the high-pressure pump 10 is attached to the engine 1, the fixed portion 25 is fixed to the engine head 2 of the engine 1 by bolts 100 provided corresponding to the bolt holes 250 (see FIG. 2). A bolt 100 has a shaft portion 101 and a head portion 102 . The shaft portion 101 is formed in a substantially cylindrical shape. The outer diameter of shaft portion 101 is slightly smaller than the inner diameter of bolt hole 250 .

Head 102 is formed integrally with shaft 101 so as to be connected to one end of shaft 101 . The outer diameter of the head portion 102 is larger than the outer diameter of the shaft portion 101 . When the high-pressure pump 10 is attached to the engine 1 , the shaft portion 101 of the bolt 100 is inserted through the bolt hole 250 of the fixed portion 25 and screwed into the fixing hole portion 120 of the engine head 2 . At this time, an axial force acts from the head portion 102 of the bolt 100 to the fixed portion 25 toward the engine head 2 side. In order to ensure that the lower housing 22 is in close contact with the engine head 2 when the bolt 100 is tightened, at least the flatness around the head 102 of the bolt 100 is appropriately ensured.

The cylinder 23 has a cylinder hole portion 231 . The cylinder hole portion 231 is formed in a substantially cylindrical shape so as to extend from one end face of the columnar member to the other end face side. That is, the cylinder 23 is formed in a bottomed tubular shape having a tubular portion and a bottom portion that closes one end of the tubular portion. A cylindrical inner peripheral wall 230, which is an inner peripheral wall of the cylinder hole portion 231, is formed in a substantially cylindrical shape. The cylindrical inner peripheral wall 230 has a sliding surface 230a, an enlarged diameter surface 230b, and the like. The sliding surface 230 a is formed in a cylindrical shape on the opening side of the tubular inner peripheral wall 230 . The enlarged diameter surface 230b is formed in a cylindrical shape on the side opposite to the opening of the tubular inner peripheral wall 230 with respect to the sliding surface 230a. The sliding surface 230a and the enlarged diameter surface 230b are formed coaxially. The diameter of the enlarged diameter surface 230b is larger than the diameter of the sliding surface 230a.

The outer diameter of the cylinder 23 is slightly larger than the inner diameter of the hole 211 of the upper housing 21 . The cylinder 23 is provided integrally with the upper housing 21 and the lower housing 22 so that it passes through the hole 221 of the lower housing 22 and the outer peripheral wall on the bottom side fits into the hole 211 of the upper housing 21 . The cylinder 23 has a suction hole 232 and a discharge hole 233 . The suction hole 232 is formed to connect the enlarged diameter surface 230 b at the bottom end of the cylinder hole 231 and the suction hole 213 of the upper housing 21 . The discharge hole 233 is formed to connect the enlarged diameter surface 230 b at the bottom end of the cylinder hole 231 and the discharge hole 215 of the upper housing 21 . That is, the suction hole 232 and the discharge hole 233 are formed to face each other with the axis Ax1 of the cylindrical inner peripheral wall 230 of the cylinder hole portion 231 interposed therebetween. That is, the suction holes 232 and the discharge holes 233 are arranged on the same plane (see FIGS. 2 to 4).

The holder support portion 24 is formed to extend in a substantially cylindrical shape from a radially outer portion of the hole portion 221 of the lower housing 22 toward the side opposite to the upper housing 21 . In this embodiment, the holder support portion 24 is formed integrally with the lower housing 22 . The holder support portion 24 is formed coaxially with the cylinder 23 on the radially outer side of one end of the cylinder 23 . When the high-pressure pump 10 is attached to the engine 1, the holder support portion 24 is inserted into the attachment hole portion 3 formed in the engine head 2 (see FIG. 2).

The plunger 11 is made of metal such as stainless steel and has a substantially cylindrical shape. The plunger 11 has a large diameter portion 111 and a small diameter portion 112 . The small diameter portion 112 has an outer diameter smaller than that of the large diameter portion 111 . The plunger 11 is provided such that the large diameter portion 111 side is inserted into the cylinder hole portion 231 of the cylinder 23 . A pressurizing chamber 200 is formed between the bottom wall of the cylinder hole portion 231 and the enlarged diameter surface 230b of the cylindrical inner peripheral wall 230 and the end of the plunger 11 on the large diameter portion 111 side. That is, the cylinder 23 forms a pressurization chamber 200 . In addition, the cylinder 23 has a tubular inner peripheral wall 230 that forms the pressure chamber 200 . Here, the cylinder 23 corresponds to the "pressure chamber forming portion". Pressurization chamber 200 is connected to suction hole 232 and discharge hole 233 .

The outer diameter of the plunger 11 is slightly smaller than the inner diameter of the cylinder 23 , that is, the inner diameter of the cylinder hole portion 231 . Therefore, the plunger 11 can axially reciprocate in the cylinder hole portion 231 while the outer peripheral wall of the large diameter portion 111 slides on the sliding surface 230 a of the cylindrical inner peripheral wall 230 of the cylinder hole portion 231 . When the plunger 11 reciprocates within the cylinder hole portion 231, the volume of the pressurizing chamber 200 increases and decreases. In this manner, the plunger 11 is axially reciprocally movable inside the cylindrical inner peripheral wall 230 such that one end thereof is located in the pressure chamber 200 .

In this embodiment, the seal holder 14 is provided inside the holder support portion 24 . The seal holder 14 is formed in a tubular shape, for example, from metal such as stainless steel. The seal holder 14 is provided such that the outer wall is fitted to the inner wall of the holder support portion 24 . An intermediate cylindrical member 241 is provided between the cylinder 23 and the seal holder 14 . The intermediate cylindrical member 241 is formed in a substantially cylindrical shape and provided coaxially with the cylinder 23 . The inner diameter of the intermediate tubular member 241 is larger than the inner diameter of the cylinder hole portion 231 . Further, the intermediate cylindrical member 241 is formed with a hole portion 242 that connects the inner peripheral wall and the outer peripheral wall. A plurality of holes 242 are formed in the circumferential direction of the intermediate cylindrical member 241 .

The seal holder 14 is provided so as to form a substantially cylindrical space between the inner wall, the end surface of the intermediate cylindrical member 241 opposite to the cylinder 23 , and the outer peripheral wall of the small diameter portion 112 of the plunger 11 . An annular seal 141 is provided in the space. The seal 141 is composed of a fluororesin ring on the radially inner side and a rubber ring on the radially outer side. The seal 141 adjusts the thickness of the fuel oil film around the small-diameter portion 112 of the plunger 11 and suppresses fuel leakage to the engine 1 . An oil seal 142 is provided at the end of the seal holder 14 opposite to the cylinder 23 . The oil seal 142 adjusts the thickness of the oil film around the small diameter portion 112 of the plunger 11 to suppress oil leakage. A variable volume chamber 201 is formed between the step surface between the large diameter portion 111 and the small diameter portion 112 of the plunger 11 and the intermediate cylindrical member 241 and the seal 141, the volume of which changes when the plunger 11 reciprocates. ing.

An annular space 202 is formed between the lower housing 22 , the outer peripheral wall of the cylinder 23 , the inner peripheral wall of the holder support portion 24 , and the seal holder 14 . Annular space 202 connects to hole 222 in lower housing 22 . The annular space 202 is a cylindrical space between the inner peripheral wall of the seal holder 14, the outer peripheral wall of the cylinder 23, and the outer peripheral wall of the intermediate cylindrical member 241, and extends to the variable volume chamber 201 via the hole 242. Connected.

A substantially disc-shaped spring seat 12 is provided at the end of the small diameter portion 112 of the plunger 11 opposite to the large diameter portion 111 . A spring 13 is provided between the seal holder 14 and the spring seat 12 . The spring 13 is, for example, a coil spring, and is provided so that one end abuts the spring seat 12 and the other end abuts the seal holder 14 via the spacer 140 . Since the seal holder 14 is made of a material that can be welded, the hardness of the seal holder 14 is relatively low. The spring 13 urges the plunger 11 to the side opposite to the pressure chamber 200 via the spring seat 12 . When the high-pressure pump 10 is attached to the engine head 2 of the engine 1 , the lifter 5 is attached to the end of the small-diameter portion 112 of the plunger 11 opposite to the large-diameter portion 111 .

When the high-pressure pump 10 is attached to the engine 1 , the lifter 5 abuts on the cam 4 of the camshaft that rotates in conjunction with the drive shaft of the engine 1 . As a result, when the engine 1 is rotating, the rotation of the cam 4 causes the plunger 11 to reciprocate in the axial direction. At this time, the volumes of the pressurization chamber 200 and the volume of the variable volume chamber 201 change periodically.

As shown in FIG. 2, when the plunger 11 is at the bottom dead center, the end of the outer peripheral wall of the large-diameter portion 111 of the plunger 11 opposite to the small-diameter portion 112 is positioned on the enlarged-diameter surface 230b side of the sliding surface 230a. is located on the side of the enlarged diameter surface 230b with respect to the end of the . At this time, the end portion of the outer peripheral wall of the large diameter portion 111 of the plunger 11 on the side of the small diameter portion 112 is opposite to the enlarged diameter surface 230b with respect to the end portion of the slide surface 230a on the side opposite to the enlarged diameter surface 230b. located on the side.

As shown in FIG. 3, when the plunger 11 is at the top dead center, the end of the outer peripheral wall of the large-diameter portion 111 of the plunger 11 opposite to the small-diameter portion 112 is positioned on the enlarged-diameter surface 230b side of the sliding surface 230a. is located on the side of the enlarged diameter surface 230b with respect to the end of the . At this time, the end portion of the outer peripheral wall of the large diameter portion 111 of the plunger 11 on the side of the small diameter portion 112 is opposite to the enlarged diameter surface 230b with respect to the end portion of the slide surface 230a on the side opposite to the enlarged diameter surface 230b. located on the side.

As described above, regardless of the position of the plunger 11 from the bottom dead center to the top dead center, the end of the outer peripheral wall of the large diameter portion 111 of the plunger 11 opposite to the small diameter portion 112 is the sliding surface. The end portion of the large diameter portion 111 of the plunger 11 on the side of the small diameter portion 112 is located on the enlarged diameter surface 230b side of the end portion on the enlarged diameter surface 230b side of the plunger 11. It is located on the side opposite to the enlarged diameter surface 230b with respect to the end on the opposite side.

The cover 26 is made of metal such as stainless steel. The cover 26 has a cover tubular portion 261, a cover bottom portion 262, and the like. The cover tubular portion 261 is formed in a substantially octagonal tubular shape. The cover tube portion 261 has an octagonal cover outer peripheral wall 280 . The cover outer peripheral wall 280 has a planar portion 281 . Eight flat portions 281 are formed in the circumferential direction of the cover outer peripheral wall 280 .

The cover bottom portion 262 is formed integrally with the cover tubular portion 261 so as to close one end of the cover tubular portion 261 . That is, the cover 26 is formed in a cylindrical shape with a bottom. In this embodiment, the cover 26 is formed by pressing a plate-like member, for example. Therefore, the cover 26 has a relatively small thickness. Since the cover 26 does not form a high pressure chamber, the thickness can be reduced.

The cover 26 has cover holes 265 , 266 and 267 . The cover hole portion 265 is formed in a substantially cylindrical shape so as to penetrate the center of the cover bottom portion 262 in the plate thickness direction. The cover hole portion 266 and the cover hole portion 267 are each formed in a substantially cylindrical shape so as to connect the inner peripheral wall of the cover cylindrical portion 261 and the outer peripheral wall, ie, the flat portion 281 of the cover outer peripheral wall 280 . The cover hole portion 266 and the cover hole portion 267 are formed substantially coaxially so as to face each other with the axis of the cover cylinder portion 261 interposed therebetween.

The cover 26 accommodates the upper housing 21 inside, and the end portion of the cover cylindrical portion 261 opposite to the cover bottom portion 262 is provided so as to abut on the surface of the lower housing 22 on the upper housing 21 side. The cover 26 forms a fuel chamber 260 between the upper housing 21 , the lower housing 22 and the cylinder 23 . Here, the end portion of the cover tubular portion 261 and the lower housing 22 are joined over the entire circumferential region by welding, for example. As a result, the space between the cover tubular portion 261 and the lower housing 22 is kept liquid-tight. The cover 26 is provided so that the cover hole 266 and the suction hole 212 of the upper housing 21 correspond, and the cover hole 267 and the discharge hole 214 of the upper housing 21 correspond. Since the operating sound is radiated from the top of the cover 26 , that is, the cover bottom 262 , it is desirable to increase the rigidity of the cover bottom 262 . In the present embodiment, the rigidity of the cover bottom portion 262 is increased by forming the cover bottom portion 262 into a dome shape. may

Thus, the cover 26 covers at least part of the cylinder 23 , the upper housing 21 and the lower housing 22 and forms a fuel chamber 260 between the cylinder 23 , the upper housing 21 and the lower housing 22 . The fuel chamber 260 is formed in a substantially octagonal tubular shape between the inner peripheral wall of the cover tubular portion 261 and the housing outer peripheral wall 270 .

A supply passage portion 29 is provided in the cover 26 . The supply passage portion 29 is formed in a cylindrical shape, and one end thereof is provided so as to be connected to the outer wall surrounding the cover hole portion 265 of the cover bottom portion 262 . The supply passage portion 29 is provided such that the inner space communicates with the fuel chamber 260 via the cover hole portion 265 . Here, the supply passage portion 29 and the cover bottom portion 262 are welded over the entire circumference of the supply passage portion 29 . A supply fuel pipe 7 is connected to the other end of the supply passage portion 29 . As a result, the fuel discharged from the fuel pump 133 flows into the fuel chamber 260 via the fuel supply pipe 7 and the supply passage portion 29 .

As shown in FIG. 5 , the suction valve portion 300 is provided inside the suction holes 212 and 213 of the upper housing 21 , that is, in the suction passage 216 . The intake valve portion 300 has a seat member 31, a stopper 35, a valve member 40, a spring 39, and the like.

The sheet member 31 is made of metal such as stainless steel and is formed in a substantially disk shape. The sheet member 31 is provided in the suction passage 216 so as to be substantially coaxial with the suction hole portion 212 inside the suction hole portion 212 . Here, the outer peripheral wall of the sheet member 31 is press-fitted into the inner peripheral wall of the suction hole portion 212 .

The seat member 31 has a communicating passage 32 , a communicating passage 33 and a valve seat 310 . The communicating passage 32 is formed in a substantially cylindrical shape so as to communicate between one surface and the other surface of the sheet member 31 at the center of the sheet member 31 . Here, the communication path 32 is formed so as to be substantially coaxial with the sheet member 31 .

The communicating path 33 is formed in a substantially cylindrical shape so as to communicate between one surface and the other surface of the sheet member 31 on the radially outer side of the communicating path 32 . A plurality of communication paths 33 are formed in the circumferential direction of the sheet member 31 . In this embodiment, for example, 12 communication paths 33 are formed at regular intervals. Since the communication passages 33 are formed at equal intervals, the fuel flow becomes uniform, and the behavior of the valve member 40, which will be described later, is stabilized. The communication path 33 is arranged on a virtual circle centered on the axis of the sheet member 31. As shown in FIG.

The valve seat 310 is annularly formed around each of the communication passages 32 and the plurality of communication passages 33 on the surface of the seat member 31 on the pressure chamber 200 side. That is, a plurality of valve seats 310 are formed on the surface of the seat member 31 on the pressure chamber 200 side.

The stopper 35 is made of metal such as stainless steel. The stopper 35 is provided on the pressure chamber 200 side with respect to the seat member 31 in the intake passage 216 . The stopper 35 has a stopper small diameter portion 36, a stopper large diameter portion 37, a stopper concave portion 351, a stopper concave portion 352, a stopper convex portion 353, a communication hole 38, and the like.

The stopper small-diameter portion 36 is formed in a substantially cylindrical shape. The outer diameter of the stopper small diameter portion 36 is slightly smaller than the inner diameter of the suction hole portion 213 . The stopper large-diameter portion 37 is formed in a substantially cylindrical shape. The outer diameter of the stopper large-diameter portion 37 is larger than the outer diameter of the stopper small-diameter portion 36 and slightly smaller than the inner diameter of the suction hole portion 212 . The stopper large-diameter portion 37 is formed integrally with the stopper small-diameter portion 36 so as to be coaxial with the stopper small-diameter portion 36 on the opposite side of the stopper small-diameter portion 36 from the pressure chamber 200 .

The stopper 35 is provided in the suction passage 216 so that the small diameter stopper portion 36 is positioned inside the suction hole portion 213 and the large diameter stopper portion 37 is positioned inside the suction hole portion 212 . That is, the stopper 35 is provided in the suction passage 216 so as to be substantially coaxial with the suction hole portions 212 and 213 inside the suction hole portions 212 and 213 .

Here, the annular stepped surface between the stopper small diameter portion 36 and the stopper large diameter portion 37 abuts the annular stepped surface between the suction hole portions 212 and 213 . As a result, movement of the stopper 35 toward the pressure chamber 200 is restricted.

The surface of the stopper large-diameter portion 37 of the stopper 35 on the side opposite to the pressure chamber 200 is in contact with the surface of the sheet member 31 on the pressure chamber 200 side. As a result, movement of the stopper 35 to the side opposite to the pressurizing chamber 200 is restricted.

The stopper recessed portion 351 is formed so as to be recessed in a substantially cylindrical shape from the sheet member 31 side surface of the stopper large diameter portion 37 toward the pressure chamber 200 side. Here, the stopper concave portion 351 is formed so as to be substantially coaxial with the stopper large-diameter portion 37 . The inner diameter of the stopper concave portion 351 is smaller than the outer diameter of the stopper large-diameter portion 37 and larger than the outer diameter of the stopper small-diameter portion 36 .

The stopper recessed portion 352 is formed so as to be recessed in a substantially cylindrical shape from the bottom surface of the stopper recessed portion 351 toward the pressurizing chamber 200 side. Here, the stopper concave portion 352 is formed so as to be substantially coaxial with the stopper concave portion 351 . The inner diameter of the stopper concave portion 352 is smaller than the inner diameter of the stopper concave portion 351 and the outer diameter of the stopper small diameter portion 36 .

The stopper protrusion 353 is formed to protrude in a substantially cylindrical shape from the center of the bottom surface of the stopper recess 352 toward the sheet member 31 . Here, the stopper convex portion 353 is formed so as to be substantially coaxial with the stopper concave portion 352 . Further, the end surface of the stopper protrusion 353 on the sheet member 31 side is located closer to the sheet member 31 than the bottom surface of the stopper recess 351 .

The communication hole 38 is formed in a substantially cylindrical shape so as to communicate between the bottom surface of the stopper concave portion 352 and the pressure chamber 200 side surface of the stopper small-diameter portion 36 on the radially outer side of the stopper convex portion 353 . A plurality of communication holes 38 are formed at equal intervals in the circumferential direction of the stopper small diameter portion 36 . In this embodiment, for example, four communication holes 38 are formed. The communication hole 38 is arranged on an imaginary circle centered on the axis of the small-diameter portion 36 of the stopper.

A suction passage 216 is formed in the communicating passage 32 and the communicating passage 33 of the seat member 31 , the stopper recessed portion 351 and the stopper recessed portion 352 of the stopper 35 , and the communicating hole 38 . Therefore, the fuel in the fuel chamber 260 passes through the communication passage 32, the communication passage 33, the stopper recess 351, the stopper recess 352, the suction passage 216 formed in the communication hole 38, and the suction hole 232 to the pressurization chamber 200. Inflow is possible.

The valve member 40 is provided inside the stopper concave portion 351 , that is, on the pressurizing chamber 200 side of the seat member 31 . The valve member 40 has a valve body 41 , a tapered portion 42 , a guide portion 43 and a communication hole 44 . The valve main body 41, the tapered portion 42, and the guide portion 43 are integrally formed of metal such as stainless steel. The valve body 41 is formed in a substantially disc shape.

The tapered portion 42 is formed integrally with the valve body 41 in a substantially annular shape on the radially outer side of the valve body 41 . The tapered portion 42 is tapered such that the surface on the pressurizing chamber 200 side approaches the axis Ax2 of the valve body 41 as it goes from the seat member 31 side to the pressurizing chamber 200 side.

The guide portion 43 protrudes radially outward from the valve body 41 so as to divide the tapered portion 42 into a plurality of parts in the circumferential direction, and is integrally formed with the valve body 41 and the tapered portion 42 . In the present embodiment, three guide portions 43 are formed at equal intervals in the circumferential direction of the valve body 41 so as to divide the tapered portion 42 into, for example, three pieces in the circumferential direction. Here, the end portion of the guide portion 43 opposite to the valve main body 41 is located radially outside the outer edge portion of the tapered portion 42 . The guide portion 43 can guide the movement of the valve member 40 in the axial direction by sliding the end portion of the guide portion 43 on the side opposite to the valve main body 41 on the inner peripheral wall of the stopper recess portion 351 .

The communication hole 44 is formed to communicate between one surface and the other surface of the valve body 41 . A plurality of communication holes 44 are formed at regular intervals in the circumferential direction of the valve body 41 . In this embodiment, nine communication holes 44 are formed, for example. The communication hole 44 is arranged on an imaginary circle centered on the axis Ax2 of the valve body 41 .

The plate thickness of the valve body 41 and the guide portion 43 of the valve member 40 is smaller than the distance between the surface of the seat member 31 on the pressurizing chamber 200 side and the end surface of the stopper convex portion 353 on the seat member 31 side.
The surface of the valve member 40 on the side of the seat member 31 can contact the surface of the seat member 31 on the side of the pressurizing chamber 200 , that is, the plurality of valve seats 310 , and the center of the surface on the side of the stopper 35 is a stopper projection 353 . can be brought into contact with the end surface of the sheet member 31 side.

The valve member 40 is axially movable within the range of the difference between the plate thickness of the valve main body 41 and the guide portion 43 and the distance between the pressure chamber 200 side surface of the seat member 31 and the end surface of the stopper convex portion 353 on the seat member 31 side. It is possible to move back and forth in the direction.
When the surface of the valve member 40 on the side of the seat member 31 separates from the surface of the seat member 31 on the side of the pressure chamber 200 , that is, the plurality of valve seats 310 , the valve member 40 opens to allow the flow of fuel in the communication passages 32 and 33 . When the surface on the side of the seat member 31 comes into contact with the plurality of valve seats 310 , the valve closes and the flow of fuel in the communication passage 33 can be restricted. In this way, the valve member 40 is a multi-seat type valve body that contacts a plurality of valve seats 310 .

When the valve member 40 opens, fuel is permitted to flow between the communicating passages 32 and 33, the communicating hole 44 and the stopper recess 351, and the fuel on the side of the fuel chamber 260 flows through the communicating passages 32, 33 and 351. It can flow to the pressurizing chamber 200 side via the communicating hole 44 , the stopper concave portion 351 , the stopper concave portion 352 , the communicating hole 38 and the suction hole 232 . Also, the fuel on the pressurization chamber 200 side can flow to the fuel chamber 260 side via the suction hole 232, the communication hole 38, the stopper concave portion 352, the stopper concave portion 351, the communication hole 44, the communication passage 33, and the communication passage 32. can. At this time, the fuel flows through the communication hole 44 of the valve member 40 and around the valve member 40 .

When the valve member 40 closes, the flow of fuel between the communicating passages 32 and 33 and the communicating hole 44 and the stopper concave portion 351 is regulated. Flow to the pressurizing chamber 200 side via the communicating hole 44 , the stopper recessed portion 351 , the stopper recessed portion 352 , the communicating hole 38 , and the suction hole 232 is restricted. Also, the fuel on the pressurization chamber 200 side can flow to the fuel chamber 260 side via the suction hole 232, the communication hole 38, the stopper concave portion 352, the stopper concave portion 351, the communication hole 44, the communication passage 33, and the communication passage 32. Regulated.

The spring 39 is, for example, a coil spring, and is provided radially outside the stopper protrusion 353 . The spring 39 has one end in contact with the bottom surface of the stopper recess 352 and the other end in contact with the surface of the valve member 40 on the pressure chamber 200 side. A spring 39 biases the valve member 40 toward the seat member 31 .

As shown in FIG. 5 , the electromagnetic driving portion 500 is provided so as to protrude radially outward of the cover outer peripheral wall 280 from the intake hole portion 212 of the upper housing 21 via the cover hole portion 266 of the cover 26 .

The electromagnetic drive unit 500 includes a cylindrical member 51, a guide member 52, a needle 53, a spring 54 as an urging member, a movable core 55, a magnetic diaphragm portion 56, a fixed core 57, a coil 60, a yoke 641, a yoke 645, a connector 65, and the like. have.

The tubular member 51 has a first tubular portion 511 , a second tubular portion 512 and a third tubular portion 513 . The first cylindrical portion 511, the second cylindrical portion 512, and the third cylindrical portion 513 are made of, for example, a magnetic material. The first tubular portion 511 is formed in a substantially cylindrical shape.

The second tubular portion 512 is formed in a tubular shape. The second cylindrical portion 512 is formed substantially coaxially and integrally with the first cylindrical portion 511 so that the end portion thereof is connected to the end portion of the first cylindrical portion 511 . The maximum outer diameter of the second tubular portion 512 is smaller than the outer diameter of the end of the first tubular portion 511 on the second tubular portion 512 side.

The third cylindrical portion 513 is formed in a substantially cylindrical shape. The third cylindrical portion 513 is formed substantially coaxially and integrally with the second cylindrical portion 512 so that the end portion thereof is connected to the end portion of the second cylindrical portion 512 opposite to the first cylindrical portion 511 . The outer diameter of the third cylindrical portion 513 is smaller than the maximum outer diameter of the second cylindrical portion 512 .

A screw thread is formed on the outer peripheral wall of the end portion of the first tubular portion 511 opposite to the second tubular portion 512 . A thread groove corresponding to the thread of the first tubular portion 511 is formed in the inner peripheral wall of the suction hole portion 212 of the upper housing 21 at the end opposite to the suction hole portion 213 .

The cylindrical member 51 is provided so that the thread of the first cylindrical portion 511 is screwed into the thread groove of the upper housing 21 . Here, the end face of the first tubular portion 511 of the tubular member 51 on the pressurizing chamber 200 side biases the sheet member 31 and the stopper 35 toward the pressurizing chamber 200 side. Therefore, the sheet member 31 and the stopper 35 are in contact with each other, and movement in the axial direction is restricted. A stepped surface between the stopper small diameter portion 36 and the stopper large diameter portion 37 is pressed against a stepped surface between the suction hole portions 213 and 212 . Therefore, an axial force directed toward the pressure chamber 200 from the stepped surface between the stopper small diameter portion 36 and the stopper large diameter portion 37 acts on the stepped surface between the suction hole portion 213 and the suction hole portion 212 . there is

In addition, the outer peripheral wall of the second tubular portion 512 is formed in a flat tubular shape such as a hexagonal tubular shape. Therefore, when the cylindrical member 51 is screwed into the suction hole portion 212 of the upper housing 21, it is relatively easy to screw the cylindrical member 51 into the suction hole portion 212 by using a tool corresponding to the outer peripheral wall of the second cylindrical portion 512. can be combined.

The tubular member 51 has the first tubular portion 511 positioned inside the cover hole portion 266 of the cover 26 . Therefore, the end portion of the first cylindrical portion 511 on the pressurizing chamber 200 side is positioned inside the cover cylindrical portion 261 , and the end portion of the first cylindrical portion 511 opposite to the pressurizing chamber 200 is located at the second cylindrical portion 512 . , and the third cylindrical portion 513 are positioned outside the cover cylindrical portion 261 . The cylindrical member 51 is provided so that its axis is orthogonal to the axis Ax1 of the cylindrical inner peripheral wall 230 of the cylinder 23 .

The inner diameter of the cylindrical member 51 on the pressurizing chamber 200 side is larger than the inner diameter of the portion on the opposite side of the pressurizing chamber 200 . A substantially annular stepped surface 514 facing the pressurizing chamber 200 is formed inside the cylindrical member 51 . The stepped surface 514 is located slightly closer to the pressurizing chamber 200 with respect to the connecting portion between the first cylindrical portion 511 and the second cylindrical portion 512 in the axial direction of the cylindrical member 51 in order to ensure the thickness.

A hole portion 515 is formed in the first tubular portion 511 to communicate between the inner peripheral wall and the outer peripheral wall. A plurality of holes 515 are formed at regular intervals in the circumferential direction of the first tubular portion 511 . In this embodiment, six holes 515 are formed. The hole portion 515 is positioned generally between the housing outer peripheral wall 270 and the cover outer peripheral wall 280 in the axial direction of the first tubular portion 511 . Therefore, the fuel in the fuel chamber 260 can flow into the first tubular portion 511 through the hole portion 515 and flow toward the pressurization chamber 200 through the suction passage 216 .

A tubular filter 510 is provided inside the first tubular portion 511 at a position corresponding to the hole portion 515 . Filter 510 can collect foreign matter contained in fuel flowing from fuel chamber 260 to pressurization chamber 200 . The filter 510 has an outer peripheral portion on the side of the pressure chamber 200 that is press-fitted into the inner peripheral wall of the first tubular portion 511 , and an end portion on the side opposite to the pressure chamber 200 that is in contact with the guide member 52 . Therefore, the fuel on the fuel chamber 260 side flows into the intake passage 216 only after passing through the filter 510 . The filter 510 is assembled with being slightly crushed in order to make sure it abuts against the guide member 52 .

A welding ring 519 is provided outside the cover 26 and radially outward of the first tubular portion 511 of the tubular member 51 . The weld ring 519 is made of metal, for example, and has a substantially cylindrical shape. The weld ring 519 is formed so that the end on the pressurizing chamber 200 side expands radially outward, and abuts around the cover hole portion 266 of the flat portion 281 of the cover outer peripheral wall 280 . The welding ring 519 is welded to the flat portion 281 of the cover outer peripheral wall 280 over the entire circumferential range at the end on the pressure chamber 200 side, and over the entire circumferential range at the portion opposite to the pressure chamber 200 . It is welded to the outer peripheral wall of the first tubular portion 511 . This prevents the fuel in the fuel chamber 260 from leaking to the outside of the cover 26 through the gap between the cover hole 266 and the outer peripheral wall of the first tubular portion 511 . It should be noted that stress does not act on the weld ring 519 because the screw of the cylindrical member 51 receives the load when the high pressure is applied.

The guide member 52 is provided inside the first tubular portion 511 . The guide member 52 is made of metal or the like and has a substantially cylindrical shape. The guide member 52 is fixed inside the first tubular portion 511 so that the outer peripheral wall fits into the inner peripheral wall of the first tubular portion 511 and the outer edge portion of one end face abuts against the stepped surface 514 of the tubular member 51 . there is A reduced diameter portion 516 is formed at a portion of the inner peripheral wall of the first tubular portion 511 that corresponds to the guide member 52 . The reduced diameter portion 516 is formed on the inner peripheral wall of the first cylindrical portion 511 so as to protrude radially inward. Therefore, the inner peripheral wall of the first cylindrical portion 511 has a smaller inner diameter at the reduced diameter portion 516 . As a result, the guide member 52 is press-fitted into the reduced diameter portion 516 .

The guide member 52 has a shaft hole 521 and a communication hole 522 . The shaft hole 521 is formed so as to axially penetrate through the center of the guide member 52 . Here, the shaft hole 521 is formed so as to be substantially coaxial with the guide member 52 .

The communication hole 522 is formed so as to communicate between the surface on the pressurizing chamber 200 side and the surface on the opposite side from the pressurizing chamber 200 on the radially outer side of the shaft hole 521 . The communication hole 522 communicates the space on the side of the pressure chamber 200 with respect to the guide member 52 and the space on the side opposite to the pressure chamber 200 with respect to the guide member 52 in the space inside the first tubular portion 511 . . The guide member 52 is formed with a tubular portion 523 projecting in a substantially cylindrical shape toward the pressurizing chamber 200 side from the periphery of the shaft hole 521 in the end face on the pressurizing chamber 200 side.

The needle 53 is provided inside the tubular member 51 . The needle 53 is made of metal, for example. The needle 53 has a needle body 531 and a locking portion 532 . The needle body 531 is formed in a substantially columnar shape. The locking portion 532 is formed integrally with the needle body 531 so as to extend radially outward in a substantially annular shape from the outer peripheral wall of the needle body 531 .

The needle 53 is provided such that the needle body 531 is inserted through the shaft hole 521 of the guide member 52 and the engaging portion 532 is positioned on the pressure chamber 200 side with respect to the guide member 52 . The end portion of the needle body 531 on the pressurizing chamber 200 side is positioned inside the communication passage 32 of the seat member 31 and can abut against the surface of the valve member 40 opposite to the pressurizing chamber 200 . The end of the needle body 531 opposite to the pressure chamber 200 is located on the side opposite to the pressure chamber 200 with respect to the end surface of the third cylindrical portion 513 opposite to the second cylindrical portion 512 .

The outer diameter of the portion of the needle body 531 corresponding to the shaft hole 521 is slightly smaller than the inner diameter of the shaft hole 521 . The outer diameter of the locking portion 532 is larger than the outer diameter of the shaft hole 521 . The needle 53 is axially reciprocable inside the tubular member 51 . The outer peripheral wall of needle body 531 is slidable with shaft hole 521 . Therefore, the guide member 52 can guide the movement of the needle 53 in the axial direction. In order to prevent deformation of the end portion of the shaft hole 521 of the guide member 52, the outer peripheral end portion of the guide member 52 is formed with a relief portion that is not press-fitted.

The spring 54 is, for example, a coil spring, and is provided radially outside the needle body 531 . One end of the spring 54 contacts the surface of the guide member 52 on the pressure chamber 200 side, and the other end contacts the surface of the locking portion 532 opposite to the pressure chamber 200 . That is, the locking portion 532 locks the other end of the spring 54 . A spring 54 biases the needle 53 toward the pressure chamber 200 . Also, the biasing force of the spring 54 is greater than the biasing force of the spring 39 . Therefore, the spring 54 urges the valve member 40 toward the pressurizing chamber 200 via the needle 53 and presses the surface of the valve member 40 on the pressurizing chamber 200 side against the stopper convex portion 353 . At this time, the valve member 40 is separated from the valve seat 310 of the seat member 31 and is open.

The movable core 55 is made of, for example, a magnetic material and has a substantially cylindrical shape. The movable core 55 has a shaft hole 553 and a communication hole 554 . The shaft hole 553 is formed so as to axially penetrate through the center of the movable core 55 . Here, the shaft hole 553 is formed so as to be substantially coaxial with the movable core 55 . The inner diameter of the shaft hole 553 is smaller than the outer diameter of the end of the needle body 531 opposite to the pressure chamber 200 .

The movable core 55 is provided integrally with the needle 53 so that the inner peripheral wall of the shaft hole 553 is fitted to the outer peripheral wall of the end of the needle body 531 opposite to the pressure chamber 200 . Here, the movable core 55 is press-fitted into the needle 53 and cannot move relative to the needle 53 . An end face 551 of the movable core 55 opposite to the pressurizing chamber 200 is located substantially on the same plane as an end face of the needle body 531 opposite to the pressurizing chamber 200 .

The communication hole 554 is formed so as to communicate between an end surface 551 opposite to the pressure chamber 200 and an end surface 552 on the pressure chamber 200 side on the radially outer side of the shaft hole 553 . The communication hole 554 reduces the fluid resistance during the reciprocating movement of the movable core 55 and enables highly responsive movement. In addition, the communication hole 554 allows fuel to be supplied to the space between the movable core 55 and the fixed core 57, and by suppressing rapid changes in pressure, it is possible to suppress the occurrence of cavitation erosion. The movable core 55 is formed with a tubular portion projecting in a substantially cylindrical shape from the periphery of the shaft hole 553 of the end face 552 on the pressurizing chamber 200 side toward the pressurizing chamber 200 side.

In addition, in this embodiment, the center of gravity of the integrally provided needle 53 and movable core 55 is always positioned on the axis of the needle 53 and inside the guide member 52 from opening to closing of the valve. Therefore, the axial movement of the integrally provided needle 53 and movable core 55 can be stabilized.

The magnetic throttle portion 56 is made of, for example, a non-magnetic member and has a substantially cylindrical shape. The inner and outer diameters of the magnetic throttle portion 56 are substantially the same as the inner and outer diameters of the third cylindrical portion 513 . The magnetic throttle portion 56 is provided on the side opposite to the pressure chamber 200 with respect to the cylindrical member 51 so as to be substantially coaxial with the third cylindrical portion 513 . The magnetic diaphragm portion 56 and the third cylindrical portion 513 are joined by welding, for example. Here, the end surface 551 of the movable core 55 on the side opposite to the pressure chamber 200 is positioned inside the magnetic throttle portion 56 .

The fixed core 57 is made of, for example, a magnetic material. The stationary core 57 has a stationary core small diameter portion 573 and a stationary core large diameter portion 574 . The fixed core small diameter portion 573 is formed in a substantially cylindrical shape. The outer diameter of the fixed core small diameter portion 573 is slightly larger than the inner diameter of the magnetic throttle portion 56 . The fixed core small diameter portion 573 is press-fitted into the magnetic throttle portion 56 .

The fixed core large diameter portion 574 is formed in a substantially cylindrical shape, and its axial end is connected to the end of the fixed core small diameter portion 573 so as to be coaxial with the fixed core small diameter portion 573 , and is integrated with the fixed core small diameter portion 573 . is formed in The outer diameter of the fixed core large diameter portion 574 is larger than the outer diameter of the fixed core small diameter portion 573 and substantially the same as the outer diameter of the magnetic throttle portion 56 .

The fixed core 57 is provided on the opposite side of the cylindrical member 51 from the pressure chamber 200 so that the fixed core small diameter portion 573 is located inside the end portion of the magnetic throttle portion 56 opposite to the cylindrical member 51 . The fixed core 57 and the magnetic diaphragm portion 56 are joined by welding, for example. Here, the annular step surface between the stationary core small diameter portion 573 and the stationary core large diameter portion 574 abuts on the end surface of the magnetic throttle portion 56 on the side opposite to the tubular member 51 . An end surface 571 of the fixed core 57 on the pressurizing chamber 200 side is located on the pressurizing chamber 200 side with respect to the end surface of the magnetic throttle portion 56 on the side opposite to the cylindrical member 51 . Also, the fixed core 57 is provided so as to be substantially coaxial with the magnetic throttle portion 56 . When the spring 54 biases the needle 53 toward the pressurizing chamber 200 and the valve member 40 is separated from the valve seat 310, the end surface 571 of the fixed core 57 on the pressurizing chamber 200 side and the pressurizing chamber 200 of the movable core 55 are aligned. is formed with the end surface 551 on the opposite side.

In the present embodiment, the tubular member 51, the guide member 52, the spring 54, the needle 53, the movable core 55, the magnetic throttle portion 56, the fixed core 57, and the filter 510 are integrally assembled in advance to form the first electromagnetic drive portion 501. It is sub-assembled to

Specifically, first, the spring 54 and the needle 53 are attached to the guide member 52 , and the movable core 55 is press-fitted into the needle 53 . Subsequently, the magnetic throttle portion 56 is press-fitted into the fixed core small diameter portion 573 of the fixed core 57 and welded, and the magnetic throttle portion 56 and the tubular member 51 are welded together. Subsequently, the guide member 52 described above is press-fitted into the tubular member 51 described above. At this time, the filter 510 is press-fitted inside the first cylindrical portion 511 until the end portion of the filter 510 contacts the end surface of the guide member 52 on the pressure chamber 200 side. Through the steps described above, the subassembly of the first electromagnetic drive unit 501 is completed.

The coil 60 has a spool 61 and a winding portion 62 . The spool 61 is made of resin, for example, and has a substantially cylindrical shape. The spool 61 is positioned radially outside the end of the cylindrical member 51 opposite to the pressurizing chamber 200 and the ends of the movable core 55 , the magnetic restrictor 56 and the fixed core 57 on the pressurizing chamber 200 side. It is provided substantially coaxially with the member 51 . The spool 61 is provided so that at least a part of it in the axial direction is located radially outside the movable core 55 .

Winding portion 62 is formed of winding 620 . The winding 620 is formed in a linear shape from an electrically conductive material such as copper. The winding portion 62 is formed in a substantially cylindrical shape by winding a winding 620 around the outer peripheral wall of the spool 61 . The coil 60 has one virtual outer cylindrical surface 600 passing through the outer peripheral surface of the winding portion 62, and a virtual inner cylindrical surface 601 passing through the inner peripheral surface of the winding portion 62 and having different diameters. It has a cylindrical surface 602 . Here, the spool 61 corresponds to the "winding forming part".

The outer cylindrical surface 600 is formed in a substantially cylindrical shape. The inner cylindrical surface 601 is formed in a substantially cylindrical shape and is located inside the portion of the outer cylindrical surface 600 opposite to the pressurizing chamber 200 . The inner cylindrical surface 602 is formed in a substantially cylindrical shape, and is positioned on the pressure chamber 200 side with respect to the inner cylindrical surface 601 inside the portion of the outer cylindrical surface 600 on the pressure chamber 200 side. The diameter of inner cylindrical surface 602 is larger than the diameter of inner cylindrical surface 601 . Inner cylindrical surface 601 and inner cylindrical surface 602 are located on the outer peripheral wall of spool 61 . In other words, the spool 61 has different outer diameters at a portion on the pressurizing chamber 200 side in the axial direction and a portion on the opposite side from the pressurizing chamber 200 .

The coil 60 has an imaginary connecting surface 605 that connects the inner cylindrical surface 601 and the inner cylindrical surface 602 . The connecting surface 605 is positioned on the outer peripheral wall of the spool 61 and formed so that at least a portion thereof is perpendicular to the axis of the spool 61 . Thus, the winding 620 is wound on the outer peripheral wall of the spool 61 , that is, on the radially outer side of the inner cylindrical surface 601 , the inner cylindrical surface 602 and the connecting surface 605 to form the cylindrical winding portion 62 . is doing.

The yokes 641 and 645 are made of, for example, a magnetic material. The yoke 641 is formed in a cylindrical shape with a bottom. A substantially circular yoke hole 642 is formed in the center of the bottom of the yoke 641 . The inner peripheral wall of the yoke hole 642 at the bottom of the yoke 641 abuts against the outer peripheral wall of the first cylindrical portion 511 , or a small gap is formed between the outer peripheral wall of the first cylindrical portion 511 and the suction force to the extent that the suction force does not decrease. , and the cylindrical portion is provided so as to be positioned radially outward of the coil 60 . Resin is filled between the yoke 641 and the coil 60 .

The yoke 645 is formed in a plate shape and is provided so as to cover the end of the cylindrical portion of the yoke 641 opposite to the bottom. Here, the outer edge portion of the end surface of the yoke 645 on the pressure chamber 200 side is in contact with the cylindrical portion of the yoke 641 . The center of the end face of the yoke 645 on the pressurizing chamber 200 side contacts and is welded to the end face 572 of the fixed core 57 on the side opposite to the pressurizing chamber 200 .

The connector 65 is formed so as to protrude radially outward from a notch formed in a part of the cylindrical portion of the yoke 641 in the circumferential direction (see FIG. 2). The connector 65 has terminals 651 . Terminal 651 is electrically connected to winding 620 of coil 60 . Harness 6 is connected to connector 65 . Thereby, power is supplied to the winding portion 62 of the coil 60 via the harness 6 and the terminal 651 .

In this embodiment, the coil 60 , the yoke 641 , and the connector 65 are pre-assembled integrally to form a sub-assembly to form the second electromagnetic drive section 502 .

Specifically, first, the terminal 651 is press-fitted into the spool 61 . Subsequently, the winding 620 is wound around the spool 61, and the terminal 651 and the winding 620 are welded, that is, fused. Subsequently, in a state in which the spool 61 and the like assembled as described above are inserted into the yoke 641 , resin is filled to form the connector 65 . Subsequently, the outer edge of the yoke 645 is welded to the tubular portion of the yoke 641 . Through the above steps, the sub-assembly of the second electromagnetic drive unit 502 is completed.

A gap is formed between the end surface of the resin portion inside the yoke 641 opposite to the pressurizing chamber 200 and the end surface of the yoke 645 on the pressurizing chamber 200 side. Therefore, the assembling property of the yoke 641 and the yoke 645 is improved. Also, the gap is formed to be small enough to prevent water or the like from passing through. As a result, water or the like can be prevented from entering the yoke 641, and corrosion of the fixed core 57, the tubular member 51, and the like can be suppressed.

The coil 60 generates an electromagnetic force when energized via the harness 6 and the terminal 651 according to a command from the ECU. As a result, a magnetic circuit is formed in the yoke 641 , the yoke 645 , the fixed core 57 , the movable core 55 and the cylindrical member 51 while avoiding the magnetic diaphragm portion 56 . As a result, an attractive force is generated between the fixed core 57 and the movable core 55 , and the movable core 55 is attracted to the fixed core 57 side together with the needle 53 . Therefore, the valve member 40 moves toward the valve seat 310 of the seat member 31 due to the biasing force of the spring 39 . As a result, the valve member 40 contacts the valve seat 310 to close the valve. In this manner, the electromagnetic drive unit 500 generates an electromagnetic force when the coil 60 is energized, generates an attractive force between the fixed core 57 and the movable core 55 , and moves the movable core 55 and the needle 53 to the valve member 40 . The valve member 40 can be closed by moving in the valve closing direction.

In this manner, the coil 60 can generate an attractive force between the fixed core 57 and the movable core 55 by energizing the winding portion 62 to move the movable core 55 and the needle 53 in the valve closing direction. be. It should be noted that when the movable core 55 and the needle 53 move in the valve closing direction, the cylindrical portion 523 of the guide member 52 comes into contact with the engaging portion 532 of the needle 53 . As a result, the movement of the movable core 55 and the needle 53 in the valve closing direction is restricted. The movable core 55 and the fixed core 57 are separated from each other when the cylindrical portion 523 abuts against the locking portion 532 and the movement of the movable core 55 and the needle 53 in the valve closing direction is restricted. That is, in this embodiment, even if the movable core 55 and the needle 53 are attracted toward the fixed core 57, the movable core 55 and the fixed core 57 do not come into contact with each other.

An orifice is provided in the communication hole 522 in order to generate a damper action on the side of the guide member 52 opposite to the pressure chamber 200 . Due to the negative pressure on the side opposite to the damper action, the speed at the time of collision between the cylindrical portion 523 and the locking portion 532 can be reduced, and the NV can be reduced.

When the coil 60 is not energized, the valve member 40 is open and the fuel chamber 260 communicates with the pressure chamber 200 . At this time, when the plunger 11 moves to the side opposite to the pressurization chamber 200, the volume of the pressurization chamber 200 increases, and the fuel in the fuel chamber 260 flows through the hole 515 to the inside of the first tubular portion 511. , and the fuel is sucked into the pressurization chamber 200 via the suction hole 232 . Further, when the plunger 11 moves toward the pressurizing chamber 200 while the valve member 40 is open, the volume of the pressurizing chamber 200 decreases, and the fuel in the pressurizing chamber 200 flows through the suction hole 232. It flows to the valve member 40 side.

When the coil 60 is energized while the plunger 11 is moving toward the pressurizing chamber 200, the valve member 40 closes, blocking the flow of fuel between the fuel chamber 260 and the pressurizing chamber 200. . When the plunger 11 moves further toward the pressurizing chamber 200 while the valve member 40 is closed, the volume of the pressurizing chamber 200 further decreases, and the fuel in the pressurizing chamber 200 is pressurized.

In this manner, the amount of fuel pressurized in the pressurization chamber 200 is adjusted by closing the valve member 40 by the electromagnetic drive unit 500 at an arbitrary timing while the plunger 11 is moving to the pressurization chamber 200 side. be. In this embodiment, the intake valve section 300 and the electromagnetic drive section 500 constitute a normally open type valve device.

In this embodiment, a communication hole 44 is formed in the valve member 40 radially inside the stopper 35 with respect to the center of the communication hole 38 of the stopper 35 . As a result, the return fuel from the pressurizing chamber 200 is branched to the inside and outside of the valve member 40 so as not to self-close. The edge of the valve member 40 on the side of the seat member 31 is chamfered. As a result, the fuel flow becomes smoother and the self-closing limit can be improved.

Further, in the present embodiment, when the fuel injection valve 138 does not inject fuel, that is, when the fuel is cut, the coil 60 is not energized and no fuel is discharged from the high-pressure pump 10 . In this case, the load of the spring 54 is set so that the valve member 40 does not close due to self-closing.

As shown in FIG. 5, when the coil 60 is not energized, that is, when the coil 60 is not energized, the end face 551 of the movable core 55 on the side opposite to the pressure chamber 200, i. is located between the axial center Ci1 of the inner cylindrical surface 601 and the axial center Co1 of the outer cylindrical surface 600, which is an inner cylindrical surface with a small diameter. Further, the end surface 552 of the movable core 55 on the pressure chamber 200 side is located on the fixed core 57 side with respect to the end surface 621 of the winding portion 62 on the pressure chamber 200 side.

In the present embodiment, even when the coil 60 is energized and the movable core 55 is closest to the fixed core 57, the end surface 551 of the movable core 55 on the fixed core 57 side is located between the center Ci1 and the center Co1. located in between. In other words, the end surface 551 of the movable core 55 on the fixed core 57 side is always positioned between the center Ci1 and the center Co1 regardless of the state of energization of the coil 60 .

As shown in FIG. 6 , the discharge passage portion 700 is provided so as to protrude radially outward of the cover outer peripheral wall 280 from the discharge hole portion 214 of the upper housing 21 via the cover hole portion 267 of the cover 26 .

The discharge passage portion 700 includes a discharge joint 70, a discharge seat member 71, an intermediate member 81, a relief seat member 85, a discharge valve 75, a spring 79 as a discharge valve biasing member, a relief valve 91, and a spring as a relief valve biasing member. 99 and a locking member 95 .

The discharge joint 70 is made of metal such as stainless steel and has a substantially cylindrical shape. A screw thread is formed on the outer peripheral wall of the discharge joint 70 at a predetermined distance from one end of the discharge joint 70 to the other end. A thread groove corresponding to the thread of the discharge joint 70 is formed in the inner peripheral wall of the discharge hole 214 of the upper housing 21 at the end opposite to the discharge hole 215 . Discharge joint 70 is provided such that the thread threads into the thread groove of upper housing 21 .

The discharge joint 70 is provided inside the cover hole 267 of the cover 26 . The end of the discharge joint 70 on the side of the pressure chamber 200 is located inside the cover cylinder 261 and the discharge hole 214 , that is, in the discharge passage 217 , and the end opposite to the pressure chamber 200 is the cover. It is positioned outside the cylindrical portion 261 . The discharge joint 70 is provided such that its axis is perpendicular to the axis Ax1 of the cylindrical inner peripheral wall 230 of the cylinder 23 . In this embodiment, the discharge joint 70 is provided substantially coaxially with the cylindrical member 51 .

The inner diameter of the portion of the discharge joint 70 on the pressurizing chamber 200 side is larger than the inner diameter of the portion on the opposite side of the pressurizing chamber 200 . Therefore, a substantially annular stepped surface 701 facing the pressurizing chamber 200 is formed inside the discharge joint 70 . The step surface 701 is located on the side opposite to the pressure chamber 200 with respect to the cover outer peripheral wall 280 .

The discharge joint 70 forms a discharge passage 705 inside. Fuel discharged from the pressurization chamber 200 flows through the discharge passage 705 . Here, the discharge joint 70 corresponds to the "discharge passage forming portion".

The discharge joint 70 is formed with a lateral hole portion 702 that communicates between the inner peripheral wall and the outer peripheral wall. A plurality of lateral holes 702 are formed at regular intervals in the circumferential direction of the discharge joint 70 . In this embodiment, one lateral hole portion 702 is formed. The lateral hole portion 702 is positioned between the housing outer peripheral wall 270 and the cover outer peripheral wall 280 in the axial direction of the discharge joint 70 . Therefore, the fuel in the discharge passage 705 can flow toward the fuel chamber 260 via the relief valve 91 and the lateral hole portion 702, which will be described later.

The discharge seat member 71 has a discharge member body 72 , a discharge hole 73 and a discharge valve seat 74 . The ejection member main body 72 is made of metal, for example, and has a substantially disk shape. The outer diameter of the discharge member body 72 is slightly larger than the inner diameter of the end of the discharge joint 70 on the pressure chamber 200 side. The discharge member main body 72 is provided in the discharge passage 705 such that the outer peripheral wall thereof is press-fitted into the inner peripheral wall of the end portion of the discharge joint 70 on the pressure chamber 200 side.

The discharge member main body 72 is formed with a discharge concave portion 721 , an inner protrusion 722 and an outer protrusion 723 . The ejection recess 721 is formed so as to be recessed in a substantially cylindrical shape toward the pressurization chamber 200 from the center of the end surface of the ejection member main body 72 opposite to the pressurization chamber 200 . The inner projection 722 is formed to protrude in a substantially annular shape from the end surface of the discharge member main body 72 on the pressurizing chamber 200 side toward the pressurizing chamber 200 . The outer protrusion 723 is formed radially outside the inner protrusion 722 so as to protrude in a substantially annular shape from the end surface of the discharge member main body 72 on the pressure chamber 200 side toward the pressure chamber 200 .

The discharge hole 73 is formed in a substantially cylindrical shape so that the end surface of the discharge member main body 72 on the pressurizing chamber 200 side and the bottom surface of the discharge recess 721 on the radially inner side of the inner projection 722 communicate with each other. The discharge valve seat 74 is formed in a substantially annular shape around the discharge hole 73 on the bottom surface of the discharge recess 721 .

The discharge recess 721 , the inner projection 722 , the outer projection 723 , the discharge hole 73 , and the discharge valve seat 74 are formed so as to be substantially coaxial with the discharge member main body 72 . The inner projection 722 and the outer projection 723 are in contact with the periphery of the discharge hole portion 215 on the bottom surface of the discharge hole portion 214 of the upper housing 21 .

The intermediate member 81 has an intermediate member main body 82 and a first flow path 83 . The intermediate member main body 82 is made of metal, for example, and has a substantially disc shape. The intermediate member main body 82 is provided on the side of the discharge sheet member 71 opposite to the pressure chamber 200 in the discharge passage 705 . The outer diameter of the intermediate member main body 82 is slightly smaller than the inner diameter of the end of the discharge joint 70 on the pressure chamber 200 side. The intermediate member main body 82 is provided substantially coaxially with the discharge member main body 72 so that the end face on the pressure chamber 200 side abuts the end face of the discharge member main body 72 on the side opposite to the pressure chamber 200 .

An intermediate recess 821 is formed in the intermediate member main body 82 . The intermediate recessed portion 821 is formed so as to be recessed in a substantially cylindrical shape from the center of the end surface of the intermediate member main body 82 on the pressurizing chamber 200 side toward the side opposite to the pressurizing chamber 200 . The intermediate concave portion 821 is formed so as to be substantially coaxial with the intermediate member main body 82 .

The first flow path 83 is formed in a substantially cylindrical shape so that the end surface of the intermediate member main body 82 on the pressure chamber 200 side and the end surface on the opposite side of the pressure chamber 200 communicate with each other on the radially outer side of the intermediate recessed portion 821 . there is A plurality of first flow paths 83 are formed at equal intervals in the circumferential direction of the intermediate member main body 82 . In this embodiment, for example, five first flow paths 83 are formed. The first flow path 83 communicates with the pressure chamber 200 via the discharge recess 721 , the discharge hole 73 , the discharge hole 215 and the discharge hole 233 .

The relief sheet member 85 has a relief member main body 86 , a relief hole 87 , a relief valve seat 88 , a second flow path 89 , a relief outer peripheral recessed portion 851 , a relief lateral hole 852 and a lateral hole 853 . The relief member body 86 is made of metal, for example. The relief member main body 86 has a relief member tubular portion 861 and a relief member bottom portion 862 .

The relief member tubular portion 861 is formed in a substantially cylindrical shape. The relief member bottom portion 862 is formed integrally with the relief member tubular portion 861 so as to close one end of the relief member tubular portion 861 . That is, the relief member main body 86 is formed in a cylindrical shape with a bottom.

The relief member main body 86 is provided on the side of the intermediate member 81 opposite to the pressure chamber 200 in the discharge passage 705 . The outer diameter of the relief member cylindrical portion 861 is slightly smaller than the inner diameter of the portion of the discharge joint 70 on the pressure chamber 200 side with respect to the step surface 701 . Thus, the relief member main body 86 is provided inside the discharge joint 70 with a clearance fit. In the relief member main body 86, the end surface of the relief member tubular portion 861 on the pressurizing chamber 200 side contacts the outer edge portion of the end surface of the intermediate member main body 82 opposite to the pressurizing chamber 200, and the relief member tubular portion 861 pressurizes. It is provided substantially coaxially with the intermediate member main body 82 so that the outer edge of the end face opposite to the chamber 200 abuts on the stepped surface 701 of the discharge joint 70 .

The relief hole 87 is formed in a substantially cylindrical shape so that the pressure chamber 200 side surface of the relief member bottom portion 862 and the surface opposite to the pressure chamber 200 communicate with each other. The relief valve seat 88 is annularly formed around the relief hole 87 on the pressure chamber 200 side surface of the relief member bottom portion 862 . Here, the relief valve seat 88 is formed in a tapered shape so as to approach the axis of the relief member tubular portion 861 as it goes from the pressure chamber 200 side toward the side opposite to the pressure chamber 200 . The relief hole 87 and the relief valve seat 88 are formed substantially coaxially with the relief member main body 86 .

The second flow path 89 is formed in a substantially cylindrical shape so that the end surface of the relief member cylindrical portion 861 on the pressure chamber 200 side and the end surface on the side opposite to the pressure chamber 200 are communicated with each other. A plurality of second flow paths 89 are formed at regular intervals in the circumferential direction of the relief member tubular portion 861 . In this embodiment, for example, four second flow paths 89 are formed. In this embodiment, the axial length of the intermediate member main body 82 is shorter than the axial length of the relief member cylindrical portion 861 . Therefore, the length of the first channel 83 is shorter than the length of the second channel 89 .

The relief outer peripheral recessed portion 851 is formed in a substantially cylindrical shape so as to be recessed radially inward from the outer peripheral wall of the relief member tubular portion 861 . Here, the relief outer peripheral concave portion 851 communicates with the fuel chamber 260 via the lateral hole portion 702 of the discharge joint 70 . The relief lateral hole 852 is formed in a substantially cylindrical shape so as to communicate between the relief outer peripheral concave portion 851 and the inner peripheral wall of the relief member tubular portion 861 .

The lateral hole 853 is formed in a substantially cylindrical shape so that the relief outer peripheral concave portion 851 and the inner peripheral wall of the relief member cylindrical portion 861 communicate with each other on the pressure chamber 200 side of the relief lateral hole 852 . As a result, the space of the discharge passage 705 on the side opposite to the pressurizing chamber 200 with respect to the relief member bottom portion 862 is connected to the fuel chamber 260 via the relief hole 87, the relief lateral hole 852, the relief outer peripheral recessed portion 851, and the lateral hole portion 702. are in communication.

In this embodiment, an annular groove 800 is formed in the intermediate member 81 . The annular groove 800 is formed in a substantially annular shape so as to be recessed toward the pressure chamber 200 from the end surface of the intermediate member main body 82 opposite to the pressure chamber 200 , that is, the surface of the intermediate member main body 82 facing the relief sheet member 85 . It is The annular groove 800 is formed substantially coaxially with the intermediate member main body 82 . Also, the annular groove 800 connects the ends of all the first flow paths 83 opposite to the pressurizing chamber 200 and the ends of all the second flow paths 89 on the pressurizing chamber 200 side. That is, the first flow path 83 and the second flow path 89 communicate with each other via the annular groove 800 . The first flow path 83 and the second flow path 89 can communicate with each other via the annular groove 800 regardless of how the intermediate member 81 and the relief sheet member 85 rotate relative to each other around the axis. .

As a result, the pressure chamber 200 passes through the discharge hole 233 , the discharge hole portion 215 , the discharge hole 73 , the discharge concave portion 721 , the first flow path 83 , the annular groove 800 , the second flow path 89 , and the discharge passage 705 . It communicates with the space on the side opposite to the pressure chamber 200 with respect to the relief member tubular portion 861 .

When fuel flows between the first flow path 83 and the second flow path 89 via the annular groove 800 , the fuel flows radially through the annular groove 800 . Here, the depth of the annular groove 800 is set to be equal to or greater than the diameter of the first flow path 83 in order to secure the flow path area.

As described above, the discharge joint 70 is provided such that the thread formed on the outer peripheral wall is screwed into the thread groove of the upper housing 21 . A gap is formed between the end portion of the discharge joint 70 on the pressurizing chamber 200 side and the bottom surface of the discharge hole portion 214 . Here, the step surface 701 of the discharge joint 70 biases the relief sheet member 85, the intermediate member 81, and the discharge sheet member 71 toward the pressure chamber 200 side. Therefore, the relief sheet member 85, the intermediate member 81, and the ejection sheet member 71 are in contact with each other, and are restricted from moving in the axial direction. The inner projection 722 and the outer projection 723 of the ejection sheet member 71 are pressed against the step surface between the ejection holes 214 and 215 , that is, around the ejection holes 215 on the bottom surface of the ejection holes 214 . ing. Therefore, an axial force directed toward the pressure chamber 200 from the inner projection 722 and the outer projection 723 acts around the discharge hole portion 215 on the bottom surface of the discharge hole portion 214 .

A polygonal cylindrical surface 703 is formed on the discharge joint 70 . The polygonal tubular surface 703 is formed in a substantially hexagonal tubular shape. The polygonal cylindrical surface 703 is formed on the outer peripheral wall of the discharge joint 70 at a position generally radially outward of the stepped surface 701 in the axial direction. When screwing the discharge joint 70 to the discharge hole 214 of the upper housing 21, the discharge joint 70 can be relatively easily screwed to the discharge hole 214 by using a tool corresponding to the polygonal cylindrical surface 703 of the discharge joint 70. be able to.

A weld ring 709 is provided on the outside of the cover 26 and radially outward of the discharge joint 70 . The weld ring 709 is made of metal, for example, and has a substantially cylindrical shape. The weld ring 709 is formed so that the end on the pressurizing chamber 200 side expands radially outward, and abuts around the cover hole portion 267 of the flat portion 281 of the cover outer peripheral wall 280 . The welding ring 709 is welded to the flat portion 281 of the cover outer peripheral wall 280 over the entire circumferential range at the end on the side of the pressure chamber 200 , and over the entire circumferential range at the portion opposite to the pressure chamber 200 . It is welded to the outer peripheral wall of the discharge joint 70 . This prevents the fuel in the fuel chamber 260 from leaking outside the cover 26 through the gap between the cover hole 267 and the outer peripheral wall of the discharge joint 70 .

A high-pressure fuel pipe 8 is connected to the end of the discharge joint 70 opposite to the pressure chamber 200 . As a result, the fuel that has flowed from the supply fuel pipe 7 through the supply passage portion 29 of the high-pressure pump 10 into the fuel chamber 260 is pressurized in the pressurization chamber 200 and passes through the discharge passage 705 inside the discharge joint 70. is discharged to the high-pressure fuel pipe 8. The high-pressure fuel discharged to the high-pressure fuel pipe 8 is supplied to the fuel rail 137 via the high-pressure fuel pipe 8 .

The discharge valve 75 is provided between the discharge seat member 71 and the intermediate member 81 . The discharge valve 75 is made of metal, for example. The discharge valve 75 has a discharge valve contact portion 76 and a discharge valve sliding portion 77 .

The discharge valve contact portion 76 is formed in a substantially disc shape. The outer diameter of the discharge valve contact portion 76 is smaller than the inner diameter of the discharge recess 721 and larger than the inner diameter of the intermediate recess 821 . The discharge valve contact portion 76 is provided inside the discharge concave portion 721 so that the outer edge of one surface can contact the discharge valve seat 74 or be separated from the discharge valve seat 74 .

The discharge valve 75 opens when the discharge valve contact portion 76 separates from the discharge valve seat 74 to allow fuel to flow through the discharge hole 73 , and closes when the discharge valve contact portion 76 contacts the discharge valve seat 74 to allow fuel to flow through the discharge hole 73 . can be regulated.

The discharge valve sliding portion 77 is formed integrally with the discharge valve contact portion 76 so as to project from the other surface of the discharge valve contact portion 76 in a substantially cylindrical shape. The discharge valve sliding portion 77 is formed substantially coaxially with the discharge valve contact portion 76 . The outer diameter of the discharge valve sliding portion 77 is slightly smaller than the inner diameter of the intermediate recess 821 .

The discharge valve 75 is provided so as to be able to reciprocate in the axial direction while the outer peripheral wall of the discharge valve sliding portion 77 slides on the inner peripheral wall of the intermediate recess 821 . The end of the discharge valve sliding portion 77 opposite to the discharge valve contact portion 76 can contact the outer edge of the bottom surface of the intermediate recess 821 or be separated from the outer edge of the bottom surface of the intermediate recess 821 . The intermediate member 81 can restrict the movement of the discharge valve 75 in the valve opening direction when the discharge valve sliding portion 77 of the discharge valve 75 contacts the bottom surface of the intermediate concave portion 821 .

A hole 771 is formed in the discharge valve sliding portion 77 . The hole portion 771 is formed in a substantially cylindrical shape so as to allow communication between the inner peripheral wall and the outer peripheral wall of the discharge valve sliding portion 77 . A plurality of holes 771 are formed at equal intervals in the circumferential direction of the discharge valve sliding portion 77 . In this embodiment, for example, four holes 771 are formed. The hole portion 771 communicates the inner space and the outer space of the discharge valve sliding portion 77 . Therefore, the discharge valve 75 can smoothly reciprocate in the axial direction. Moreover, even when the discharge valve 75 is in contact with the bottom surface of the intermediate recess 821 of the intermediate member 81 , at least a part of the hole 771 is pressurized more than the end surface of the intermediate member 81 on the pressure chamber 200 side. It is on the room 200 side. In other words, regardless of the position of the reciprocally movable discharge valve 75 between the discharge seat member 71 and the intermediate member 81 , at least a portion of the hole 771 always extends from the end surface of the intermediate member 81 on the pressurizing chamber 200 side. , and communicates the space inside and outside the discharge valve sliding portion 77 .

The spring 79 is, for example, a coil spring and is provided inside the discharge valve sliding portion 77 . The spring 79 has one end in contact with a concave spring seat formed in the center of the bottom surface of the intermediate recess 821 and the other end in contact with the end surface of the discharge valve contact portion 76 on the discharge valve sliding portion 77 side. A spring 79 biases the discharge valve 75 toward the discharge valve seat 74 .

When the pressure of the fuel in the pressurization chamber 200 rises above a predetermined value, the discharge valve 75 moves toward the high-pressure fuel pipe 8 against the biasing force of the spring 79 . As a result, the discharge valve 75 is separated from the discharge valve seat 74 and opened. Therefore, the fuel on the pressurizing chamber 200 side of the discharge sheet member 71 passes through the discharge hole 73, the discharge valve seat 74, the discharge concave portion 721, the first flow path 83, the annular groove 800, and the second flow path 89, and is pressurized. It is discharged to the fuel pipe 8 side.

The relief valve 91 is provided inside the relief member tubular portion 861 . The relief valve 91 is made of metal, for example. The relief valve 91 has a relief valve contact portion 92 , a relief valve sliding portion 93 and a relief valve projecting portion 94 .

The relief valve contact portion 92 is formed in a substantially cylindrical shape. The relief valve contact portion 92 is tapered such that the outer peripheral wall of one end portion approaches the shaft as it goes from the other to the other. The relief valve contact portion 92 is provided so that one end can contact the relief valve seat 88 or can be separated from the relief valve seat 88 .

The relief valve 91 opens when the relief valve contact portion 92 separates from the relief valve seat 88 to allow the flow of fuel through the relief hole 87, and closes when the relief valve seat 88 contacts the relief valve seat 88 to allow fuel to flow through the relief hole 87. can be regulated.

The relief valve sliding portion 93 is formed in a substantially cylindrical shape. The relief valve sliding portion 93 is formed integrally with the relief valve contact portion 92 so that one end thereof is connected to the other end of the relief valve contact portion 92 . The relief valve sliding portion 93 is formed substantially coaxially with the relief valve contact portion 92 . The outer diameter of the relief valve sliding portion 93 is slightly smaller than the inner diameter of the relief member tubular portion 861 . An outer peripheral wall of the relief valve sliding portion 93 can slide with an inner peripheral wall of the relief member cylinder portion 861 .

If the clearance between the outer peripheral wall of the relief valve sliding portion 93 and the inner peripheral wall of the relief member cylindrical portion 861 is too large, fuel pressure may escape through the clearance and the relief valve 91 may close. Therefore, in this embodiment, the size of the clearance is set to such an extent that the fuel pressure does not escape through the clearance.

The relief valve sliding portion 93 has an outer peripheral wall at the end on the relief valve contact portion 92 side that is tapered so as to approach the shaft from the side opposite to the relief valve contact portion 92 toward the relief valve contact portion 92 side. ing. When the relief valve contact portion 92 is in contact with the relief valve seat 88, the relief lateral hole 852 of the relief seat member 85 is closed by the outer peripheral wall of the relief valve sliding portion 93 (see FIG. 6).

The relief valve projecting portion 94 is formed in a substantially cylindrical shape. The relief valve projecting portion 94 is formed integrally with the relief valve sliding portion 93 so that one end thereof is connected to the center of the end surface of the relief valve sliding portion 93 opposite to the relief valve contact portion 92 . The relief valve projecting portion 94 is formed substantially coaxially with the relief valve sliding portion 93 . The outer diameter of the relief valve projecting portion 94 is smaller than the outer diameter of the relief valve sliding portion 93 . When the relief valve contact portion 92 is in contact with the relief valve seat 88, the end surface of the relief valve protruding portion 94 on the pressure chamber 200 side is more relief than the end surface of the relief member cylindrical portion 861 on the pressure chamber 200 side. It is positioned on the member bottom 862 side (see FIG. 6).

The locking member 95 is formed of metal, for example, in a substantially cylindrical shape. The outer diameter of the locking member 95 is slightly larger than the inner diameter of the relief member tubular portion 861 . The locking member 95 is provided inside the relief member tubular portion 861 so that the outer peripheral wall thereof fits into the inner peripheral wall of the relief member tubular portion 861 . That is, the locking member 95 is provided substantially coaxially with the relief member tubular portion 861 . The locking member 95 is positioned near the end of the relief member tubular portion 861 on the pressure chamber 200 side in the axial direction of the relief member tubular portion 861 . Here, the locking member 95 forms a gap with the intermediate member 81 .

The inner diameter of the locking member 95 is larger than the outer diameter of the relief valve projecting portion 94 . When the relief valve contact portion 92 is in contact with the relief valve seat 88, the end surface of the relief valve projecting portion 94 on the pressure chamber 200 side is positioned inside the locking member 95 (see FIG. 6). A substantially cylindrical gap is formed between the inner peripheral wall of the locking member 95 and the outer peripheral wall of the relief valve projecting portion 94 . That is, the inner peripheral wall of the locking member 95 and the outer peripheral wall of the relief valve projecting portion 94 do not slide.

The relief valve 91 is provided so as to be able to reciprocate in the axial direction while the outer peripheral wall of the relief valve sliding portion 93 slides on the inner peripheral wall of the relief member cylindrical portion 861 . The end of the relief valve projecting portion 94 opposite to the relief valve sliding portion 93 contacts the end face of the intermediate member 81 on the relief seat member 85 side, or the end face of the intermediate member 81 on the relief seat member 85 side Separable. The intermediate member 81 can restrict movement of the relief valve 91 in the valve opening direction when the relief valve projecting portion 94 contacts the intermediate member 81 .

When the relief valve contact portion 92 is separated from the relief valve seat 88 by a predetermined distance, the blockage of the relief lateral hole 852 by the outer peripheral wall of the relief valve sliding portion 93 is released. As a result, the relief hole 87 communicates with the fuel chamber 260 via the lateral relief hole 852 , the relief outer peripheral concave portion 851 and the lateral hole portion 702 .

Further, when the relief valve 91 reciprocates in the axial direction inside the relief member tubular portion 861 , the fuel inside the relief member tubular portion 861 can travel between the relief outer peripheral concave portion 851 via the lateral hole 853 . be. Therefore, the relief valve 91 can smoothly reciprocate in the axial direction.

The spring 99 is, for example, a coil spring, and is provided radially outside the relief valve projecting portion 94 . One end of the spring 99 contacts the outer edge of the end surface of the relief valve sliding portion 93 on the side of the pressure chamber 200 , and the other end contacts the end surface of the locking member 95 opposite to the pressure chamber 200 . . That is, the locking member 95 locks the other end of the spring 99 . A spring 99 biases the relief valve 91 toward the relief valve seat 88 side.

In this embodiment, the inner peripheral portion of one end of the spring 99 is guided by the outer peripheral wall of the end of the relief valve projecting portion 94 on the relief valve sliding portion 93 side. In addition, the inner peripheral wall of the relief member cylindrical portion 861 is formed so that the inner diameter of the portion on the pressure chamber 200 side with respect to the sliding portion is larger than the inner diameter of the sliding portion with the relief valve sliding portion 93 . (See Figure 6). This prevents the outer peripheral portion of the spring 99 from coming into contact with the inner peripheral wall of the relief member cylindrical portion 861 , and stabilizes the behavior of the spring 99 and the relief valve 91 .

When the pressure of the fuel on the side of the high-pressure fuel pipe 8 rises to an abnormal value with respect to the relief member bottom portion 862 of the discharge passage 705, the relief valve 91 resists the biasing force of the spring 99 and moves toward the pressure chamber 200 side. Moving. As a result, the relief valve 91 is separated from the relief valve seat 88 and opened. Therefore, the fuel on the side of the high-pressure fuel pipe 8 with respect to the relief member bottom portion 862 of the discharge passage 705 is returned to the fuel chamber 260 side via the relief hole 87 , the relief lateral hole 852 , the relief outer peripheral concave portion 851 and the lateral hole portion 702 . By operating the relief valve 91 in this manner, it is possible to prevent the pressure of the fuel on the high-pressure fuel pipe 8 side from reaching an abnormal value.

As described above, in the present embodiment, when the pressure of the fuel on the side of the high-pressure fuel pipe 8 with respect to the relief member bottom portion 862 of the discharge passage 705 becomes an abnormal value, the fuel is transferred to the pressurization chamber 200 side, which has a high pressure. Instead, it escapes to the low-pressure fuel chamber 260 side.

In this embodiment, the channel area of the lateral hole portion 702 is larger than the channel area of the relief hole 87 when the relief valve 91 is fully opened. Further, the channel area of the lateral relief hole 852 varies depending on the position of the relief valve sliding portion 93 with respect to the lateral relief hole 852 . That is, the relief lateral hole 852 functions as a variable orifice. In this embodiment, the passage area of the lateral hole portion 702 on the downstream side of the lateral relief hole 852 that functions as a variable orifice is larger than the passage area of the relief hole 87 on the upstream side of the lateral relief hole 852 . Therefore, when the pressure of the fuel on the side of the high-pressure fuel pipe 8 becomes an abnormal value, the pressure of the fuel on the side of the high-pressure fuel pipe 8 can be quickly lowered, and the pressure can be stabilized at a lower value. can.

In this embodiment, the ejection sheet member 71, the intermediate member 81, and the relief sheet member 85 are arranged in this order from the pressure chamber 200 toward the outside (see FIG. 6). Therefore, the discharge valve 75 is arranged on the pressure chamber 200 side with respect to the relief valve 91 . Thereby, the dead volume communicating with the pressurization chamber 200 can be reduced.

In this embodiment, the discharge joint 70, the discharge seat member 71, the intermediate member 81, the relief seat member 85, the discharge valve 75, the spring 79, the relief valve 91, the spring 99, and the locking member 95 are integrally assembled in advance to discharge. It is sub-assembled to form the passage portion 700 .

The process of assembling the discharge passage portion 700 is as follows.

First, the relief valve 91 and the spring 99 are inserted inside the relief seat member 85 . Subsequently, the locking member 95 is fitted or press-fitted into the inner peripheral wall of the relief sheet member 85 to adjust the valve opening pressure.

Subsequently, the relief sheet member 85 assembled with the relief valve 91 , the spring 99 and the locking member 95 is inserted inside the discharge joint 70 . Subsequently, the intermediate member 81 is inserted inside the discharge joint 70 .

Subsequently, the spring 79 and the discharge valve 75 are provided in the intermediate recess 821 of the intermediate member 81 . Subsequently, the ejection sheet member 71 is fitted or press-fitted to the inner peripheral wall of the ejection joint 70 .

As described above, the assembly of the discharge passage portion 700, that is, the subassembly is completed. In the discharge passage portion 700 after subassembly, the discharge joint 70 includes a discharge seat member 71, an intermediate member 81, a relief seat member 85, a discharge valve 75, a spring 79, a relief valve 91, a spring 99, and a locking member 95 inside. accommodates Further, the step surface 701 of the discharge joint 70, the relief sheet member 85, the intermediate member 81, and the discharge sheet member 71 are in contact with each other.

As shown in FIGS. 2 to 4, the central axis Axc1 of the electromagnetic drive portion 500 and the central axis Axc2 of the discharge passage portion 700 are located on the same plane. Therefore, it is possible to suppress the increase in size of the high-pressure pump 10 in the direction of the axis Ax1 of the cylindrical inner peripheral wall 230 of the cylinder 23 . Here, the central axis Axc<b>1 of the electromagnetic drive unit 500 coincides with the axis of the cylindrical member 51 . Also, the central axis Axc2 of the discharge passage portion 700 coincides with the axis of the discharge joint 70 .

In this embodiment, the high-pressure pump 10 further includes a pulsation damper 15 , a support member 16 , an upper support 171 and a lower support 172 . The pulsation damper 15 is formed, for example, by joining two disc-shaped thin metal plates together and joining the outer edges thereof by welding. The inside of the pulsation damper 15 is filled with a gas of a predetermined pressure such as nitrogen or argon.

The support member 16 is made of metal, for example, and is formed into a cylindrical shape with a bottom. The support member 16 is provided in the fuel chamber 260 so that the outer edge of the bottom portion contacts the outer edge portion of the cover bottom portion 262 and the outer peripheral wall of the tubular portion contacts the inner peripheral wall of the cover tubular portion 261 . A hole is formed in the center of the bottom of the support member 16 so as to penetrate the bottom in the plate thickness direction.

The upper support 171 and the lower support 172 are each made of metal, for example, and formed in a ring shape. The upper support 171 and the lower support 172 sandwich the pulsation damper 15 so that the outer edges of the upper support 171 and the lower support 172 come into contact with the outer edge of the pulsation damper 15 . Upper support 171 and lower support 172 are welded together at their outer edges. As a result, the pulsation damper 15 , the upper support 171 and the lower support 172 are sub-assembled in advance to form the damper unit 170 .

The damper unit 170 is configured such that the upper support 171 contacts the bottom of the support member 16 and the lower support 172 contacts the surface of the upper housing 21 on the cover bottom 262 side, thereby separating the upper housing 21 and the support member 16 . placed in between. Here, support member 16 , upper support 171 and lower support 172 support pulsation damper 15 in fuel chamber 260 . The lower support 172 is arranged in a recess formed in the end surface of the upper housing 21 opposite to the lower housing 22 . Also, the support member 16 increases the rigidity of the cover 26 and contributes to the reduction of NV. A plurality of holes are formed in the lower support 172 in the circumferential direction, and the fuel spreads above and below the pulsation damper 15 via the holes.

In this embodiment, the joint portion between the cylinder 23 and the upper housing 21 forming the pressurizing chamber 200, the joint portion between the upper housing 21 and the cylindrical member 51, and the joint portion between the upper housing 21 and the discharge joint 70 is located in the fuel chamber 260 , even if high pressure fuel leaks from the pressurization chamber 200 , it can be retained in the fuel chamber 260 .

A “high-pressure chamber” from the valve member 40 to the discharge valve 75 pressurized by sliding of the plunger 11 is formed by the cylinder 23 , the upper housing 21 , the stopper 35 , the valve member 40 and the discharge seat member 71 . A "low pressure chamber" is formed by the lower housing 22, the cover 26, the welding rings 519 and 709, the outer peripheral surface of the discharge joint 70, the seal holder 14 and the seal 141 so as to cover the "high pressure chamber". Therefore, even if fuel leaks from the "high-pressure chamber", it is connected to the "low-pressure chamber" and does not leak to the outside. Also, the "low pressure chamber" and the outside are sealed by welding. Therefore, the fuel does not leak to the outside. Further, the "high pressure chamber" is sealed by the tightening force of the screw of the cylindrical member 51 and the discharge joint 70. As shown in FIG. Therefore, an excessive external force due to high pressure does not act on the welded portion that seals the "low pressure chamber" from the outside.

Next, the cylinder 23 of this embodiment will be described more specifically.

As shown in FIGS. 7-9, the cylinder 23 has a tapered surface 234, an outer peripheral recess 235, and an outer peripheral recess 236. As shown in FIGS.

The tapered surface 234 is formed at the end of the suction hole 232 opposite to the pressure chamber 200 . The tapered surface 234 is formed in a tapered shape so as to separate from the axis of the suction hole 232 as it goes from the pressurizing chamber 200 side toward the side opposite to the pressurizing chamber 200 .

A cylindrical inner peripheral wall 230, which is an inner peripheral wall of the cylinder hole portion 231, has inner tapered surfaces 230c and 230d in addition to a sliding surface 230a and an enlarged diameter surface 230b. The inner tapered surface 230c is formed to connect the sliding surface 230a and the enlarged diameter surface 230b. The inner tapered surface 230c is formed in a tapered shape so as to separate from the axis Ax1 as it goes from the sliding surface 230a side to the enlarged diameter surface 230b side.

The inner tapered surface 230 d is formed to connect the sliding surface 230 a and the opening of the cylindrical inner peripheral wall 230 . The inner tapered surface 230d is formed in a tapered shape so as to separate from the axis Ax1 as it goes from the side of the sliding surface 230a toward the opening of the cylindrical inner peripheral wall 230 .

As shown in FIG. 9, no matter where the plunger 11 is located from the bottom dead center to the top dead center, the end of the outer peripheral wall of the large diameter portion 111 of the plunger 11 opposite to the small diameter portion 112 is sliding. The end portion of the large-diameter portion 111 of the plunger 11 on the small-diameter portion 112 side is located on the enlarged-diameter surface 230b side of the end portion on the enlarged-diameter surface 230b side of the sliding surface 230a. It is located on the side opposite to the enlarged diameter surface 230b with respect to the end on the side opposite to the surface 230b. That is, regardless of the position of the plunger 11, the sliding surface 230a can slide on the outer peripheral wall of the large diameter portion 111 over the entire range in the axial direction.

When the plunger 11 is provided inside the cylindrical inner peripheral wall 230, an annular gap is formed between the outer peripheral wall of the large diameter portion 111 of the plunger 11 and the inner tapered surfaces 230c and 230d. Therefore, when the plunger 11 reciprocates inside the cylindrical inner peripheral wall 230, fuel in the gap is guided between the outer peripheral wall of the large diameter portion 111 and the sliding surface 230a. This facilitates formation of an oil film between the outer peripheral wall of the large-diameter portion 111 and the sliding surface 230a, thereby suppressing uneven wear and seizure between the outer peripheral wall of the large-diameter portion 111 and the sliding surface 230a. .

Here, the angles of the inner tapered surfaces 230c and 230d with respect to the axis Ax1 and the outer peripheral wall of the large diameter portion 111 are set to, for example, 10 degrees or less. The corners of both ends in the axial direction of the large diameter portion 111 of the plunger 11 are chamfered.

The outer peripheral recessed portion 235 and the outer peripheral recessed portion 236 are each formed to be recessed to a predetermined depth radially inward from the outer peripheral wall of the cylinder 23 . The outer peripheral recessed portion 235 is formed in a range that includes the entire intake hole 232 , that is, the tapered surface 234 in the circumferential direction of the cylinder 23 . In addition, when viewed from the axial direction of the suction hole 232 , the outer peripheral recessed portion 235 extends from a position slightly on the bottom side of the cylinder 23 with respect to the axis of the suction hole 232 to the lower end of the tapered surface 234 in the axial direction of the cylinder 23 . It is formed in a range up to a position a predetermined distance away from the bottom of 23 . The outer peripheral recessed portion 235 is formed to have a substantially rectangular shape when viewed from the axial direction of the suction hole 232 . At least a portion of the outer peripheral recessed portion 235 is formed in a range that overlaps with the sliding surface 230a in the axially lower portion of the cylinder 23 when viewed from the axial direction of the suction hole 232 (see FIG. 7).

The outer peripheral recessed portion 236 is formed in a range that includes all the discharge holes 233 in the circumferential direction of the cylinder 23 . In addition, when viewed from the axial direction of the discharge hole 233 , the outer peripheral concave portion 236 extends from a position slightly on the bottom side of the cylinder 23 with respect to the axis of the discharge hole 233 to the lower end of the discharge hole 233 in the axial direction of the cylinder 23 . It is formed in a range up to a position a predetermined distance away from the bottom of 23 . The outer peripheral recessed portion 236 is formed to have a substantially rectangular shape when viewed from the axial direction of the discharge hole 233 . At least a portion of the outer peripheral recessed portion 236 is formed in a range that overlaps with the sliding surface 230a in the axial lower portion of the cylinder 23 when viewed from the axial direction of the discharge hole 233 (see FIG. 8).

In addition, when viewed from the axial direction of the suction hole 232 or the discharge hole 233, the outer peripheral recesses 235 and 236 are formed so as to leave a fitting portion with the upper housing 21, i.e., a shrink-fit portion at the axially upper portion of the cylinder 23. formed in a range (see FIGS. 7 and 8).

As described above, when the cylindrical member 51 of the electromagnetic drive unit 500 is screwed to the suction hole portion 212 of the upper housing 21, the stepped surface between the suction hole portions 213 and 212 has the stopper small diameter portion 36 and the stopper small diameter portion 36. An axial force directed toward the pressurizing chamber 200 side acts from the stepped surface between the large-diameter portion 37 of the stopper. Therefore, the inner peripheral wall of the hole portion 211 of the upper housing 21 may slightly deform radially inward around the suction hole portion 213 . However, in this embodiment, since the outer peripheral recessed portion 235 is formed in the outer peripheral wall of the cylinder 23 at a position corresponding to the suction hole portion 213, even if the inner peripheral wall of the hole portion 211 of the upper housing 21 is deformed radially inward, Also, it is possible to suppress the surface pressure caused by the deformation acting on the outer peripheral wall of the cylinder 23 . As a result, it is possible to suppress radially inward deformation of the cylindrical inner peripheral wall 230 of the cylinder hole portion 231 . Therefore, the clearance between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be kept constant, and uneven wear and seizure between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be suppressed.

Further, the axial force described above causes the inner peripheral wall of the hole 211 of the upper housing 21 to deform radially inward, thereby increasing the surface pressure at the boundary of the outer peripheral recessed portion 235 of the cylinder 23 . It becomes easy to cope with high pressure.

Further, when the discharge joint 70 of the discharge passage portion 700 is screwed to the discharge hole portion 214 of the upper housing 21 , pressure is applied from the inner projection 722 and the outer projection 723 around the discharge hole portion 215 on the bottom surface of the discharge hole portion 214 . An axial force directed toward the chamber 200 acts. Therefore, the inner peripheral wall of the hole portion 211 of the upper housing 21 may slightly deform radially inward around the discharge hole portion 215 . However, in this embodiment, since the outer peripheral recessed portion 236 is formed in the outer peripheral wall of the cylinder 23 at a position corresponding to the discharge hole portion 215, even if the inner peripheral wall of the hole portion 211 of the upper housing 21 is deformed radially inward, Also, it is possible to suppress the surface pressure caused by the deformation acting on the outer peripheral wall of the cylinder 23 . As a result, it is possible to suppress radially inward deformation of the cylindrical inner peripheral wall 230 of the cylinder hole portion 231 . Therefore, the clearance between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be kept constant, and uneven wear and seizure between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be suppressed.

Furthermore, the axial force described above causes the inner peripheral wall of the hole 211 of the upper housing 21 to deform radially inward, thereby increasing the surface pressure at the boundary of the outer peripheral concave portion 236 of the cylinder 23 , thereby increasing the pressure in the pressurizing chamber 200 . It becomes easy to cope with high pressure.

Next, assembly of the high-pressure pump 10 will be described.

The high-pressure pump 10 is assembled, for example, in the following steps.

First, the cylinder 23 is inserted into the hole 221 of the lower housing 22 .

Subsequently, the cylinder 23 is inserted together with the lower housing 22 into the hole 211 of the upper housing 21 so that the suction hole 232 corresponds to the suction hole 213 and the discharge hole 233 corresponds to the discharge hole 215 . Here, the cylinder 23 is inserted into the hole portion 211 in a state where the upper housing 21 is heated in advance and the inner diameter of the hole portion 211 is expanded. When the upper housing 21 cools, the inner diameter of the hole 211 is reduced and the upper housing 21 and the cylinder 23 are fixed. Similarly, the upper outer diameter portion of the lower housing 22 and the lower inner diameter portion of the upper housing 21 are reduced and fixed to the upper housing 21 . That is, the cylinder 23 and the lower housing 22 are fixed to the upper housing 21 by shrink fitting or cooling fitting. At this time, the lower housing 22 is locked between the upper end of the outermost diameter of the cylinder 23 and the lowermost end of the upper housing 21, so that the upper housing 21, the lower housing 22, and the cylinder 23 is defined in the vertical direction and assembled integrally with the upper housing 21 .

Subsequently, the stopper 35 is inserted into the suction holes 213 and 212 . Subsequently, the spring 39 is placed in the stopper recess 352 and the valve member 40 is placed in the stopper recess 351 . Subsequently, the sheet member 31 is press-fitted into the stopper 35 of the suction hole portion 212 on the side opposite to the pressurizing chamber 200 , and both end surfaces of the stopper 35 are brought into contact with the concave portion of the upper housing 21 and the sheet member 31 . Here, the sliding portion 430 of the valve member 40 overlaps the inner peripheral wall of the stopper concave portion 351 when the spring 39 is in the natural length state. Therefore, it is possible to improve the assemblability.

Subsequently, the damper unit 170 consisting of the pulsation damper 15 , the upper support 171 and the lower support 172 is arranged in the concave portion of the upper housing 21 , that is, on the side opposite to the lower housing 22 .

Subsequently, the upper housing 21 is covered with the cover 26 provided with the support member 16 in advance. Here, the cover 26 is arranged so that the cover hole portion 266 corresponds to the suction hole portion 212 and the cover hole portion 267 corresponds to the discharge hole portion 214 .

Subsequently, the sub-assembled first electromagnetic drive portion 501 is inserted into the cover hole portion 266 , and the tubular member 51 is screwed to the intake hole portion 212 of the upper housing 21 . At this time, a tool (not shown) corresponding to the second cylindrical portion 512 of the cylindrical member 51 is used to screw the cylindrical member 51 and the suction hole portion 212 together. As a result, an axial force from the cylindrical member 51 toward the pressure chamber 200 acts on the step surface between the seat member 31 , the stopper 35 , and the suction hole portions 212 and 213 of the upper housing 21 .

Subsequently, the sub-assembled discharge passage portion 700 is inserted into the cover hole portion 267 , and the discharge joint 70 is screwed to the discharge hole portion 214 of the upper housing 21 . At this time, the discharge joint 70 and the discharge hole portion 214 are screwed together using a tool (not shown) corresponding to the polygonal cylindrical surface 703 of the discharge joint 70 . As a result, the relief sheet member 85 , the intermediate member 81 , the discharge sheet member 71 , and the discharge holes 214 and 215 of the upper housing 21 are separated from the discharge joint 70 from the discharge joint 70 to the pressure chamber. An axial force acts on the 200 side.

Subsequently, the end portion of the tubular cover portion 261 opposite to the cover bottom portion 262 is welded to the lower housing 22 over the entire circumferential region of the tubular cover portion 261 . Subsequently, the weld ring 709 is arranged radially outside the discharge joint 70 , and the weld ring 709 is welded to the cover outer peripheral wall 280 and the outer peripheral wall of the discharge joint 70 over the entire circumferential direction of the weld ring 709 . Next, the weld ring 519 is arranged radially outward of the first tubular portion 511 of the tubular member 51 , and the weld ring 519 and the cover outer peripheral wall 280 and the outer peripheral wall of the first tubular portion 511 are arranged in the circumferential direction of the weld ring 519 . Weld over the entire area.

Subsequently, the seal 141, the intermediate cylindrical member 241, and the plunger 11 are inserted into the seal holder 14 in this order, and after the seal holder 14 is assembled inside the holder support portion 24, the whole area in the circumferential direction is welded. Subsequently, the oil seal 142 is assembled to the seal holder 14 .

Subsequently, the seal member 240 is assembled to the holder support portion 24 . Subsequently, the spacer 140 is arranged on the seal holder 14 , the spring 13 is arranged on the side of the seal holder 14 opposite to the upper housing 21 , and the spring seat 12 is assembled with the plunger 11 .

Subsequently, one end of the supply passage portion 29 is arranged to contact the outer peripheral portion of the cover hole portion 265 of the cover bottom portion 262, and the supply passage portion 29 and the cover bottom portion 262 are welded over the entire circumferential direction of the supply passage portion 29. do.

Subsequently, the sub-assembled second electromagnetic drive section 502 is mounted on the end of the first electromagnetic drive section 501 opposite to the pressure chamber 200 so that the magnetic throttle section 56 and the fixed core 57 are positioned inside the coil 60 . provided in the department. Here, the second electromagnetic driving portion 502 is arranged such that the connector 65 faces the side opposite to the fixed portion 25 and is substantially parallel to the axis Ax1 of the cylindrical inner peripheral wall 230 of the cylinder 23 .

Subsequently, the center of the yoke 645 is welded to the end surface 572 of the fixed core 57 opposite to the pressure chamber 200 . By the above, the assembly of the high-pressure pump 10 is completed.

Next, attachment of the high-pressure pump 10 to the engine 1 will be described.

In this embodiment, the high-pressure pump 10 is attached to the engine 1 such that the holder support portion 24 is inserted into the attachment hole portion 3 of the engine head 2 (see FIG. 2). The high-pressure pump 10 is fixed to the engine 1 by fixing the fixed portion 25 to the engine head 2 with bolts 100 . Here, the high-pressure pump 10 is attached to the engine 1 in such a posture that the axis Ax1 of the cylindrical inner peripheral wall 230 of the cylinder 23 is along the vertical direction.

The high-pressure pump 10 is attached to the engine 1 by, for example, the following steps. First, the lifter 5 is inserted into the mounting hole 3 of the engine head 2 . Subsequently, the holder support portion 24 of the high-pressure pump 10 is inserted into the mounting hole portion 3 of the engine head 2 . Here, the position of the bolt hole 250 of the fixed portion 25 and the position of the fixing hole portion 120 of the engine head 2 are made to correspond.

Subsequently, the bolt 100 is inserted through the bolt hole 250 and screwed into the fixing hole portion 120 . At this time, a tool (not shown) corresponding to the head portion 102 of the bolt 100 is used to screw the bolt 100 and the fixing hole portion 120 together. As a result, the fixed portion 25 is fixed to the engine head 2 . Thus, the attachment of the high-pressure pump 10 to the engine 1 is completed.

Next, the operation of the high-pressure pump 10 of this embodiment will be described with reference to FIGS.

"Inhalation process"
When the power supply to the coil 60 of the electromagnetic drive unit 500 is stopped, the valve member 40 is biased toward the pressure chamber 200 by the spring 54 and the needle 53 . Therefore, the valve member 40 is separated from the valve seat 310, that is, the valve is open. In this state, when the plunger 11 moves to the side opposite to the pressure chamber 200, the volume of the pressure chamber 200 increases, and the fuel on the side opposite to the pressure chamber 200 with respect to the valve seat 310, that is, on the fuel chamber 260 side, , through the communication passage 33 into the pressurizing chamber 200 side.

"Weighing process"
When the plunger 11 moves toward the pressurizing chamber 200 while the valve member 40 is open, the volume of the pressurizing chamber 200 decreases, and the fuel on the pressurizing chamber 200 side with respect to the valve seat 310 flows into the valve seat 310. On the other hand, it is returned to the fuel chamber 260 side. When power is supplied to the coil 60 during the metering process, the movable core 55 is attracted together with the needle 53 toward the fixed core 57 side, and the valve member 40 is biased by the spring 39 to contact the valve seat 310 to close the valve. When the plunger 11 moves to the pressurizing chamber 200 side, the amount of fuel returned from the pressurizing chamber 200 side to the fuel chamber 260 side is adjusted by closing the valve member 40 . As a result, the amount of fuel pressurized in pressurization chamber 200 is determined. By closing the valve member 40, the metering process of returning the fuel from the pressure chamber 200 to the fuel chamber 260 ends.

When the fuel injection valve 138 does not inject fuel, that is, when the fuel is cut, the coil 60 is not energized and no fuel is discharged from the high-pressure pump 10 . At this time, since the valve member 40 is open, the fuel in the pressure chamber 200 moves back and forth between the pressure chamber 200 and the fuel chamber 260 as the plunger 11 reciprocates.

"Pressure process"
When the plunger 11 moves further toward the pressurizing chamber 200 while the valve member 40 is closed, the volume of the pressurizing chamber 200 decreases, and the fuel in the pressurizing chamber 200 is compressed and pressurized. When the pressure of the fuel in the pressurization chamber 200 becomes equal to or higher than the valve opening pressure of the discharge valve 75, the discharge valve 75 opens, and the fuel is discharged from the pressurization chamber 200 to the high pressure fuel pipe 8 side, that is, the fuel rail 137 side. be done.

When the power supply to the coil 60 is stopped and the plunger 11 moves away from the pressurizing chamber 200, the valve member 40 opens again. As a result, the pressurization process for pressurizing the fuel ends, and the intake process for sucking fuel from the fuel chamber 260 side to the pressurization chamber 200 side resumes.

By repeating the above "suction process", "metering process", and "pressurization process", the high-pressure pump 10 pressurizes and discharges the fuel in the fuel chamber 260 sucked into the pressurization chamber 200, and the fuel rail 137. The amount of fuel supplied from the high-pressure pump 10 to the fuel rail 137 is adjusted by controlling the timing of power supply to the coil 60 of the electromagnetic drive unit 500 and the like.

When the plunger 11 reciprocates while the valve member 40 is open, such as in the above-described "suction process" and "metering process", the fuel in the fuel chamber 260 changes the volume of the pressurization chamber 200. pressure pulsation due to The pulsation damper 15 provided in the fuel chamber 260 can reduce the pressure pulsation of the fuel in the fuel chamber 260 by elastically deforming according to changes in the fuel pressure in the fuel chamber 260 .

In addition, when the plunger 11 is reciprocating, pressure pulsation may occur due to changes in the volume of the variable volume chamber 201 . In this case as well, the pulsation damper 15 is elastically deformed according to changes in the fuel pressure in the fuel chamber 260 , thereby reducing the pressure pulsation of the fuel in the fuel chamber 260 .

When the plunger 11 descends, the volume of the variable volume chamber 201 decreases following the descending speed of the plunger 11, and fuel is pushed out to the fuel chamber 260 side. As a result, the fuel in the fuel chamber 260 is easily introduced into the pressurization chamber 200 when the plunger 11 descends. Further, when the plunger 11 rises, the volume of the variable volume chamber 201 increases, so the fuel returned from the pressurization chamber 200 is easily discharged into the variable volume chamber 201 during metering. Due to the above action, pulsation in the fuel chamber 260 is reduced.

Further, since the volume of the variable volume chamber 201 increases or decreases when the plunger 11 reciprocates, fuel flows back and forth between the fuel chamber 260 and the hole 222 , the annular space 202 and the variable volume chamber 201 . As a result, the cylinder 23 and the plunger 11, which have reached a high temperature due to the heat generated by the sliding movement between the plunger 11 and the cylinder 23 and the heat generated by the pressurization of the fuel in the pressurization chamber 200, can be cooled by the low temperature fuel. . Thereby, seizing of the plunger 11 and the cylinder 23 can be suppressed.

Also, part of the fuel that has become high pressure in the pressurization chamber 200 flows into the variable volume chamber 201 via the clearance between the plunger 11 and the cylinder 23 . As a result, an oil film is formed between plunger 11 and cylinder 23, and seizure of plunger 11 and cylinder 23 can be effectively suppressed. The fuel that has flowed from the pressurization chamber 200 into the variable volume chamber 201 returns to the fuel chamber 260 via the annular space 202 and the hole 222 .

<A-1> Next, the intake valve section 300 will be described in detail.

As shown in FIGS. 10 and 11, the sheet member 31 is formed in a substantially disc shape. The sheet member 31 is provided in the suction passage 216 so as to be substantially coaxial with the suction hole portion 212 inside the suction hole portion 212 . Here, the outer peripheral wall of the sheet member 31 is press-fitted into the inner peripheral wall of the suction hole portion 212 .

The seat member 31 has a communicating passage 32 , a communicating passage 33 and a valve seat 310 . The communicating passage 32 is formed in a substantially cylindrical shape so as to communicate between one surface and the other surface of the sheet member 31 at the center of the sheet member 31 . Here, the communication path 32 is formed so as to be substantially coaxial with the sheet member 31 . In addition, the inner diameter of the communicating passage 32 is larger than the outer diameter of the end of the needle body 531 on the pressure chamber 200 side. Therefore, a substantially cylindrical gap is formed between the inner peripheral wall of the communication passage 32 and the outer peripheral wall of the needle body 531, and the fuel can flow through the gap.

The communicating path 33 is formed in a substantially cylindrical shape so as to communicate between one surface and the other surface of the sheet member 31 on the radially outer side of the communicating path 32 . Twelve communicating paths 33 are formed at equal intervals in the circumferential direction of the sheet member 31 . Since the communication passages 33 are formed at equal intervals, the fuel flow becomes uniform and the behavior of the valve member 40 is stabilized. The communication path 33 is arranged on a virtual circle VC11 centered on the axis of the seat member 31 (see FIG. 11). Also, the inner diameter of the communicating path 33 is smaller than the inner diameter of the communicating path 32 .

Here, the communicating path 32 corresponds to the "inner communicating path", and the communicating path 33 corresponds to the "outer communicating path".

The valve seat 310 is annularly formed around each of the communication passages 32 and the plurality of communication passages 33 on the surface of the seat member 31 on the pressure chamber 200 side. That is, a plurality of valve seats 310 are formed on the surface of the seat member 31 on the pressure chamber 200 side. Specifically, one valve seat 310 is provided between the communicating path 32 and the communicating hole 44, one between the communicating hole 44 and the communicating path 33, and one outside the communicating path 33 in the radial direction. Three are formed. Here, the three valve seats 310 are formed concentrically.

An annular recess 311 is formed in the seat member 31 . The annular recess 311 is formed in a substantially annular shape so as to be recessed from the end face of the sheet member 31 on the pressurizing chamber 200 side toward the cylinder member 51 on the radially outer side of the sheet member 31 with respect to the plurality of communicating passages 33 . The annular recess 311 is formed substantially coaxially with the seat member 31 (see FIGS. 10 and 11). In this manner, since the annular recess 311 is formed radially outward of the seat member 31 with respect to the plurality of communicating passages 33, the flowability of the fuel during metering can be improved. Further, the pressure of the fuel in the annular recess 311 acts on the valve member 40 in the valve opening direction. Therefore, it is possible to suppress the closing of the valve due to the influence of the dynamic pressure.

As shown in FIGS. 10 and 12, the stopper 35 has a stopper small diameter portion 36, a stopper large diameter portion 37, a stopper concave portion 351, a stopper concave portion 352, a stopper convex portion 353, a communication hole 38, and the like.

The stopper small-diameter portion 36 is formed in a substantially cylindrical shape. The outer diameter of the stopper small diameter portion 36 is slightly smaller than the inner diameter of the suction hole portion 213 . The stopper large-diameter portion 37 is formed in a substantially cylindrical shape. The outer diameter of the stopper large-diameter portion 37 is larger than the outer diameter of the stopper small-diameter portion 36 and slightly smaller than the inner diameter of the suction hole portion 212 . The stopper large-diameter portion 37 is formed integrally with the stopper small-diameter portion 36 so as to be coaxial with the stopper small-diameter portion 36 on the opposite side of the stopper small-diameter portion 36 from the pressure chamber 200 .

The stopper 35 is provided in the suction passage 216 so that the small diameter stopper portion 36 is positioned inside the suction hole portion 213 and the large diameter stopper portion 37 is positioned inside the suction hole portion 212 . Here, the annular stepped surface between the stopper small diameter portion 36 and the stopper large diameter portion 37 abuts the annular stepped surface between the suction hole portions 212 and 213 . As a result, movement of the stopper 35 toward the pressure chamber 200 is restricted.

The surface of the stopper large-diameter portion 37 of the stopper 35 on the side opposite to the pressure chamber 200 is in contact with the surface of the sheet member 31 on the pressure chamber 200 side. As a result, movement of the stopper 35 to the side opposite to the pressurizing chamber 200 is restricted.

The stopper recessed portion 351 is formed so as to be recessed in a substantially cylindrical shape from the sheet member 31 side surface of the stopper large diameter portion 37 toward the pressure chamber 200 side. Here, the stopper concave portion 351 is formed so as to be substantially coaxial with the stopper large-diameter portion 37 . The inner diameter of the stopper concave portion 351 is smaller than the outer diameter of the stopper large-diameter portion 37 and larger than the outer diameter of the stopper small-diameter portion 36 .

The stopper recessed portion 352 is formed so as to be recessed in a substantially cylindrical shape from the bottom surface of the stopper recessed portion 351 toward the pressurizing chamber 200 side. Here, the stopper concave portion 352 is formed so as to be substantially coaxial with the stopper concave portion 351 . The inner diameter of the stopper concave portion 352 is smaller than the inner diameter of the stopper concave portion 351 and the outer diameter of the stopper small diameter portion 36 . The bottom surface of the stopper concave portion 352 is located closer to the pressurizing chamber 200 than the stepped surface between the stopper small-diameter portion 36 and the stopper large-diameter portion 37 .

The stopper protrusion 353 is formed to protrude in a substantially cylindrical shape from the center of the bottom surface of the stopper recess 352 toward the sheet member 31 . Here, the stopper convex portion 353 is formed so as to be substantially coaxial with the stopper concave portion 352 . Further, the end surface of the stopper protrusion 353 on the sheet member 31 side is located closer to the sheet member 31 than the bottom surface of the stopper recess 351 .

The communication hole 38 is formed in a substantially cylindrical shape so as to communicate between the bottom surface of the stopper concave portion 352 and the pressure chamber 200 side surface of the stopper small-diameter portion 36 on the radially outer side of the stopper convex portion 353 . Four communication holes 38 are formed at equal intervals in the circumferential direction of the stopper small diameter portion 36 . The communication hole 38 is arranged on a virtual circle VC12 centered on the axis of the stopper small diameter portion 36 (see FIG. 12). Here, the diameter of the virtual circle VC12 is smaller than the diameter of the virtual circle VC11.

A suction passage 216 is formed in the communicating passage 32 and the communicating passage 33 of the seat member 31 , the stopper recessed portion 351 and the stopper recessed portion 352 of the stopper 35 , and the communicating hole 38 . Therefore, the fuel in the fuel chamber 260 passes through the communication passage 32, the communication passage 33, the stopper recess 351, the stopper recess 352, the suction passage 216 formed in the communication hole 38, and the suction hole 232 to the pressurization chamber 200. Inflow is possible. Here, the seat member 31 and the stopper 35 correspond to the "intake passage forming portion".

As shown in FIG. 10 , the valve member 40 is provided inside the stopper concave portion 351 , that is, on the pressure chamber 200 side of the seat member 31 in the intake passage 216 . As shown in FIGS. 10 and 13 to 16, the valve member 40 has a valve body 41, a tapered portion 42, a guide portion 43, and a communicating hole 44. As shown in FIG.

The valve main body 41, the tapered portion 42, and the guide portion 43 are integrally formed of metal such as stainless steel. The valve body 41 is formed in a substantially disc shape.

The tapered portion 42 is formed integrally with the valve body 41 in a substantially annular shape on the radially outer side of the valve body 41 . The tapered portion 42 is tapered such that the surface on the side of the pressure chamber 200 approaches the axis Ax2 of the valve body 41 as it goes from the side of the seat member 31 toward the side of the pressure chamber 200 (see FIGS. 10, 15 and 16). ).

The guide portion 43 protrudes radially outward from the valve body 41 so as to divide the tapered portion 42 into a plurality of parts in the circumferential direction, and is integrally formed with the valve body 41 and the tapered portion 42 . In this embodiment, three guide portions 43 are formed at equal intervals in the circumferential direction of the valve body 41 so as to divide the tapered portion 42 into three in the circumferential direction. Here, the end portion of the guide portion 43 opposite to the valve body 41 is located radially outside the outer edge portion of the tapered portion 42 (see FIGS. 13 and 14). A slide portion 430 formed at the end portion of the guide portion 43 opposite to the valve main body 41 slides on the inner peripheral wall of the stopper concave portion 351 of the stopper 35 as the intake passage forming portion, whereby the valve member 40 is moved. can guide the axial movement of the

The communication hole 44 is formed to communicate between one surface and the other surface of the valve body 41 . Nine communication holes 44 are formed at equal intervals in the circumferential direction of the valve body 41 . The communication hole 44 is arranged on a virtual circle VC1 centered on the axis Ax2 of the valve body 41 (see FIGS. 13 and 14).

As shown in FIG. 13, a boundary line B1 between the inner edges of the three tapered portions 42 and the outer edge of the valve body 41 is formed along a concentric circle CC1 with respect to the virtual circle VC1.

As shown in FIG. 13 , the communication hole 44 extends from the center of the valve body 41 in the valve body 41 and is partitioned by three straight lines L11 passing through the center of the guide portion 43. Three are formed in each of the third regions T3.

Here, if the number of the communication holes 44 is h=9 and the number of the guide portions 43 is g=3, the inner edge portion of one of the tapered portions 42 divided by the guide portion 43 is opposed to the inner edge portion of the tapered portion 42 . The number of communicating holes 44 to be connected is h/g=9/3=3.

Also, the three communication holes 44 formed in the first region T1, the second region T2, and the third region T3 are sequentially arranged in the circumferential direction of the virtual circle VC1 as a communication hole 441, a communication hole 442, and a communication hole. 443, the boundary line B1 between the inner edge of the tapered portion 42 on the radially outer side of the first region T1 of the valve body 41 and the outer edge of the valve body 41 is the outer edge of the communication hole 441 in the first region T1, and Two tangent lines passing through the outer edge of the communication hole 443 of the second region T2 formed at a position line-symmetrical to the communication hole 441 of the first region T1 with respect to the straight line L11 between the first region T1 and the second region T2 of the first region T1 with respect to the tangent line LT11 that is the tangent line on the third region T3 side, the outer edge of the communication hole 443 in the first region T1, and the straight line L11 between the first region T1 and the third region T3. It is formed in a range between a tangent line LT11 that is a tangent line on the second region T2 side of two tangent lines that pass through the outer edge of the communication hole 441 of the third region T3 that is formed at a line-symmetrical position with the communication hole 443. ing.

A boundary line B1 between the inner edge of the radially outer tapered portion 42 of the second region T2 of the valve body 41 and the outer edge of the valve body 41, and the radially outer tapered portion 42 of the third region T3 of the valve body 41. A boundary line B1 between the inner edge of the valve body 41 and the outer edge of the valve body 41 is also formed in the same manner as described above.

That is, in the present embodiment, the boundary line B1 between the inner edge portion of one tapered portion 42 and the outer edge portion of the valve body 41 sandwiched between the two guide portions 43 is a plurality of points where the inner edge portions of the one tapered portion 42 face each other. of the communication holes 44 at both ends, and the straight line L11 extending from the center of the valve body 41 and passing through the center of the guide portion 43. It is formed in a range between two tangent lines LT11 passing through the outer edge of the communication hole 44 (443, 441) formed at a position line-symmetrical to (441, 443).

As shown in FIG. 10, in this embodiment, one surface 401 of the valve member 40, that is, the surface of the valve body 41 opposite to the pressurizing chamber 200, and the guide portion 43 opposite to the pressurizing chamber 200 and the surface of the tapered portion 42 opposite to the pressurizing chamber 200 are formed flat on the same plane. The other surface 402 of the valve member 40, that is, the pressure chamber 200 side surface of the valve body 41 and the pressure chamber 200 side surface of the guide portion 43 are formed flat on the same plane.

Further, as shown in FIG. 10, in this embodiment, the plate thickness of the valve body 41 and the guide portion 43 of the valve member 40, that is, the distance between the one surface 401 and the other surface 402 of the valve member 40 is the same as the sheet thickness. It is smaller than the distance between the surface of the member 31 on the pressurizing chamber 200 side and the end surface of the stopper protrusion 353 on the sheet member 31 side.

One surface 401 of the valve member 40 on the side of the seat member 31 can contact the surface of the seat member 31 on the side of the pressurizing chamber 200 , that is, the plurality of valve seats 310 . The center of the other surface 402 can come into contact with the end surface of the stopper protrusion 353 on the sheet member 31 side.

The valve member 40 is determined by the plate thickness of the valve body 41 and the guide portion 43, that is, the distance between one surface 401 and the other surface 402, the surface of the seat member 31 on the pressurizing chamber 200 side, and the sheet thickness of the stopper convex portion 353. It is possible to reciprocate in the axial direction within the range of the difference DD1 between the distance from the end face on the member 31 side.

The valve member 40 opens when one surface 401 , which is the surface on the side of the seat member 31 , is separated from the surface of the seat member 31 on the side of the pressure chamber 200 , that is, the plurality of valve seats 310 . , and when one surface 401 on the side of the seat member 31 comes into contact with a plurality of valve seats 310 , the valve closes and the flow of fuel in the communication passage 33 can be restricted.

When the valve member 40 is opened, fuel is permitted to flow between the communication passages 32 and 33 and the stopper recess 351, and the fuel in the fuel chamber 260 flows through the communication passage 32, the communication passage 33, the stopper recess 351, and the stopper recess 351. It can flow to the pressurizing chamber 200 side via the stopper concave portion 352 , the communication hole 38 and the suction hole 232 . Also, the fuel on the pressurization chamber 200 side can flow to the fuel chamber 260 side via the suction hole 232 , the communication hole 38 , the stopper recess 352 , the stopper recess 351 , the communication passage 33 , and the communication passage 32 . At this time, the fuel flows through the communication hole 44 of the valve member 40 , the periphery of the valve member 40 , the surface of the valve member 40 , and the boundary line B<b>1 between the inner edge portion of the tapered portion 42 and the outer edge portion of the valve body 41 .

When the valve member 40 closes, the flow of fuel between the communication passages 32 and 33 and the stopper recess 351 is restricted, and the fuel on the side of the fuel chamber 260 flows through the communication passage 32, the communication passage 33, the stopper recess 351, Flow toward the pressurizing chamber 200 via the stopper recess 352 , the communication hole 38 , and the suction hole 232 is restricted. Also, the fuel in the pressurization chamber 200 is restricted from flowing to the fuel chamber 260 via the suction hole 232 , the communication hole 38 , the stopper recess 352 , the stopper recess 351 , the communication passage 33 , and the communication passage 32 .

As shown in FIG. 10 , the spring 39 is provided radially outside the stopper protrusion 353 . The spring 39 has one end in contact with the bottom surface of the stopper recess 352 and the other end in contact with the other surface 402 of the valve member 40 on the pressure chamber 200 side. A spring 39 biases the valve member 40 toward the seat member 31 .

A plurality of seal portions 410 are formed in the valve member 40 at positions corresponding to the valve seats 310 formed in the seat member 31 . The seal portion 410 includes an annular first seal portion 411 that seals between the communication passage 32 as the inner communication passage and the communication hole 44, and an annular seal portion that seals between the communication passage 33 as the outer communication passage and the communication hole 44. and the outer diameter passage 45 formed between the valve body 41 and the stopper recessed portion 351 in the outer diameter direction of the valve body 41 of the valve member 40 and the communicating passage 33. An annular third seal portion 413 is included.

Here, the relationship between the flow path areas of the communication path 32 and the communication path 33 formed in the seat member 31 and the communication hole 44 formed in the valve member 40 will be described.

When the valve member 40 is in contact with the stopper 35, i.e., during full lift, as shown in FIGS. and the wall surface of the valve member 40 (the third seal portion 413) is defined as a first flow area S1, and the area of the communication path 33 The total flow area is defined as a second flow area S2, and the wall surface (second 2 seal portion 412) and the wall surface of the sheet member 31 is defined as a third flow area S3. It is larger than the sum of the three flow path areas S3.

The area of the annular flow path formed between the wall surface of the opening of the communication path 32 on the side of the valve member 40 and the wall surface (first seal portion 411) of the valve member 40 is defined as a fourth flow area S4. Assuming that the total channel area of the communication holes 44 formed in the second channel is a fifth channel area S5, the fifth channel area S5 is larger than the sum of the third channel area S3 and the fourth channel area S4.

Furthermore, when the passage area of the communication path 32 formed in the sheet member 31 is defined as a sixth passage area S6, the sixth passage area S6 is larger than the fourth passage area S4.

By setting the flow path areas of the communication path 32 and the communication path 33 formed in the seat member 31 and the communication hole 44 formed in the valve member 40 to the relationship described above, the valve member 40 and the seat member 31 The flow path formed between is a throttle.

Next, the plate thickness of the valve member 40 will be described.

As shown in FIG. 10 , the plate thickness of the valve body 41 of the valve member 40 is smaller than the plate thickness of the seat member 31 . As a result, the valve main body 41 deforms following the seat member 31, so that the sealing performance can be improved. The shape of the valve body 41 is desirably such that the surface pressure on the seat member 31 is uniform when pressure is received.

In this embodiment, the maximum injection pressure of the fuel injected by the fuel injection valve 138, that is, the system fuel pressure of the fuel supply system 9 is 20 MPa or more, and the pressure in the pressure chamber 200 rises to a peak fuel pressure of about 40 MPa due to pressure loss. I have something to do. In order to ensure the strength and sealing performance of the valve member 40 in such a high fuel pressure environment, it is desirable to set the plate thickness ratio t/D as shown in Equation 1 below.
0.06≦t/D≦0.13 Formula 1

In Equation 1 above, D is the diameter of the third seal portion 413 that seals between the outer diameter flow path 45 and the communication path 33 (see FIGS. 11 and 14). Further, t is the plate thickness of the valve body 41 (see FIG. 10). In this embodiment, t is 1 (mm), for example.

The significance of setting the plate thickness ratio t/D as in Equation 1 above will be described with reference to FIG. The graph of FIG. 17 shows the relationship between the plate thickness ratio t/D, the seal surface pressure (double-dot chain line), and the limit pressure (material strength, single-dot chain line).

As shown in FIG. 17, if the plate thickness ratio t/D is 0.06 or more, the desired material strength, ie, the peak fuel pressure of the pressure chamber 200 of about 40 MPa can be ensured. Further, if the plate thickness ratio t/D is 1.13 or less, a desired sealing surface pressure (40 MPa or more) can be secured.

Since the valve body 41 is easily deformed in a high fuel pressure environment, it is desirable to increase the plate thickness t of the valve body 41 in order to increase strength. However, in the case of the valve member 40 having a plurality of seal portions 410 as in the present embodiment, it is necessary to seal a plurality of flow paths, so it is also necessary to ensure sealing performance. In order to improve the sealing performance, it is necessary to reduce the plate thickness t. Therefore, in the present embodiment, the plate thickness ratio t/D is set to Equation 1 based on the graph shown in FIG. In order to further improve the sealing performance, for example, in order to set the sealing surface pressure to 60 MPa or more, it is desirable that the plate thickness ratio t/D is as shown in Equation 2 below.
0.06≦t/D≦0.12 Formula 2

As described above, (A1) the high-pressure pump 10 of the present embodiment includes the cylinder 23 as a pressure chamber forming portion, the upper housing 21 as a suction passage forming portion, the stopper 35, the seat member 31, and the valve member 40. I have it.

Cylinder 23 forms a pressure chamber 200 in which fuel is pressurized. The upper housing 21 and the stopper 35 form an intake passage 216 through which the fuel sucked into the pressurization chamber 200 flows.

The seat member 31 is provided in the suction passage 216 and has a communication passage 32 positioned radially inward of the suction passage 216 and communicating between one surface and the other surface of the suction passage 216 , and a radially outer portion of the communication passage 32 . A communication passage 33 is provided to communicate between the surface of the housing and the other surface. The valve member 40 is provided on the pressurizing chamber 200 side of the seat member 31, and is separated from the seat member 31 to open the valve or contact the seat member 31 to close the valve, thereby restricting the flow of fuel in the communication passages 32 and 33. Permissible or regulatable.

The valve member 40 includes a plate-shaped valve body 41, a plurality of communication holes 44 formed between the communication passages 33 and 32 for communicating one side and the other side of the valve body 41, and the valve body 41. A tapered portion 42 provided on the radially outer side of the pressure chamber 200 side is tapered so that it approaches the axis Ax2 of the valve body 41 as it goes from the seat member 31 side to the pressure chamber 200 side, and a taper It has a plurality of guide portions 43 that protrude radially outward from the valve body 41 so as to divide the portion 42 into a plurality of pieces in the circumferential direction and can guide the movement of the valve member 40 by sliding on the stopper recessed portion 351 of the stopper 35 . there is The plurality of communication holes 44 are arranged on a virtual circle VC1 centered on the axis Ax2 of the valve body 41. As shown in FIG.

In this embodiment, the sheet member 31 has a communication path 32 in the radially inner direction of the sheet member 31 and a communication path 33 provided in the radially outer direction of the communication path 32 . The valve member 40 can contact and separate from the seat member 31 and has a communicating hole 44 located between the communicating passages 32 and 33 in the radial direction. The fuel flows in the radially outward direction of the valve member 40 and passes between the valve member 40 and the stopper recessed portion 351 to reach the communication passage 33 of the seat member 31, and also passes through the communication hole 44 of the valve member 40 to the seat member 31. and a passage through the communication hole 44 of the valve member 40 and the communication passage 33 of the seat member 31 .

Therefore, even if the amount of lift of the valve member 40 from the seat member 31 is reduced, the valve member 40 and the stopper recessed portion 351 can be connected to the valve member 40 and the stopper recessed portion 351 even if the valve member 40 is lifted from the seat member 31 by a small amount. Equivalent flow passage area can be secured under the configuration having only the flow passage between. Therefore, the lift amount of the valve member 40 from the seat member 31 can be reduced, the driving force for lifting the valve member 40 from the seat member 31 can be set small, and the maximum output of the electromagnetic drive unit 500 can be increased. can be made smaller. Thereby, the size reduction of the electromagnetic drive unit 500 is realized. Furthermore, by reducing the lift amount, the collision noise between the valve member 40 and the needle body 531 can be suppressed. Also, by reducing the lift amount, the responsiveness of the electromagnetic drive unit 500 can be enhanced. As a result, excessive backflow of fuel during metering can be suppressed, and discharge efficiency during high-speed operation can be increased.

Furthermore, in the present embodiment, the boundary line B1 between the inner edge of the tapered portion 42 and the outer edge of the valve body 41 is formed along the concentric circle CC1 with respect to the virtual circle VC1. Therefore, the distance between both ends of each boundary line B1 and the communication hole 44 can be reduced. As a result, it is possible to suppress the portions near both ends of each boundary line B<b>1 from acting as resistance to the fuel flowing on the surface of the valve member 40 . Therefore, a sufficient flow rate of fuel sucked into the pressurization chamber 200 can be ensured. Also, the flow rate of the fuel returned from the pressurization chamber 200 to the fuel chamber 260 side can be sufficiently ensured.

(A2) In the present embodiment, when h is the number of communication holes 44 and g is the number of guide portions 43, the inner edge of one of the tapered portions 42 divided by the guide portions 43 into a plurality of tapered portions 42 is The number of communicating holes 44 facing each other is equal and is h/g. Therefore, the communication holes 44 can be arranged in a well-balanced manner corresponding to one tapered portion 42 . As a result, the flow of fuel passing through the valve member 40 can be stabilized.

(A3) In the present embodiment, the boundary line B1 between the inner edge of one tapered portion 42 sandwiched between the two guide portions 43 and the outer edge of the valve body 41 is defined by the inner edge of the single tapered portion 42. Outer edges of the end communication holes (441, 443), which are the communication holes 44 at both ends of the plurality of opposing communication holes 44, and a straight line L11 extending from the center of the valve body 41 and passing through the center of the guide portion 43. It is formed in a range between two tangent lines LT1 passing through the outer edge of the communication holes 44 (443, 441) formed at positions line-symmetrical to the communication holes (441, 443). Therefore, the distance between both ends of each boundary line B1 and the communication hole 44 can be reduced while ensuring the length of each boundary line B1, and the portions near both ends of each boundary line B1 act as resistance to the flow of fuel. can be suppressed.

(A9) The high-pressure pump 10 of the present embodiment is applied to a fuel supply system 9 having a fuel injection valve 138 that supplies fuel to the engine 1 . In the fuel supply system 9 in which the maximum injection pressure of the fuel injected by the fuel injection valve 138 is 20 MPa or more, the valve member 40 is provided between the outer diameter flow path 45 located radially outwardly of the valve member 40 and the communication passage 33 . If the diameter of the third seal portion 413 is D, the plate thickness of the valve member 40 is t, and the plate thickness ratio is t/D, then 0.06≦t/ D≤0.13.

Therefore, in a high fuel pressure environment, the strength of the valve member 40 having the plurality of seal portions 410 can be ensured, and the sealing performance can be improved.

<B-1> Next, the electromagnetic driving section 500 will be described in detail.

As shown in FIG. 18, the outer peripheral wall of the second tubular portion 512 of the tubular member 51 is formed in a substantially hexagonal tubular shape. Specifically, the six circumferential corners of the outer peripheral wall of the second tubular portion 512 are curved so as to be positioned on an imaginary cylindrical surface centered on the axis of the second tubular portion 512 . A gap is formed between the flat portion of the outer peripheral wall of the second tubular portion 512 and the inner peripheral wall of the spool 61 .

In the present embodiment, when the cylindrical member 51 is screwed to the suction hole portion 212 of the upper housing 21, the wall surface of the tool is brought into contact with the outer peripheral wall of the second cylindrical portion 512 and rotated, so that the cylindrical member 51 is screwed to the suction hole portion. 212.

As shown in FIGS. 5 and 18, in the present embodiment, the second tubular portion 512 of the tubular member 51 is positioned inside the inner tubular surface 602 of the coil 60, that is, at the end of the spool 61 on the pressure chamber 200 side. located inside. Therefore, when the hexagonal cylindrical outer peripheral wall against which the wall surface of the tool is applied when the cylindrical member 51 is screwed to the suction hole portion 212 is formed on the pressure chamber 200 side of the outer peripheral wall of the cylindrical member 51 with respect to the spool 61. , the axial lengths of the tubular member 51 and the needle 53 can be shortened. As a result, the inertial mass can be reduced, improving responsiveness and reducing NV.

Further, in this embodiment, the coil 60 has an inner cylindrical surface 601 and an inner cylindrical surface 602 having different diameters, and the winding wire 620 is radially outward of the inner cylindrical surface 601 and the inner cylindrical surface 602 . is wound around. Further, as described above, the second tubular portion 512 of the tubular member 51 is positioned inside the inner tubular surface 602 of the coil 60 . Therefore, the radial thickness of the second cylindrical portion 512 can be increased, and the second cylindrical portion 512 can be prevented from becoming a magnetic diaphragm.

On the other hand, if the coil 60 does not have the inner cylindrical surface 601 but has only the inner cylindrical surface 602, and the winding 620 is wound radially outward of the inner cylindrical surface 602 by the same amount as in the present embodiment, As a result, the axial length of the winding portion 62 increases, and the axial lengths of the fixed core 57 and the needle 53 increase. As a result, the NV increases and the resistance of the winding portion 62 increases, which may increase the power consumption of the coil 60 .

Also, if the coil 60 does not have the inner cylindrical surface 602 but has only the inner cylindrical surface 601, and the winding 620 is wound radially outward of the inner cylindrical surface 601 by the same amount as in the present embodiment, Then, in addition to the same problem as described above, the radial thickness of the second cylindrical portion 512 of the cylindrical member 51 is reduced, and the second cylindrical portion 512 may act as a magnetic diaphragm. In this case, the attractive force between the fixed core 57 and the movable core 55 becomes insufficient, and there is a possibility that necessary responsiveness cannot be ensured.

FIG. 19 schematically shows a simplified part of the coil 60 of this embodiment. Therefore, relative lengths, sizes, and the like between each member and each part constituting the coil 60 are different from the actual ones. In addition, the number of turns of the winding 620 wound around the outer peripheral wall of the spool 61 is also shown in a simplified manner by being smaller than the actual number.

As shown in FIG. 19, the coil 60 has an imaginary connecting surface 605 that connects the inner cylindrical surface 601 and the inner cylindrical surface 602 . The connecting surface 605 is formed in a substantially annular shape. The inner cylindrical surface 601 , the inner cylindrical surface 602 and the connecting surface 605 are located on the outer peripheral wall of the spool 61 . At least a portion of the connecting surface 605 is formed in a tapered shape so as to approach the axis of the spool 61 from the pressure chamber 200 side toward the side opposite to the pressure chamber 200 .

More specifically, the connection surface 605 is tapered at the connection portion with the inner cylindrical surface 601 which is the inner cylindrical surface having the smallest diameter among the inner cylindrical surfaces 601 and 602 . The other portion, that is, the portion on the inner cylindrical surface 602 side, is formed so as to be perpendicular to the axis of the spool 61 . A tapered portion of the connecting surface 605 that is connected to the inner cylindrical surface 601 is called a tapered surface portion 691 , and the other flat portion that is perpendicular to the axis of the spool 61 is called a vertical surface portion 692 . do.

Further, as shown in FIG. 19, in the cross section along the virtual plane VP1 including the axis of the spool 61, the angle formed between the inner cylindrical surface 601 and the connecting surface 605, that is, the angle formed between the inner cylindrical surface 601 and the tapered surface portion 691 The minor angle θ of the angles is 120 degrees.

In this embodiment, the end surface 621 of the winding portion 62 on the pressurizing chamber 200 side is tapered at the connection portion with the inner cylindrical surface 602 . The angle θ between the connecting portion and the inner cylindrical surface 602 is 120 degrees.

Further, as shown in FIG. 19, the winding 620 extends N from the inner cylindrical surface 601, which is the inner cylindrical surface having the smallest diameter among the inner cylindrical surfaces 601 and 602, toward the radial direction outside. layers are wound. In this embodiment, N is an even number. FIG. 19 shows N=10, that is, the windings 620 wound in 10 layers from the inner cylindrical surface 601 radially outward.

In this embodiment, when the winding 620 is wound around the outer peripheral wall of the spool 61, the winding 620 is wound in the axial direction of the spool 61 toward the pressure chamber 200 side in the first layer, and the winding is wound in the second layer. 620 is wound in the axial direction of the spool 61 toward the side opposite to the pressurizing chamber 200, and in the third layer, the winding 620 is wound in the axial direction of the spool 61 toward the pressurizing chamber 200 side, and this is N Repeat until layer. As described above, by setting N to an even number, the winding start position and the winding end position of the winding 620 are set, for example, on the opposite side of the axial end of the spool 61 from the pressure chamber 200. can do. Therefore, connection to the terminal 651 can be facilitated (see FIGS. 22 and 23).

In addition, as shown in FIG. 19, the winding 620 has the same number of axial turns in the first layer extending radially outward from the inner cylindrical surface 601 and the number of axial turns in the second layer. FIG. 19 shows that the number of windings in the axial direction of the winding 620 in the first layer and the number of windings in the axial direction of the second layer are both 5 for simplification from the actual one. Here, the windings 620 of the second layer are positioned between the windings 620 adjacent in the axial direction in the first layer.

Note that, in the present embodiment, the tapered surface portion 691 is the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 of the first layer, and the winding 620 of the second layer. It abuts on the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 . The connection portion of the vertical surface portion 692 with the tapered surface portion 691 is in contact with the winding 620 of the second layer winding 620 that is positioned closest to the pressure chamber 200 in the axial direction of the spool 61 . That is, the boundary between the tapered surface portion 691 and the vertical surface portion 692 is located on the second layer of the winding 620 wound radially outward from the inner cylindrical surface 601 .

Further, as shown in FIG. 19, the winding 620 is formed between the inner cylindrical surface 601 having the smallest diameter and the inner cylindrical surface having the largest diameter among the inner cylindrical surface 601 and the inner cylindrical surface 602 . Between TB1 and inner cylindrical surface 602, which is a surface, the number of turns in the axial direction of winding 620 for each layer is the same for all layers. In FIG. 19, the winding 620 is wound radially outward in four layers at TB1 between the inner cylindrical surface 601 and the inner cylindrical surface 602, and each layer of the winding 620 is axially wound. The number of times is 5 for all layers (1st to 4th layers). Here, the m+1-th layer winding 620 is positioned between the windings 620 adjacent in the axial direction in the m-th layer.

Next, the coil 60 according to the present embodiment and the coil 60 according to the comparative embodiment are compared to clarify the superiority in effect of the present embodiment over the comparative embodiment.

FIG. 20 shows the coil 60 according to the first comparative form, and FIG. 21 shows the coil 60 according to the second comparative form.

As shown in FIG. 20, the coil 60 according to the first comparative embodiment differs from the coil 60 according to this embodiment in the shape of the connecting surface 605 . In the coil 60 according to the first comparative embodiment, the connecting surface 605 is formed flat so that all parts are perpendicular to the axis of the spool 61, and the angle between the inner cylindrical surface 601 and the connecting surface 605 is The minor angle θ is 90 degrees. Therefore, a gap Sp<b>1 is formed between the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 of the first layer and the connecting surface 605 . As a result, the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 of the first layer may be displaced toward the gap Sp1. As a result, the second-layer winding 620 in contact with the winding 620 located closest to the pressure chamber 200 in the axial direction of the spool 61 among the first-layer windings 620 is displaced in the radial direction of the spool 61 . There is a risk. Therefore, the state of the winding 620 wound around the spool 61 may become unstable.

On the other hand, the coil 60 according to the present embodiment, as shown in FIG. The minor angle θ of the angle formed by 601 and tapered surface portion 691 is 120 degrees. Therefore, the tapered surface portion 691 includes the winding 620 of the winding 620 on the first layer that is positioned closest to the pressurizing chamber 200 in the axial direction of the spool 61 and the winding 620 of the winding 620 on the second layer that is the axis of the spool 61 . It abuts on the winding 620 positioned closest to the pressure chamber 200 in the direction. Therefore, in the coil 60 according to the present embodiment, the gap Sp1 formed in the coil 60 according to the first comparative embodiment is not formed. The connection portion of the vertical surface portion 692 with the tapered surface portion 691 is in contact with the winding 620 of the second layer winding 620 that is positioned closest to the pressure chamber 200 in the axial direction of the spool 61 . With this configuration, in the coil 60 according to the present embodiment, the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 of the first layer, and the winding 620 in contact with the winding 620 Positional deviation of the windings 620 in each layer can be suppressed, and the state of the windings 620 wound around the spool 61 can be stabilized.

As shown in FIG. 21, in the coil 60 according to the second comparative embodiment, the number of windings in the axial direction of the winding 620 of each layer in the space TB1 between the inner cylindrical surface 601 and the inner cylindrical surface 602 is the same as that of the present embodiment. Different from coil 60 . In the coil 60 according to the second comparative example, the number of turns in the axial direction of the windings 620 of the first and third layers is 5, and the number of turns of the windings 620 of the second and fourth layers in the axial direction is 4. . Therefore, a gap Sp<b>2 is formed between the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 of the second layer and the connecting surface 605 . A gap Sp<b>3 is formed between the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 in the fourth layer and the connection surface 605 . As a result, the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 of the third layer may be displaced toward the gap Sp2. Moreover, there is a possibility that the winding 620 of the fifth layer facing the gap Sp3 may be displaced toward the gap Sp3. Therefore, the state of the winding 620 wound around the spool 61 may become unstable.

On the other hand, in the coil 60 according to this embodiment, as shown in FIG. The number of turns is the same for all layers. Therefore, in the coil 60 according to the present embodiment, the gaps Sp2 and Sp3 formed in the coil 60 according to the second comparative embodiment are not formed. With this configuration, in the coil 60 according to the present embodiment, the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 of the third layer, and the winding 620 of the fifth layer. Positional deviation can be suppressed, and the state of the winding 620 wound around the spool 61 can be stabilized.

As shown in FIG. 24 , spool grooves 611 and 612 are formed in the outer peripheral wall of the spool 61 . 24 shows a developed view of the outer peripheral wall of the spool 61, and FIG. 24 shows a sectional view of the spool 61 in the lower part.

The spool groove portion 611 is formed to extend in the circumferential direction of the spool 61 while being recessed radially inward from a portion of the outer peripheral wall of the spool 61 corresponding to the inner cylindrical surface 601 . The spool groove portion 611 is not partially formed in the spool 61 in the circumferential direction, but is formed in substantially the entire circumferential range of the spool 61 .

The spool groove portion 612 is formed to extend in the circumferential direction of the spool 61 while being recessed radially inward from a portion of the outer peripheral wall of the spool 61 corresponding to the inner cylindrical surface 602 . The spool groove portion 612 is formed in a range of approximately 90 to 360 degrees in the circumferential direction of the spool 61 . That is, the spool groove portion 612 is not formed in a portion of the outer peripheral wall of the spool 61 corresponding to the inner cylindrical surface 602 in the circumferential direction (in the range of 0 to about 90 degrees).

In a part of the outer peripheral wall of the spool 61 corresponding to the inner cylindrical surface 601 in the circumferential direction (range of 0 to about 90 degrees), the spool groove portion 611 360-degree range) with respect to the spool groove portion 611.

The winding 620 is wound around the spool 61 so that a portion of the winding 620 enters the spool grooves 611 and 612 . This allows the winding 620 to be stabilized with respect to the spool 61 . At the time of switching, when the winding 620 wound around the portion corresponding to the inner cylindrical surface 601 of the outer peripheral wall of the spool 61 is wound around the portion corresponding to the inner cylindrical surface 602, The position of winding 620 may vary. In this embodiment, as described above, the spool groove 612 is not formed in a portion of the outer peripheral wall of the spool 61 corresponding to the inner cylindrical surface 602 in the circumferential direction. Therefore, the variation in the position of the winding 620 can be absorbed by the portion of the outer peripheral wall of the spool 61 where the spool groove 612 is not formed.

As described above, (B1) the high-pressure pump 10 of the present embodiment includes the cylinder 23 as a pressure chamber forming portion, the upper housing 21 as a suction passage forming portion, the seat member 31, the valve member 40, and the cylindrical member 51. It has a needle 53 , a movable core 55 , a spring 54 as an urging member, a fixed core 57 and a coil 60 . Cylinder 23 forms a pressure chamber 200 in which fuel is pressurized.

The upper housing 21 forms a suction passage 216 through which fuel drawn into the pressurization chamber 200 flows. The seat member 31 has a communicating passage 32 and a communicating passage 33 provided in the intake passage 216 and communicating between one surface and the other surface. The valve member 40 is provided on the pressurizing chamber 200 side of the seat member 31, and is separated from the seat member 31 to open the valve or contact the seat member 31 to close the valve, thereby restricting the flow of fuel in the communication passages 32 and 33. Permissible or regulatable.

The cylindrical member 51 is provided on the side of the sheet member 31 opposite to the pressure chamber 200 . The needle 53 is provided so as to be able to reciprocate in the axial direction inside the cylindrical member 51 , and one end can abut against the surface of the valve member 40 opposite to the pressure chamber 200 . A movable core 55 is provided at the other end of the needle 53 .

A spring 54 can bias the needle 53 toward the pressurizing chamber 200 . The fixed core 57 is provided on the opposite side of the cylinder member 51 from the pressure chamber 200 . The coil 60 has a winding portion 62 formed in a cylindrical shape by winding a winding 620 around a spool 61 . When the winding portion 62 is energized, an attractive force is generated between the fixed core 57 and the movable core 55 . to move the movable core 55 and the needle 53 in the valve closing direction.

The coil 60 has one outer cylindrical surface 600 passing through the outer peripheral surface of the winding portion 62, and an inner cylindrical surface 601 and an inner cylindrical surface 602 passing through the inner peripheral surface of the winding portion 62 and having different diameters. is doing. The inner cylindrical surface 601 and the inner cylindrical surface 602 have a larger diameter toward the pressure chamber 200 side.

At least when the coil 60 is not energized, the end surface 551 of the movable core 55 on the side of the fixed core 57 is positioned between the axial center Ci1 of the inner cylindrical surface 601, which is the inner cylindrical surface with the smallest diameter, and the outer cylindrical surface 600. It is located between the center Co1 in the axial direction. Therefore, when the coil 60 is energized, the attractive force acting on the movable core 55 can be increased. Thereby, the responsiveness of the movable core 55 can be improved. In addition, since the movable core 55 has high responsiveness, the current flowing through the coil 60 can be reduced without reducing the attractive force acting on the movable core 55 . Therefore, the power consumption of the electromagnetic driving section including the coil 60 can be reduced.

(B2) In the present embodiment, the end surface 552 of the movable core 55 on the pressurizing chamber 200 side is located on the fixed core 57 side with respect to the end surface 621 of the winding portion 62 on the pressurizing chamber 200 side. Therefore, the axial length of the movable core 55 can be shortened, and the weight of the movable core 55 can be reduced. This can improve the responsiveness of the movable core 55 and reduce NV.

(B3) In the present embodiment, the coil 60 has a connecting surface 605 that connects the inner cylindrical surface 601 and the inner cylindrical surface 602 . The inner cylindrical surface 601 , the inner cylindrical surface 602 and the connecting surface 605 are located on the outer peripheral wall of the spool 61 . The connecting surface 605 is formed such that at least a portion thereof, ie, the vertical surface portion 692 is perpendicular to the axis of the spool 61 . Therefore, positional displacement of the winding 620 wound radially outward of the inner cylindrical surface 601 can be suppressed. Thereby, the coil 60 can be manufactured easily.

(B4) In the present embodiment, at least a portion of the connecting surface 605, that is, the tapered surface portion 691 tapers toward the axis of the spool 61 as it goes from the pressure chamber 200 side toward the side opposite to the pressure chamber 200. formed in the shape of Therefore, the tapered surface portion 691 of the connecting surface 605 can be brought into contact with the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 of each layer. Thereby, the positional deviation of the winding 620 can be suppressed.

(B5) In the present embodiment, the connection surface 605 has a tapered portion connected to the inner cylindrical surface 601, which is the inner cylindrical surface with the smallest diameter, that is, the tapered surface portion 691 is formed. In a cross section along a virtual plane VP1 including the axis of the spool 61, the angle formed by the inner cylindrical surface 601 and the tapered surface portion 691 of the connecting surface 605 is 120 degrees. Therefore, the tapered surface portion 691 of the connecting surface 605 is the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 of the first layer, and the winding 620 of the winding 620 of the second layer. It can be brought into contact with the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 . As a result, displacement of the winding 620 can be suppressed particularly at the connecting portion between the inner cylindrical surface 601 and the connecting surface 605 . Therefore, the state of winding 620 wound around spool 61 can be stabilized.

(B7) In the present embodiment, the winding 620 is wound in N layers radially outward from the inner cylindrical surface 601, which is the inner cylindrical surface with the smallest diameter. N is an even number. Therefore, the winding start position and the winding end position of the winding 620 can be set, for example, on the opposite side of the axial end of the spool 61 from the pressure chamber 200 . Thereby, the winding 620 can be fixed along the spool 61 . Therefore, even if the spool 61 is deformed by heat, it is possible to suppress the application of excessive tension to the winding 620 and to suppress the breaking of the winding 620 due to thermal fatigue. Also, by setting N to an even number, the connection between the terminal 651 and the winding 620 is facilitated.

(B8) In the present embodiment, the winding 620 has the number of windings in the axial direction in the first layer radially outward from the inner cylindrical surface 601, which is the inner cylindrical surface with the smallest diameter, and the number of turns in the second layer. The number of turns in the axial direction is the same. Therefore, the windings 620 of the second layer can be positioned between the windings 620 adjacent in the axial direction in the first layer. Further, the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 of the second layer can be brought into contact with the connecting surface 605 . As a result, positional displacement of the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the windings 620 of the third layer can be suppressed. Therefore, the state of winding 620 wound around spool 61 can be stabilized.

(B9) In this embodiment, the winding 620 has a distance TB1 between the inner cylindrical surface 601, which is the inner cylindrical surface with the smallest diameter, and the inner cylindrical surface 602, which is the inner cylindrical surface with the largest diameter. , the number of turns in the axial direction for each layer of winding 620 is the same for all layers. Therefore, the winding 620 of the (N+1)th layer can be positioned between the windings 620 adjacent in the axial direction in the Nth layer. Further, the winding 620 positioned closest to the pressure chamber 200 in the axial direction of the spool 61 among the even-layered windings 620 can be brought into contact with the connecting surface 605 . Thereby, the positional deviation of the winding 620 can be suppressed. Therefore, the state of winding 620 wound around spool 61 can be stabilized.

<C-1> Next, the discharge joint 70, the discharge seat member 71, the intermediate member 81, the relief seat member 85, the discharge valve 75, the relief valve 91, the spring 79, and the spring 99, which constitute the discharge passage portion 700, are individually explain.

As shown in FIGS. 25-27, the discharge joint 70 is formed in a substantially cylindrical shape. A substantially annular stepped surface 701 is formed inside the discharge joint 70 . The discharge joint 70 forms a discharge passage 705 inside. The discharge joint 70 is formed with a lateral hole portion 702 that communicates between the inner peripheral wall and the outer peripheral wall. One lateral hole portion 702 is formed in the circumferential direction of the discharge joint 70 . The discharge joint 70 is formed with a polygonal tubular surface 703 having a substantially hexagonal tubular shape. The polygonal cylindrical surface 703 is formed on the outer peripheral wall of the discharge joint 70 at a position generally radially outward of the stepped surface 701 in the axial direction.

As shown in FIGS. 28 to 30, the discharge seat member 71 has a discharge member main body 72, a discharge hole 73, and a discharge valve seat 74. As shown in FIGS. The ejection member main body 72 is formed in a substantially disc shape. The outer diameter of the discharge member main body 72 is slightly larger than the inner diameter of one end of the discharge joint 70 . The discharge member main body 72 is provided inside the discharge joint 70 such that the outer peripheral wall is fitted to the inner peripheral wall at one end of the discharge joint 70 .

The discharge member main body 72 is formed with a discharge concave portion 721 , an inner protrusion 722 and an outer protrusion 723 . The discharge concave portion 721 is formed so as to be recessed in a substantially cylindrical shape from the center of one end face of the discharge member body 72 toward the other end face side. The inner protrusion 722 is formed to protrude in a substantially annular shape from the other end surface of the discharge member main body 72 . The outer protrusion 723 is formed to protrude in a substantially annular shape from the other end surface of the discharge member main body 72 on the radially outer side of the inner protrusion 722 .

The discharge hole 73 is formed in a substantially cylindrical shape so that the end surface of the discharge member main body 72 on the radially inner side of the inner protrusion 722 and the bottom surface of the discharge concave portion 721 communicate with each other. The discharge valve seat 74 is formed in a substantially annular shape around the discharge hole 73 on the bottom surface of the discharge recess 721 . The discharge recess 721 , the inner projection 722 , the outer projection 723 , the discharge hole 73 , and the discharge valve seat 74 are formed so as to be substantially coaxial with the discharge member main body 72 .

As shown in FIGS. 31 to 33, the intermediate member 81 has an intermediate member main body 82 and a first channel 83. As shown in FIGS. The intermediate member main body 82 is formed in a substantially disc shape. The intermediate member main body 82 is provided inside one end of the discharge joint 70 so as to abut on the discharge sheet member 71 . The outer diameter of the intermediate member main body 82 is slightly smaller than the inner diameter of one end of the discharge joint 70 .

An intermediate recess 821 is formed in the intermediate member main body 82 . The intermediate recess 821 is formed so as to be recessed in a substantially cylindrical shape from the center of one end surface of the intermediate member main body 82 toward the other end surface. The intermediate concave portion 821 is formed so as to be substantially coaxial with the intermediate member main body 82 .

The first flow path 83 is formed in a substantially cylindrical shape so as to communicate between one end surface and the other end surface of the intermediate member main body 82 on the radially outer side of the intermediate recessed portion 821 . Five first flow paths 83 are formed at equal intervals in the circumferential direction of the intermediate member main body 82 .

In this embodiment, an annular groove 800 is formed in the intermediate member 81 . The annular groove 800 is formed in a substantially annular shape so as to be recessed from the other end surface of the intermediate member main body 82 toward one end surface. The annular groove 800 is formed substantially coaxially with the intermediate member main body 82 . Also, the annular groove 800 is connected to all the ends of the first flow paths 83 .

As shown in FIGS. 34 to 36, the relief seat member 85 has a relief member main body 86, a relief hole 87, a relief valve seat 88, a second flow path 89, a relief outer peripheral recessed portion 851, a relief lateral hole 852, and a lateral hole 853. there is The relief member main body 86 has a relief member tubular portion 861 and a relief member bottom portion 862 . The relief member tubular portion 861 is formed in a substantially cylindrical shape. The relief member bottom portion 862 is formed integrally with the relief member tubular portion 861 so as to close one end of the relief member tubular portion 861 .

The inner peripheral wall of the relief member tubular portion 861 is formed so that the inner diameter of the portion 806 on the pressurizing chamber 200 side with respect to the sliding portion 805 is larger than the inner diameter of the sliding portion 805 with the relief valve sliding portion 93 . . Further, the inner peripheral wall of the relief member tubular portion 861 is formed so that the inner diameter of the portion 807 on the pressurizing chamber 200 side is larger than the inner diameter of the portion 806 (see FIG. 34).

The relief member main body 86 is provided inside the discharge joint 70 on the opposite side of the intermediate member 81 from the discharge sheet member 71 . The outer diameter of the relief member cylindrical portion 861 is substantially the same as the inner diameter of the portion of the discharge joint 70 on the discharge sheet member 71 side with respect to the stepped surface 701 . In the relief member main body 86, the end surface of the relief member tubular portion 861 on the side opposite to the relief member bottom portion 862 abuts the outer edge portion of the end surface of the intermediate member main body 82, and the end surface of the relief member tubular portion 861 on the relief member bottom portion 862 side abuts. It is provided inside the discharge joint 70 so that the outer edge contacts the step surface 701 of the discharge joint 70 .

The relief hole 87 is formed in a substantially cylindrical shape so as to communicate between one central surface of the relief member bottom portion 862 and the other central surface. The relief valve seat 88 is annularly formed around the relief hole 87 on one surface of the relief member bottom portion 862 . Here, the relief valve seat 88 is formed in a tapered shape so as to approach the axis of the relief member tubular portion 861 as it goes from one axial side to the other axial side of the relief member tubular portion 861 . The relief hole 87 and the relief valve seat 88 are formed substantially coaxially with the relief member main body 86 .

The second flow path 89 is formed in a substantially cylindrical shape so as to communicate between one end surface and the other end surface of the relief member cylindrical portion 861 . Four second flow paths 89 are formed at regular intervals in the circumferential direction of the relief member cylindrical portion 861 .

The relief outer peripheral recessed portion 851 is formed in a substantially cylindrical shape so as to be recessed radially inward from the outer peripheral wall of the relief member tubular portion 861 . The relief lateral hole 852 is formed in a substantially cylindrical shape so as to communicate between the relief outer peripheral concave portion 851 and the inner peripheral wall of the relief member tubular portion 861 . Two relief lateral holes 852 are formed at intervals of 90 degrees in the circumferential direction of the relief member tubular portion 861 (see FIG. 35). By not arranging the two relief lateral holes 852 evenly in the circumferential direction, the relief valve 91 can be moved to one side during the valve opening operation to stabilize the flow. Note that if the two lateral relief holes 852 were evenly arranged in the circumferential direction, the deviation direction would not be constant due to variations in the negative pressure balance, and the behavior of the relief valve 91 could become unstable.

The lateral hole 853 is formed in a substantially cylindrical shape so that the relief outer peripheral concave portion 851 and the inner peripheral wall of the relief member cylindrical portion 861 communicate with each other on the opposite side of the relief member bottom portion 862 of the relief lateral hole 852 . One lateral hole 853 is formed in the relief member tubular portion 861 in the circumferential direction. The inner diameter of the lateral hole 853 and the inner diameter of the relief lateral hole 852 are the same.

Note that when the relief member main body 86 is provided inside the discharge joint 70 on the side opposite to the discharge sheet member 71 of the intermediate member 81, the annular groove 800 is formed between the first flow path 83 of the intermediate member 81 and the relief sheet. It connects with the second channel 89 of the member 85 . Further, in this embodiment, the axial length of the relief member tubular portion 861 in which the second flow path 89 is formed is longer than the axial length of the intermediate member main body 82 in which the first flow path 83 is formed.

As shown in FIGS. 37-39, the discharge valve 75 has a discharge valve contact portion 76 and a discharge valve sliding portion 77 . The discharge valve contact portion 76 is formed in a substantially disc shape. The outer diameter of the discharge valve contact portion 76 is smaller than the inner diameter of the discharge recess 721 of the discharge seat member 71 and larger than the inner diameter of the intermediate recess 821 of the intermediate member 81 . The discharge valve contact portion 76 is provided inside the discharge concave portion 721 so that the outer edge of one surface can contact the discharge valve seat 74 or be separated from the discharge valve seat 74 .

The discharge valve sliding portion 77 is formed integrally with the discharge valve contact portion 76 so as to project from the other surface of the discharge valve contact portion 76 in a substantially cylindrical shape. The discharge valve sliding portion 77 is formed substantially coaxially with the discharge valve contact portion 76 . The outer diameter of the discharge valve sliding portion 77 is slightly smaller than the inner diameter of the intermediate recess 821 . The discharge valve 75 is provided so as to be able to reciprocate in the axial direction while the outer peripheral wall of the discharge valve sliding portion 77 slides on the inner peripheral wall of the intermediate recess 821 .

A hole 771 is formed in the discharge valve sliding portion 77 . The hole portion 771 is formed in a substantially cylindrical shape so as to allow communication between the inner peripheral wall and the outer peripheral wall of the discharge valve sliding portion 77 . Four holes 771 are formed at equal intervals in the circumferential direction of the discharge valve sliding portion 77 . The hole portion 771 communicates the inner space and the outer space of the discharge valve sliding portion 77 .

In this embodiment, the inner peripheral wall of the discharge valve sliding portion 77 is tapered such that the inner diameter increases from the discharge valve contact portion 76 side toward the side opposite to the discharge valve contact portion 76 (see FIG. 37). reference). Therefore, it is possible to prevent the outer peripheral portion of the spring 79 from contacting the inner peripheral wall of the discharge valve sliding portion 77 . Moreover, since the inner peripheral wall of the discharge valve sliding portion 77 is not stepped, deburring can be simplified. Further, in the present embodiment, the end surface of the discharge valve contact portion 76 and the hole portion 771 are separated from the viewpoint of workability.

As shown in FIGS. 40 to 42, the relief valve 91 has a relief valve contact portion 92, a relief valve sliding portion 93, and a relief valve projecting portion 94. As shown in FIGS. The relief valve contact portion 92 is formed in a substantially cylindrical shape. The relief valve contact portion 92 is tapered such that the outer peripheral wall of one end portion approaches the shaft as it goes from the other to the other. The relief valve contact portion 92 is provided inside the relief member cylindrical portion 861 so that one end thereof can contact the relief valve seat 88 or can be separated from the relief valve seat 88 .

The relief valve sliding portion 93 is formed in a substantially cylindrical shape. The relief valve sliding portion 93 is formed integrally with the relief valve contact portion 92 so that one end thereof is connected to the other end of the relief valve contact portion 92 . The relief valve sliding portion 93 is formed substantially coaxially with the relief valve contact portion 92 . The outer diameter of the relief valve sliding portion 93 is slightly smaller than the inner diameter of the relief member tubular portion 861 . When the relief valve sliding portion 93 is provided inside the relief member tubular portion 861 , the outer peripheral wall of the relief valve sliding portion 93 can slide with the inner peripheral wall of the relief member tubular portion 861 .

The relief valve sliding portion 93 has an outer peripheral wall at the end on the relief valve contact portion 92 side that is tapered so as to approach the shaft from the side opposite to the relief valve contact portion 92 toward the relief valve contact portion 92 side. ing. When the relief valve contact portion 92 is in contact with the relief valve seat 88, the relief lateral hole 852 of the relief seat member 85 is closed by the outer peripheral wall of the relief valve sliding portion 93 (see FIG. 6).

The relief valve projecting portion 94 is formed in a substantially cylindrical shape. The relief valve projecting portion 94 is formed integrally with the relief valve sliding portion 93 so that one end thereof is connected to the center of the end surface of the relief valve sliding portion 93 opposite to the relief valve contact portion 92 . The relief valve projecting portion 94 is formed substantially coaxially with the relief valve sliding portion 93 . The outer diameter of the relief valve projecting portion 94 is smaller than the outer diameter of the relief valve sliding portion 93 . When the relief valve contact portion 92 is in contact with the relief valve seat 88 , the end surface of the relief valve projecting portion 94 opposite to the relief valve sliding portion 93 is aligned with the relief member bottom portion 862 of the relief member cylindrical portion 861 . is positioned closer to the relief member bottom 862 than the opposite end face (see FIG. 6).

As shown in FIG. 6, the locking member 95 is formed in a substantially cylindrical shape. The outer diameter of the locking member 95 is slightly larger than the inner diameter of the portion 807 of the inner peripheral wall of the relief member tubular portion 861 . The locking member 95 is press-fitted inside the relief member tubular portion 861 so that the outer peripheral wall thereof fits into the portion 807 of the inner peripheral wall of the relief member tubular portion 861 . That is, the locking member 95 is provided substantially coaxially with the relief member tubular portion 861 . The locking member 95 is provided in the vicinity of the end of the relief member tubular portion 861 opposite to the relief member bottom portion 862 in the axial direction of the relief member tubular portion 861 .

The inner diameter of the locking member 95 is larger than the outer diameter of the relief valve projecting portion 94 . When the relief valve contact portion 92 is in contact with the relief valve seat 88 , the end surface of the relief valve projecting portion 94 opposite to the relief valve sliding portion 93 is positioned inside the locking member 95 . A substantially cylindrical gap Sq1 is formed between the inner peripheral wall of the locking member 95 and the outer peripheral wall of the relief valve projecting portion 94 . That is, the inner peripheral wall of the locking member 95 and the outer peripheral wall of the relief valve projecting portion 94 do not slide.

As shown in FIGS. 43 and 44, the spring 79 is formed in a coil shape by winding a wire 790 made of metal. The spring 79 has a spring end face 791 and a spring end face 792 . The spring end face 791 is formed flat at one axial end of the spring 79 . The spring end face 792 is formed flat at the other axial end of the spring 79 .

The spring 79 is arranged so that the spring end face 791 contacts the bottom surface of the intermediate recess 821 of the intermediate member 81 and the spring end face 792 contacts the end face of the discharge valve contact portion 76 of the discharge valve 75 on the side of the discharge valve sliding portion 77 . It is provided inside the sliding portion 77 . In this state, the spring 79 can bias the discharge valve 75 to the side opposite to the intermediate member 81 . The wire diameter of the wire rod 790 is smaller than the inner diameter of the lateral hole 853 of the relief sheet member 85 .

As shown in FIGS. 45 and 46, the spring 99 is formed in a coil shape by winding a metal wire rod 990 . Here, the wire diameter of wire 990 is larger than the wire diameter of wire 790 . The spring 99 has a spring end face 991 and a spring end face 992 . The spring end face 991 is formed flat at one axial end of the spring 99 . The spring end face 992 is formed flat at the other axial end of the spring 99 .

The spring 99 is arranged so that the spring end face 991 contacts the end face of the relief valve sliding portion 93 on the relief valve projecting portion 94 side, and the spring end face 992 contacts the end face of the locking member 95 on the relief member bottom portion 862 side. It is provided inside the portion 861 . In this state, the spring 99 can bias the relief valve 91 toward the relief member bottom portion 862 . By adjusting the axial position of the locking member 95 with respect to the portion 807 of the inner peripheral wall of the relief member cylindrical portion 861, the biasing force of the spring 99 can be adjusted.

As described above, in the present embodiment, the intermediate member 81 has five, that is, an odd number of, first flow paths 83 formed at regular intervals in the circumferential direction. Further, the relief sheet member 85 is formed with four second flow paths 89 at regular intervals in the circumferential direction, that is, an even number of the second flow paths 89 . Also, the number of first flow paths 83 and the number of second flow paths 89 are coprime. Therefore, no matter how the intermediate member 81 and the relief sheet member 85 rotate relative to each other around the axis, the overlapping area of the first flow path 83 and the second flow path 89 when viewed from the axial direction of the intermediate member 81 is variation can be reduced. As a result, it is possible to suppress fluctuations in fuel flow depending on the relative positional relationship between the intermediate member 81 and the relief sheet member 85 in the rotational direction. Therefore, it is possible to suppress the variation in the ejection amount for each product.

In this embodiment, the discharge valve 75 includes a discharge valve contact portion 76 that can abut against the discharge valve seat 74, and a discharge valve contact portion 76 that is formed on the side of the intermediate member 81 that is slidable on the intermediate member 81. It has a discharge valve sliding portion 77 . The outer diameter of the discharge valve sliding portion 77 is smaller than the outer diameter of the discharge valve contact portion 76 .

When the discharge valve 75 is open, the plunger 11 moves to the side opposite to the pressure chamber 200 and the volume of the pressure chamber 200 increases, causing the fuel in the discharge recess 721 to flow toward the discharge hole 73 . The flow of fuel at this time hits the outer edge of the surface of the discharge valve sliding portion 77 side of the discharge valve contact portion 76, so that the discharge valve 75 can be quickly closed.

Further, in the present embodiment, the discharge sheet member 71 annularly protrudes toward the pressure chamber 200 from the pressure chamber 200 side surface of the discharge member main body 72 on the radially outer side of the discharge hole 73 and serves as a discharge passage forming portion. an inner projection 722 that abuts on the bottom surface of the discharge hole portion 214 of the housing 21; 21 has an outer protrusion 723 that contacts the bottom surface of the discharge hole 214 .

If the inner projection 722 is not formed and only the outer projection 723 is formed, a gap is formed between the inner edge portion of the end surface of the discharge member main body 72 on the pressurizing chamber 200 side and the bottom surface of the discharge hole portion 214 . be. In this case, when the discharge valve 75 comes into contact with the discharge valve seat 74 , the inner edge of the discharge member main body 72 inclines so as to deform toward the pressurizing chamber 200 and slips between the discharge seat member 71 and the discharge valve 75 . may occur and cause wear.

On the other hand, in this embodiment, the inner projection 722 is formed radially inward of the outer projection 723, so that when the discharge valve 75 abuts against the discharge valve seat 74, the inner edge of the discharge member main body 72 is in contact with the pressure chamber. It is possible to suppress tilting so as to deform toward the 200 side. Therefore, wear of the discharge seat member 71 and the discharge valve 75 can be suppressed.

By arranging the inner protrusion 722 at a position axially overlapping the sealing portion formed by the discharge valve 75, deformation of the discharge seat member 71 can be suppressed (see FIG. 6).

In addition, the inner projection 722 and the outer projection 723 contact the bottom surface of the discharge hole portion 214 without the end surface of the discharge member main body 72 on the pressurizing chamber 200 side contacting the bottom surface of the discharge hole portion 214. The surface pressure of the ejection sheet member 71 against the bottom surface of the ejection hole portion 214 can be ensured.

In this embodiment, the ejection sheet member 71, the intermediate member 81, and the relief sheet member 85 are set to have the same hardness. Here, the hardness of the intermediate member 81 may be lower than the hardness of the ejection sheet member 71 and the relief sheet member 85 . In this case, sealing performance can be improved.

Further, in this embodiment, the relief valve 91 includes a relief valve contact portion 92 that can contact the relief valve seat 88, and a relief member body 86 that is formed on the intermediate member 81 side of the relief valve contact portion 92 and is slidable. It has a relief valve sliding portion 93 . The center of gravity of the relief valve 91 is set at the relief valve sliding portion 93 . Therefore, when grinding the sliding portion of the relief valve sliding portion 93 with the relief member main body 86, the relief valve 91 does not easily fall down, so grinding is easy. Further, if the center of gravity is set in the relief valve sliding portion 93 that slides on the relief member main body 86, force is applied to the location where the center of gravity is located, so that the movement of the relief valve 91 is stabilized.

Moreover, in this embodiment, the relief member main body 86 is formed in a tubular shape. The relief sheet member 85 has a lateral hole 853 connecting the inner peripheral wall and the outer peripheral wall of the relief member main body 86 . This embodiment further includes a spring 99 as a relief valve biasing member. The spring 99 is formed in a coil shape by winding a wire 990, is provided inside the relief member main body 86, and biases the relief valve 91 toward the relief valve seat 88 side. The wire diameter of wire 990 is smaller than the inner diameter of lateral hole 853 . Therefore, it is possible to prevent the horizontal hole 853 from being blocked by the wire rod 990 of the spring 99 .

Moreover, in this embodiment, the relief member main body 86 is formed in a tubular shape. The relief valve 91 includes a relief valve contact portion 92 that can contact a relief valve seat 88, and a relief valve sliding portion formed on the intermediate member 81 side of the relief valve contact portion 92 and slidable on the inner peripheral wall of the relief member main body 86. 93 , and a relief valve projecting portion 94 projecting from the relief valve sliding portion 93 toward the intermediate member 81 . This embodiment further includes a spring 99 and a locking member 95 as relief valve biasing members. A spring 99 is provided inside the relief member main body 86 and biases the relief valve 91 toward the relief valve seat 88 side. The locking member 95 is formed in a cylindrical shape, is provided inside the relief member main body 86 so that a part of the relief valve projecting portion 94 is positioned inside, and locks the end of the spring 99 . A cylindrical gap Sq1 is formed between the outer peripheral wall of the relief valve projecting portion 94 and the inner peripheral wall of the locking member 95 . Therefore, when the relief valve 91 opens and moves toward the pressurizing chamber 200, the fuel between the locking member 95 and the relief valve sliding portion 93 flows toward the pressurizing chamber 200 through the gap Sq1. be able to. As a result, it is possible to prevent the fuel in the space between the locking member 95 and the relief valve sliding portion 93 from acting as a damper and acting as a resistance to the movement of the relief valve 91 in the valve opening direction.

Further, in the present embodiment, the intermediate member 81 can restrict the movement of the relief valve 91 toward the pressurizing chamber 200 when coming into contact with the relief valve 91 . Further, in this embodiment, when fuel is discharged from the pressurizing chamber 200, the pressure in the space on the side of the pressurizing chamber 200 with respect to the intermediate member 81 in the discharge passage 705 is It becomes higher than the pressure in the space on the relief sheet member 85 side. Therefore, pressure acts on the intermediate member 81 from the pressure chamber 200 side toward the relief sheet member 85 side. As a result, the stress on the contact surface of the intermediate member 81 with the relief valve 91 increases. Therefore, even if the relief valve 91 comes into contact with the intermediate member 81, it is possible to suppress the intermediate member 81 from moving toward the pressurizing chamber 200 side.

As described above, (C1) the high-pressure pump 10 of this embodiment includes the cylinder 23 as a pressure chamber forming portion, the upper housing 21 as a discharge passage forming portion, the discharge sheet member 71, the intermediate member 81, and the relief sheet member. 85 , a discharge valve 75 and a relief valve 91 .

Cylinder 23 forms a pressure chamber 200 in which fuel is pressurized. The upper housing 21 forms a discharge passage 217 through which fuel discharged from the pressurization chamber 200 flows. The discharge sheet member 71 includes a discharge member main body 72 provided in the discharge passage 217, a discharge hole 73 that communicates between a surface of the discharge member main body 72 on the side of the pressure chamber 200 and a surface opposite to the pressure chamber 200, and A discharge valve seat 74 is formed around the discharge hole 73 on the side of the discharge member main body 72 opposite to the pressurizing chamber 200 .

The intermediate member 81 includes an intermediate member main body 82 provided on the opposite side of the discharge sheet member 71 from the pressurizing chamber 200, a surface of the intermediate member main body 82 on the pressurizing chamber 200 side, and a surface on the opposite side from the pressurizing chamber 200. It has a first flow path 83 that communicates with. The relief sheet member 85 includes a relief member main body 86 provided on the opposite side of the intermediate member 81 from the pressurizing chamber 200, a surface of the relief member main body 86 on the pressurizing chamber 200 side, and a surface on the opposite side from the pressurizing chamber 200. and a relief valve seat 88 formed around the relief hole 87 on the pressure chamber 200 side surface of the relief member main body 86, and the pressure chamber 200 side surface of the relief member main body 86. It has a second flow path 89 that communicates with the surface opposite to the pressurizing chamber 200 .

The discharge valve 75 is provided on the intermediate member 81 side of the discharge seat member 71 , and is separated from the discharge valve seat 74 to open or contact the discharge valve seat 74 to close, thereby permitting or allowing the flow of fuel in the discharge hole 73 . Regulatable. The relief valve 91 is provided on the intermediate member 81 side of the relief seat member 85, and is separated from the relief valve seat 88 to open or to contact the relief valve seat 88 to close, thereby permitting or allowing the flow of fuel in the relief hole 87. Regulatable.

At least one of the intermediate member 81 and the relief sheet member 85 is an annular groove that is annularly formed in the mutually facing surfaces of the intermediate member main body 82 and the relief member main body 86 and connects the first flow path 83 and the second flow path 89. has 800. Therefore, the first flow path 83 and the second flow path 89 can communicate with each other via the annular groove 800 regardless of how the intermediate member 81 and the relief sheet member 85 rotate relative to each other around the axis. . Thereby, regardless of the relative position between the intermediate member 81 and the relief sheet member 85, a flow path for the fuel discharged from the pressurizing chamber 200 to the engine 1 side can be secured.

In this embodiment, the discharge valve 75 is arranged near the pressurizing chamber 200 , and the relief valve 91 is arranged on the side opposite to the pressurizing chamber 200 with respect to the discharge valve 75 . Therefore, dead volume that communicates with the pressurization chamber 200 and becomes a high-pressure space during pressurization can be reduced. Thereby, high-pressure fuel can be discharged from the high-pressure pump 10 .

Further, in the present embodiment, the discharge valve 75 and the relief valve 91 can be arranged coaxially and integrated in a predetermined range. Thereby, the discharge passage portion 700, which is a portion including the discharge valve 75 and the relief valve 91, can be downsized, and as a result, the high-pressure pump 10 can be downsized.

(C2) In the present embodiment, a plurality of first flow paths 83 are formed in the intermediate member main body 82 in the circumferential direction. A plurality of second flow paths 89 are formed in the relief member main body 86 in the circumferential direction. Therefore, the flow rate of the fuel discharged from the pressurizing chamber 200 to the engine 1 side can be ensured.

Note that when a plurality of first flow paths 83 and a plurality of second flow paths 89 are formed, depending on the relative positions of the intermediate member 81 and the relief sheet member 85, the first flow path when viewed from the axial direction of the intermediate member 81 may vary. There is a possibility that the overlapping area of the first channel 83 and the second channel 89 will be extremely small. However, in this embodiment, since the intermediate member 81 is formed with the annular groove 800 connecting the first flow path 83 and the second flow path 89, the relative positions of the intermediate member 81 and the relief sheet member 85 Regardless, the flow rate of the fuel discharged from the pressurizing chamber 200 to the engine 1 side can be ensured.

(C3) In the present embodiment, the number of first flow paths 83 and the number of second flow paths 89 are different. Therefore, the deviation angle between the center of the first flow path 83 and the center of the second flow path 89 can be reduced.

Also, (C4) in the present embodiment, the number of first flow paths 83 is greater than the number of second flow paths 89 . An annular groove 800 is formed in the intermediate member body 82 . That is, the annular groove 800 is formed in the intermediate member 81, which is the member having the greater number of flow passages, out of the intermediate member 81 and the relief sheet member 85. As shown in FIG.

In general, the tip of a tooth tool that cuts a member to form a groove has an R-shaped corner. It is formed. When the first flow path 83 intersects the R-shaped corner of the annular groove 800, a sharp corner is formed at the intersection, and stress concentrates on the corner. Therefore, in terms of strength, it is necessary to reduce the flow area of the first flow path 83 so that the first flow path 83 does not intersect the rounded corners of the annular groove 800 . In this embodiment, even if the flow area of the first flow path 83 is reduced, the number of the first flow paths 83 is reduced to that of the second flow paths 89 in order to ensure the flow rate of the fuel flowing through the first flow paths 83. More than a number.

(C5) In the present embodiment, the number of first flow paths 83 and the number of second flow paths 89 are coprime. Therefore, no matter how the intermediate member 81 and the relief sheet member 85 rotate relative to each other around the axis, the overlapping area of the first flow path 83 and the second flow path 89 when viewed from the axial direction of the intermediate member 81 is variation can be reduced. As a result, it is possible to suppress fluctuations in fuel flow depending on the relative positional relationship between the intermediate member 81 and the relief sheet member 85 in the rotational direction. Therefore, it is possible to suppress the variation in the ejection amount for each product.

Also, (C6) in the present embodiment, the number of first flow paths 83 is greater than the number of second flow paths 89 . The length of the first channel 83 is shorter than the length of the second channel 89 . Since the number of the first flow paths 83 is greater than the number of the second flow paths 89, the flow rate can be ensured even if the flow path area per one of the first flow paths 83 is reduced. For example, when the flow area of the first flow path 83 is reduced, the diameter of the hole forming the first flow path 83 is reduced, which may make processing difficult. However, in this embodiment, the length of the first channel 83 is shorter than the length of the second channel 89 . Therefore, even if the flow path area of the first flow path 83 is reduced, the processing of the first flow path 83 is easy.

In addition, (C7) the present embodiment further includes a discharge joint 70 . The discharge joint 70 is formed in a cylindrical shape, accommodates therein a discharge seat member 71 , an intermediate member 81 , a relief seat member 85 , a discharge valve 75 and a relief valve 91 , and has an outer peripheral wall coupled to the upper housing 21 . there is Therefore, the discharge joint 70, the discharge seat member 71, the intermediate member 81, the relief seat member 85, the discharge valve 75, and the relief valve 91 can be integrally assembled in advance to form a subassembly. As a result, assembly of the entire high-pressure pump 10 is facilitated, and the high-pressure pump 10 can be manufactured easily.

(Second embodiment)
<A-2> FIGS. 47 and 48 show part of the high-pressure pump according to the second embodiment. 2nd Embodiment differs in the structure of the valve member 40 from 1st Embodiment.

In this embodiment, the boundary line B1 between the inner edge portion of the tapered portion 42 on the radially outer side of the first region T1 of the valve body 41 and the outer edge portion of the valve body 41 extends from the center of the valve body 41 to the first region T1. and a straight line LC11 extending from the center of the valve body 41 and passing through the center of the communication hole 443 of the first region T1.

A boundary line B1 between the inner edge of the radially outer tapered portion 42 of the second region T2 of the valve body 41 and the outer edge of the valve body 41, and the radially outer tapered portion 42 of the third region T3 of the valve body 41. A boundary line B1 between the inner edge of the valve body 41 and the outer edge of the valve body 41 is also formed in the same manner as described above.

That is, (A4) In the present embodiment, the boundary line B1 between the inner edge of one tapered portion 42 sandwiched between the two guide portions 43 and the outer edge of the valve body 41 extends from the center of the valve body 41 to form a tapered portion. The inner edge of the portion 42 is formed in a range between two straight lines LC11 passing through the centers of the end communication holes (441, 443), which are the communication holes 44 at both ends of the plurality of communication holes 44 facing each other. Therefore, the distance between both ends of each boundary line B1 and the communication hole 44 can be reduced while ensuring the length of each boundary line B1, and the portions near both ends of each boundary line B1 act as resistance to the flow of fuel. can be suppressed.

(Third embodiment)
<A-3> FIGS. 49 and 50 show part of the high-pressure pump according to the third embodiment. 3rd Embodiment differs in the structure of the valve member 40 from 2nd Embodiment.

In the present embodiment, the guide portion 43 through which the straight line L11 between the first region T1 and the second region T2 passes is a portion that slides on the inner peripheral wall of the stopper recessed portion 351 of the stopper 35 as the intake passage forming portion. The moving part 430 extends from the center of the valve body 41 and extends along the tangent line LT21, which is the tangent line on the communication hole 441 side of the second region T2 among the two tangent lines passing through the outer edge of the communication hole 443 of the first region T1, and the valve body 41. and a tangent line LT21 extending from the center of the second region T2 and passing through the outer edge of the communication hole 441 in the second region T2.

The same applies to the guide portion 43 through which the straight line L11 between the second region T2 and the third region T3 passes and the guide portion 43 through which the straight line L11 between the third region T3 and the first region T1 passes. formed.

That is, (A5) In the present embodiment, the guide portion 43 is such that the sliding portion 430, which is a portion that slides against the stopper concave portion 351 of the stopper 35, extends from the center of the valve body 41 and extends between the two adjacent communication holes 44. It is formed in a range between two tangent lines LT21 passing through the outer edges facing each other. Therefore, the size of the sliding portion 430 of the guide portion 43 can be set according to the distance between the adjacent communication holes 44, and the sliding portion 430 can be prevented from interfering with the flow of fuel.

(Fourth embodiment)
<A-4> FIGS. 51 and 52 show part of the high-pressure pump according to the fourth embodiment. 4th Embodiment differs in the structure of the valve member 40 from 1st Embodiment.

In this embodiment, four guide portions 43 are formed at equal intervals in the circumferential direction of the valve body 41 so as to divide the tapered portion 42 into four in the circumferential direction. Eight communication holes 44 are formed at equal intervals in the circumferential direction of the valve body 41 . The communication hole 44 is arranged on a virtual circle VC1 centered on the axis Ax2 of the valve body 41 (see FIGS. 51 and 52). As shown in FIG. 51, a boundary line B1 between the inner edges of the four tapered portions 42 and the outer edge of the valve body 41 is formed along a concentric circle CC1 with respect to the virtual circle VC1.

As shown in FIG. 51 , the communication hole 44 includes a first region T1, a second region T2, and a second region T2 defined by four straight lines L11 extending from the center of the valve body 41 and passing through the center of the guide portion 43. Two are formed in each of the third region T3 and the fourth region T4.
Here, if the number of the communication holes 44 is h=8 and the number of the guide portions 43 is g=4, the inner edge portion of one of the tapered portions 42 divided by the guide portion 43 is opposed to the inner edge portion of one of the tapered portions 42 . The number of communicating holes 44 to be connected is h/g=8/4=2.

Also, the two communication holes 44 formed in the first region T1, the second region T2, the third region T3, and the fourth region T4 are sequentially connected to the communication holes 441 in the circumferential direction of the virtual circle VC1. Assuming the hole 442, the boundary line B1 between the inner edge portion of the tapered portion 42 on the radially outer side of the first region T1 of the valve body 41 and the outer edge portion of the valve body 41 is the outer edge of the communication hole 441 in the first region T1 and , through the outer edge of the communication hole 442 of the second region T2 formed at a position line-symmetrical to the communication hole 441 of the first region T1 with respect to the straight line L11 between the first region T1 and the second region T2. A tangent line LT31, which is a tangent line on the opposite side of the tangent lines to the third region T3 and the fourth region T4, the outer edge of the communication hole 442 in the first region T1, and a line between the first region T1 and the fourth region T4. The second region T2 and the third region T3 are two tangent lines passing through the outer edge of the communication hole 441 of the fourth region T4 formed at a position symmetrical to the communication hole 442 of the first region T1 with respect to the straight line L11. It is formed in the range between the tangent line LT31, which is the tangent line on the opposite side.

Boundary line B1 between the inner edge of the tapered portion 42 on the radially outer side of the second region T2 of the valve body 41 and the outer edge of the valve body 41, the inner edge of the tapered portion 42 on the radially outer side of the third region T3 of the valve body 41 and the outer edge of the valve body 41, and the boundary B1 between the inner edge of the tapered portion 42 on the radially outer side of the fourth region T4 of the valve body 41 and the outer edge of the valve body 41. It is formed in the same manner as above.

That is, (A3) In the present embodiment, the boundary line B1 between the inner edge of one tapered portion 42 sandwiched between the two guide portions 43 and the outer edge of the valve body 41 is defined by the inner edge of the single tapered portion 42. Outer edges of the end communication holes (441, 442), which are the communication holes 44 at both ends of the plurality of opposing communication holes 44, and a straight line L11 extending from the center of the valve main body 41 and passing through the center of the guide portion 43. It is formed in a range between two tangent lines LT31 passing through the outer edges of the communication holes 44 (442, 441) formed at positions line-symmetrical to the communication holes (441, 442). Therefore, the distance between both ends of each boundary line B1 and the communication hole 44 can be reduced while ensuring the length of each boundary line B1, and the portions near both ends of each boundary line B1 act as resistance to the flow of fuel. can be suppressed.

Further, in this embodiment, four guide portions 43 are formed in the circumferential direction of the valve member 40 . Therefore, compared with the first embodiment having three guide portions 43, eccentricity is reduced, and the effect of suppressing inclination of the valve member 40 can be obtained.

(Fifth embodiment)
<A-5> FIG. 53 shows part of the high-pressure pump according to the fifth embodiment. The fifth embodiment differs from the first embodiment in the configuration of the discharge passage portion 700 .

In this embodiment, the discharge passage portion 700 has the seat member 31 , the stopper 35 , the valve member 40 and the spring 39 instead of the discharge seat member 71 , the intermediate member 81 , the discharge valve 75 and the spring 79 .

In the present embodiment, the discharge joint 70 is formed so that the end surface on the side of the pressure chamber 200 is located on the side opposite to the pressure chamber 200 with respect to the end surface on the side of the pressure chamber 200 of the discharge joint 70 of the first embodiment. It is That is, the axial length of the discharge joint 70 of the present embodiment is shorter than the axial length of the discharge passage portion 700 of the first embodiment.

The sheet member 31 is provided in the discharge passage 217 so that one surface thereof contacts the bottom surface of the discharge hole portion 214 . Here, the sheet member recessed portion 312 is formed in the sheet member 31 . The sheet member recess 312 is formed in a substantially cylindrical shape so as to be recessed from the pressure chamber 200 side surface of the sheet member 31 toward the side opposite to the pressure chamber 200 . The sheet member recessed portion 312 is formed substantially coaxially with the sheet member 31 . The communication path 32 and the communication path 33 communicate between the bottom surface of the sheet member recess 312 and the surface of the sheet member 31 opposite to the pressure chamber 200 .

The structure of the stopper 35 of the discharge passage portion 700 is similar to that of the stopper 35 of the suction valve portion 300 . The stopper 35 is provided on the side of the sheet member 31 opposite to the pressure chamber 200 . Here, the surface of the stopper large-diameter portion 37 opposite to the stopper small-diameter portion 36 is in contact with the outer edge portion of the surface of the sheet member 31 opposite to the pressure chamber 200 . Further, the stopper small diameter portion 36 is positioned inside the end portion of the discharge joint 70 on the pressure chamber 200 side. A stepped surface between the stopper small-diameter portion 36 and the stopper large-diameter portion 37 faces the end surface of the discharge joint 70 on the pressurizing chamber 200 side. Further, the outer edge portion of the surface of the stopper small diameter portion 36 opposite to the stopper large diameter portion 37 is in contact with the end surface of the relief member tubular portion 861 on the pressure chamber 200 side.

Here, the step surface 701 of the discharge joint 70 biases the relief sheet member 85, the stopper 35, and the sheet member 31 toward the pressure chamber 200 side. Therefore, the relief sheet member 85, the stopper 35, and the sheet member 31 are in contact with each other, and movement in the axial direction is restricted. In addition, the surface of the sheet member 31 on the side of the pressurizing chamber 200 is pressed against the stepped surface between the discharge hole portions 214 and 215 , that is, the periphery of the discharge hole portion 215 on the bottom surface of the discharge hole portion 214 . there is Therefore, an axial force from the sheet member 31 toward the pressurizing chamber 200 side acts around the discharge hole portion 215 on the bottom surface of the discharge hole portion 214 . This makes it possible to seal under high pressure with a simple structure.

The stopper 35 is provided so that the communication hole 38 and the second flow path 89 of the relief sheet member 85 communicate with each other. In this embodiment, the pressurizing chamber 200 includes a discharge hole 233 , a discharge hole portion 215 , a seat member recessed portion 312 , a communication passage 32 , a communication passage 33 , a stopper recessed portion 351 , a stopper recessed portion 352 , a communication hole 38 , a second flow path 89 . can be communicated with the high-pressure fuel pipe 8 via the .

The valve member 40 and the spring 39 of the discharge passage portion 700 are similar in structure to the valve member 40 and the spring 39 of the suction valve portion 300 . The valve member 40 is provided inside the stopper concave portion 351 in the same manner as the valve member 40 of the suction valve portion 300 . The spring 39 is also provided radially outside the stopper protrusion 353 in the same manner as the spring 39 of the intake valve portion 300 .

When the pressure of the fuel in the pressurization chamber 200 rises above a predetermined value, the valve member 40 moves toward the high-pressure fuel pipe 8 against the biasing force of the spring 39 . As a result, the valve member 40 is separated from the valve seat 310 to open the valve. Therefore, the fuel on the pressurizing chamber 200 side of the seat member 31 flows through the seat member recessed portion 312 , the communicating passage 32 , the communicating passage 33 , the valve seat 310 , the stopper recessed portion 351 , the stopper recessed portion 352 , the communicating hole 38 , the second flow path 89 . and is discharged to the high-pressure fuel pipe 8 side.

As described above, this embodiment includes the cylinder 23 as a pressure chamber forming portion, the upper housing 21 as a discharge passage forming portion, the seat member 31 and the valve member 40 . Cylinder 23 forms a pressure chamber 200 in which fuel is pressurized. The upper housing 21 forms a discharge passage 217 through which fuel discharged from the pressurization chamber 200 flows.

The sheet member 31 has a communication passage 32 and a communication passage 33 provided in the discharge passage 217 and communicating between one surface and the other surface. The valve member 40 is provided on the opposite side of the seat member 31 from the pressurizing chamber 200 , and when separated from the seat member 31 , the valve member 40 opens to allow the flow of fuel in the communication passages 32 and 33 and hits the seat member 31 . When they come into contact with each other, the valve closes and the flow of fuel in the communicating passages 32 and 33 can be regulated.

The valve member 40 includes a plate-like valve body 41 that can be separated from or abutted against the seat member 31 , a plurality of communication holes 44 communicating between one surface and the other surface of the valve body 41 , and the valve body 41 . The surface opposite to the pressure chamber 200 is formed in a tapered shape so as to approach the axis Ax2 of the valve body 41 as it goes from the side opposite to the pressure chamber 200 toward the pressure chamber 200 side. A tapered portion 42, and a plurality of tapered portions 42 projecting radially outward from the valve body 41 so as to divide the tapered portion 42 in the circumferential direction into a plurality of pieces, and capable of guiding the movement of the valve member 40 by sliding on the stopper concave portion 351 of the stopper 35. It has a guide portion 43 . The plurality of communication holes 44 are arranged on a virtual circle VC1 centered on the axis Ax2 of the valve body 41. As shown in FIG.

A boundary line B1 between the inner edge of the tapered portion 42 and the outer edge of the valve body 41 is formed along the concentric circle CC1 with respect to the virtual circle VC1. Therefore, the distance between both ends of each boundary line B1 and the communication hole 44 can be reduced. As a result, it is possible to suppress the portions near both ends of each boundary line B<b>1 from acting as resistance to the fuel flowing on the surface of the valve member 40 . Therefore, a sufficient flow rate of fuel discharged from the pressurizing chamber 200 can be ensured. Further, by reducing the lift amount of the valve member 40, the valve closing responsiveness is improved, the reverse flow rate is reduced, and the discharge amount of the high-pressure pump 10 can be secured.

Thus, this embodiment shows an example in which the multi-seat type valve member 40 is applied as a discharge valve in the discharge passage 217. As shown in FIG.

(Sixth embodiment)
<A-6> FIG. 54 shows part of the high-pressure pump according to the sixth embodiment. The sixth embodiment differs from the first embodiment in the configuration of the valve member 40 .

In this embodiment, the valve member 40 has one surface 401 in the axial direction, that is, the surface on the side of the seat member 31, and the other surface 402, that is, the pressurizing chamber, in a cross section along a virtual plane VP1 that includes the axis Ax2 of the valve body 41. The surface on the 200 side is formed to be curved. Here, one surface 401 and the other surface 402 of the valve member 40 are formed to be convex toward the seat member 31 side. That is, the valve member 40 is formed so as to curve toward the pressurizing chamber 200 as it goes radially outward from the center.

The amount of bending QC1 of one surface 401 in the axial direction and the amount of bending QC2 of the other surface 402 of the valve member 40 correspond to the amount of bending between the valve member 40 and the seat member 31 when the valve member 40 is separated from the seat member 31. It is set smaller than the minimum distance DL1. Here, the minimum value DL1 is the pressure applied between the one surface 401 of the valve member 40 and the seat member 31 on the axis Ax2 of the valve body 41 when the other surface 402 of the valve member 40 is in contact with the stopper convex portion 353. It is equal to the distance to the surface on the chamber 200 side (see FIG. 54). Incidentally, in the present embodiment, the amount of bending QC1 and the amount of bending QC2 are the same.

In the present embodiment, when the plunger 11 moves toward the pressurizing chamber 200 and the volume of the pressurizing chamber 200 decreases, when the coil 60 of the electromagnetic drive unit 500 is energized, the needle 53 moves away from the pressurizing chamber 200. It moves to the opposite side, and the valve member 40 moves in the valve closing direction. At this time, the pressure of the fuel in the pressure chamber 200 acts on the other surface 402 of the valve member 40 . Therefore, as indicated by broken lines in FIG. 54, the outer edge of the valve member 40 deforms toward the seat member 31, and one surface 401 becomes the surface of the seat member 31 on the pressure chamber 200 side, that is, a plurality of valve seats. Adhere to 310. Thereby, the valve member 40 is closed.

As described above, in this embodiment, one surface 401 of the valve member 40 is curved and formed to be convex toward the seat member 31 side. Therefore, if the minimum value DL1 is the lift amount QL1 of the valve member 40, the apparent lift amount of the valve member 40 at the outer edge of the valve member 40 is larger than the lift amount QL1 by the bending amount QC1. As a result, the amount of fuel sucked into the pressurization chamber 200, the amount of fuel returned from the pressurization chamber 200 to the fuel chamber 260 side, and the self-closing limit of the valve member 40 can be improved.

As described above, (A6) in the present embodiment, the valve member 40 is configured so that one surface 401, which is the surface on the side of the seat member 31, is curved in a cross section along the virtual plane VP1 including the axis Ax2 of the valve body 41. formed. Therefore, in a part of the valve member 40 , the apparent lift amount of the valve member 40 is increased by the amount of curvature of the one surface 401 . As a result, the amount of fuel sucked into the pressurization chamber 200, the amount of fuel returned from the pressurization chamber 200 to the fuel chamber 260 side, and the self-closing limit of the valve member 40 can be improved. Therefore, the lift amount of the valve member 40 for ensuring the same performance can be reduced, and the power consumption of the electromagnetic drive unit 500 and the NV can be reduced.

(A7) In the present embodiment, the valve member 40 has a surface 401 on the side of the seat member 31 whose curvature amount QC1 is the same as that of the valve member 40 and the seat member 31 when the valve member 40 is separated from the seat member 31 . It is set smaller than the minimum value DL1 of the distance to the member 31 .

(A8) In the present embodiment, the valve member 40 is formed so that one surface 401, which is the surface on the side of the seat member 31, is convex toward the side of the seat member 31. As shown in FIG. This embodiment shows an example of a specific configuration of the valve member 40 .

(Seventh embodiment)
<A-7> FIG. 55 shows part of the high-pressure pump according to the seventh embodiment. The seventh embodiment differs from the first embodiment in the configuration of the valve member 40 .

In this embodiment, the valve member 40 has one surface 401 in the axial direction, that is, the surface on the side of the seat member 31, and the other surface 402, that is, the pressurizing chamber, in a cross section along a virtual plane VP1 that includes the axis Ax2 of the valve body 41. The surface on the 200 side is formed to be curved. Here, one surface 401 and the other surface 402 of the valve member 40 are formed to be convex toward the pressurizing chamber 200 side. That is, the valve member 40 is formed so as to curve toward the seat member 31 as it goes radially outward from the center.

The amount of bending QC1 of one surface 401 in the axial direction and the amount of bending QC2 of the other surface 402 of the valve member 40 correspond to the amount of bending between the valve member 40 and the seat member 31 when the valve member 40 is separated from the seat member 31. It is set smaller than the minimum distance DL1. Here, the minimum value DL1 is the distance between the outer edge portion of one surface 401 of the valve member 40 and the pressure chamber 200 side of the seat member 31 when the other surface 402 of the valve member 40 is in contact with the stopper protrusion 353 . Equal to the distance to the surface (see Figure 55). Incidentally, in the present embodiment, the amount of bending QC1 and the amount of bending QC2 are the same.

In the present embodiment, when the plunger 11 moves toward the pressurizing chamber 200 and the volume of the pressurizing chamber 200 decreases, when the coil 60 of the electromagnetic drive unit 500 is energized, the needle 53 moves away from the pressurizing chamber 200. It moves to the opposite side, and the valve member 40 moves in the valve closing direction. At this time, the pressure of the fuel in the pressure chamber 200 acts on the other surface 402 of the valve member 40 . 55, the central portion of the valve member 40 is deformed toward the seat member 31, and one surface 401 is the surface of the seat member 31 facing the pressure chamber 200, that is, the plurality of valve seats. Adhere to 310. Thereby, the valve member 40 is closed.

As described above, in the present embodiment, one surface 401 of the valve member 40 is curved and formed to protrude toward the pressurizing chamber 200 side. Therefore, if the minimum value DL1 is the lift amount QL1 of the valve member 40, the apparent lift amount of the valve member 40 at the central portion of the valve member 40 is larger than the lift amount QL1 by the bending amount QC1. As a result, the amount of fuel sucked into the pressurization chamber 200, the amount of fuel returned from the pressurization chamber 200 to the fuel chamber 260 side, and the self-closing limit of the valve member 40 can be improved.

(Eighth embodiment)
<A-8> FIG. 56 shows part of the high-pressure pump according to the eighth embodiment. The eighth embodiment differs from the sixth embodiment in the configuration of the valve member 40 .

In this embodiment, the other surface 402 of the valve member 40 on the side of the pressurizing chamber 200 is formed flat. That is, the curvature amount of the other surface 402 is zero.

In the present embodiment, when the plunger 11 moves toward the pressurizing chamber 200 and the volume of the pressurizing chamber 200 decreases, when the coil 60 of the electromagnetic drive unit 500 is energized, the needle 53 moves away from the pressurizing chamber 200. It moves to the opposite side, and the valve member 40 moves in the valve closing direction. At this time, the pressure of the fuel in the pressure chamber 200 acts on the other surface 402 of the valve member 40 . 56, the outer edge of the valve member 40 is deformed toward the seat member 31, and one surface 401 is the surface of the seat member 31 on the pressure chamber 200 side, that is, the plurality of valve seats. Adhere to 310. Thereby, the valve member 40 is closed.

In this embodiment, as in the sixth embodiment, one surface 401 of the valve member 40 is curved and formed to protrude toward the seat member 31 side. Therefore, the same effects as in the sixth embodiment can be obtained.

(Ninth embodiment)
<A-9> FIG. 57 shows part of the high-pressure pump according to the ninth embodiment. The ninth embodiment differs from the seventh embodiment in the configuration of the valve member 40 .

In this embodiment, the other surface 402 of the valve member 40 on the side of the pressurizing chamber 200 is formed flat. That is, the curvature amount of the other surface 402 is zero.

In the present embodiment, when the plunger 11 moves toward the pressurizing chamber 200 and the volume of the pressurizing chamber 200 decreases, when the coil 60 of the electromagnetic drive unit 500 is energized, the needle 53 moves away from the pressurizing chamber 200. It moves to the opposite side, and the valve member 40 moves in the valve closing direction. At this time, the pressure of the fuel in the pressure chamber 200 acts on the other surface 402 of the valve member 40 . 57, the central portion of the valve member 40 is deformed toward the seat member 31, and one surface 401 is the surface of the seat member 31 on the pressure chamber 200 side, that is, a plurality of valve seats. Adhere to 310. Thereby, the valve member 40 is closed.

In this embodiment, as in the seventh embodiment, one surface 401 of the valve member 40 is curved and formed to protrude toward the pressurizing chamber 200 side. Therefore, the same effects as in the seventh embodiment can be obtained.

(Tenth embodiment)
<A-10> FIG. 58 shows part of the high-pressure pump according to the tenth embodiment. The tenth embodiment differs from the first embodiment in the configuration of the valve member 40 .

In the present embodiment, the guide portion 43 of the valve member 40 has a surface on the side of the seat member 31 and a surface on the side of the pressurizing chamber 200 in a cross section along a virtual plane VP1 including the axis Ax2 of the valve body 41 . It is formed to curve toward the pressure chamber 200 side. That is, the guide portion 43 is formed so as to curve toward the pressure chamber 200 as it extends radially outward from the valve body 41 .

The amount of curvature QC3 of the surface on the side of the seat member 31 and the amount of curvature QC4 of the surface on the side of the pressurizing chamber 200 of the guide portion 43 are the same as those of the valve member 40 and the seat member 31 when the valve member 40 is separated from the seat member 31. is set smaller than the minimum value DL1 of the distance from Here, the minimum value DL1 is the pressure applied between the one surface 401 of the valve member 40 and the seat member 31 on the axis Ax2 of the valve body 41 when the other surface 402 of the valve member 40 is in contact with the stopper convex portion 353. It is equal to the distance to the surface on the chamber 200 side (see FIG. 58). Incidentally, in the present embodiment, the amount of bending QC3 and the amount of bending QC4 are the same.

In the present embodiment, when the plunger 11 moves toward the pressurizing chamber 200 and the volume of the pressurizing chamber 200 decreases, when the coil 60 of the electromagnetic drive unit 500 is energized, the needle 53 moves away from the pressurizing chamber 200. It moves to the opposite side, and the valve member 40 moves in the valve closing direction. At this time, the pressure of the fuel in the pressurizing chamber 200 acts on the surface of the guide portion 43 on the pressurizing chamber 200 side. 58, the guide portion 43 of the valve member 40 is deformed toward the seat member 31, and the surface on the seat member 31 side becomes the surface of the seat member 31 on the pressure chamber 200 side, that is, the valve It adheres to the seat 310 . Thereby, the valve member 40 is closed.

As described above, in the present embodiment, the surface of the guide portion 43 of the valve member 40 on the side of the seat member 31 is formed so as to curve from the valve body 41 toward the pressurizing chamber 200 side. Therefore, if the minimum value DL1 is the lift amount QL1 of the valve member 40, the apparent lift amount of the valve member 40 at the guide portion 43 of the valve member 40 is larger than the lift amount QL1 by the bending amount QC3. As a result, the amount of fuel sucked into the pressurization chamber 200, the amount of fuel returned from the pressurization chamber 200 to the fuel chamber 260 side, and the self-closing limit of the valve member 40 can be improved.

(Eleventh embodiment)
<A-11> FIG. 59 shows part of the high-pressure pump according to the eleventh embodiment. The eleventh embodiment differs from the tenth embodiment in the configuration of the valve member 40 .

In the present embodiment, the guide portion 43 of the valve member 40 has a surface on the side of the seat member 31 and a surface on the side of the pressurizing chamber 200 in a cross section along a virtual plane VP1 including the axis Ax2 of the valve body 41. It is formed so as to curve toward the member 31 side. That is, the guide portion 43 is formed so as to curve toward the seat member 31 as it extends radially outward from the valve body 41 .

The amount of curvature QC3 of the surface on the side of the seat member 31 and the amount of curvature QC4 of the surface on the side of the pressurizing chamber 200 of the guide portion 43 are the same as those of the valve member 40 and the seat member 31 when the valve member 40 is separated from the seat member 31. is set smaller than the minimum value DL1 of the distance from Here, the minimum value DL1 is the end of the surface of the guide portion 43 on the side of the seat member 31 opposite to the valve body 41 when the other surface 402 of the valve member 40 is in contact with the stopper convex portion 353. It is equal to the distance from the surface of the sheet member 31 on the pressure chamber 200 side (see FIG. 59). Incidentally, in the present embodiment, the amount of bending QC3 and the amount of bending QC4 are the same.

In the present embodiment, when the plunger 11 moves toward the pressurizing chamber 200 and the volume of the pressurizing chamber 200 decreases, when the coil 60 of the electromagnetic drive unit 500 is energized, the needle 53 moves away from the pressurizing chamber 200. It moves to the opposite side, and the valve member 40 moves in the valve closing direction. At this time, the pressure of the fuel in the pressurizing chamber 200 acts on the surface of the guide portion 43 on the pressurizing chamber 200 side. 59, the guide portion 43 of the valve member 40 is deformed toward the pressure chamber 200, and the surface of the valve main body 41 on the side of the seat member 31 faces the pressure chamber 200 of the seat member 31. It seals against the surface, ie, the plurality of valve seats 310 . Thereby, the valve member 40 is closed.

As described above, in the present embodiment, the surface of the guide portion 43 of the valve member 40 on the side of the seat member 31 is formed so as to curve from the valve body 41 toward the seat member 31 side. Therefore, if the minimum value DL1 is the lift amount QL1 of the valve member 40, the apparent lift amount of the valve member 40 in the valve body 41 of the valve member 40 is larger than the lift amount QL1 by the bending amount QC3. As a result, the amount of fuel sucked into the pressurization chamber 200, the amount of fuel returned from the pressurization chamber 200 to the fuel chamber 260 side, and the self-closing limit of the valve member 40 can be improved.

(12th embodiment)
<A-12> FIGS. 60 and 61 show part of the high-pressure pump according to the twelfth embodiment. The twelfth embodiment differs from the first embodiment in the configuration of the cylinder 23 .

In this embodiment, when viewed from the axial direction of the suction hole 232 , the outer peripheral recessed portion 235 extends from a position slightly closer to the bottom side of the cylinder 23 than the upper end of the tapered surface 234 in the axial direction of the cylinder 23 to the lower end of the tapered surface 234 . is formed in a range up to a position away from the bottom of the cylinder 23 by a predetermined distance. That is, the outer peripheral recessed portion 235 of the present embodiment is formed so as to include the entire tapered surface 234 inside when viewed from the axial direction of the suction hole 232 , and is larger than the outer peripheral recessed portion 235 of the first embodiment in the axial direction of the cylinder 23 . big. As in the first embodiment, the outer peripheral recessed portion 235 is at least partly formed in a range that overlaps with the sliding surface 230a in the axially lower portion of the cylinder 23 when viewed from the axial direction of the suction hole 232. (See FIG. 60).

When viewed from the axial direction of the discharge hole 233 , the outer peripheral concave portion 236 extends from a position slightly closer to the bottom of the cylinder 23 than the upper end of the discharge hole 233 to the lower end of the discharge hole 233 in the axial direction of the cylinder 23 . It is formed in a range up to a position a predetermined distance away from the bottom. That is, the outer peripheral recessed portion 236 of the present embodiment is formed so as to include the entire discharge hole 233 inside when viewed from the axial direction of the discharge hole 233, and is larger than the outer peripheral recessed portion 236 of the first embodiment in the axial direction of the cylinder 23. big. As in the first embodiment, the outer peripheral recessed portion 236 is formed at least partially in a range that overlaps with the sliding surface 230a in the axially lower portion of the cylinder 23 when viewed from the axial direction of the discharge hole 233. (See Figure 61).

As in the first embodiment, the outer peripheral recesses 235 and 236 are fitted to the upper housing 21 at the axially upper portion of the cylinder 23 when viewed from the axial direction of the suction hole 232 or the discharge hole 233 . It is formed in such a range that the shrink-fit portion remains (see FIGS. 60 and 61). However, the size of the fitting portion with the upper housing 21 is smaller than that of the first embodiment.

In this embodiment, as in the first embodiment, the outer peripheral wall of the cylinder 23 is formed with the outer peripheral recess 235 and the outer peripheral recess 236, so that the cylindrical member 51 of the electromagnetic drive unit 500 is inserted into the suction hole 212 of the upper housing 21. Even if the inner peripheral wall of the hole portion 211 of the upper housing 21 is deformed radially inward when the discharge joint 70 of the discharge passage portion 700 is screwed to the discharge hole portion 214 of the upper housing 21, It is possible to suppress the surface pressure caused by the deformation acting on the outer peripheral wall of the cylinder 23 . Therefore, the clearance between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be kept constant, and uneven wear and seizure between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be suppressed.

Note that the outer peripheral recessed portion 235 and the outer peripheral recessed portion 236 of the present embodiment are larger than the outer peripheral recessed portion 235 and the outer peripheral recessed portion 236 of the first embodiment. The effect of suppressing wear and seizure is higher.

In this embodiment, the outer peripheral recessed portion 235 and the outer peripheral recessed portion 236 are formed to include the upper and lower portions of the portions corresponding to the valve seat 310 and the discharge valve seat 74 . Therefore, deformation of the valve seat 310 and the discharge valve seat 74 is prevented compared to the case where the outer periphery recess 235 and the outer periphery recess 236 are formed to include only one of the upper portion and the lower portion of the portion corresponding to the valve seat 310 and the discharge valve seat 74. can be equalized. Thereby, the difference in deformation between the upper and lower sides of the valve seat 310 and the discharge valve seat 74 can be suppressed, and uneven wear of the valve member 40 and the discharge valve 75 can be suppressed.

(13th embodiment)
<A-01> FIG. 62 shows part of a high-pressure pump according to the thirteenth embodiment. The thirteenth embodiment differs from the first embodiment in the configuration of the stopper 35 .

In this embodiment, the inner diameter of the stopper concave portion 351 is smaller than the outer diameter of the stopper large-diameter portion 37 and the outer diameter of the stopper small-diameter portion 36 . Thereby, the thickness of the stopper 35 on the pressurizing chamber 200 side can be ensured with respect to the bottom surface of the stopper concave portion 351 .

(14th embodiment)
<A-02> FIG. 63 shows part of the high-pressure pump according to the fourteenth embodiment. The fourteenth embodiment differs from the first embodiment in the configuration of the stopper 35 .

In this embodiment, six communicating holes 38 are formed at equal intervals in the circumferential direction of the stopper 35 . Therefore, variations in fuel flow due to the relative angular difference between the stopper 35 and the valve member 40 and the seat member 31 during assembly and operation are reduced. As a result, the flow of fuel into the communication hole 44 of the valve member 40 is stabilized, and the behavior of the valve member 40 is stabilized.

(15th embodiment)
<B-2> FIG. 64 shows part of the high-pressure pump according to the fifteenth embodiment. The fifteenth embodiment differs from the first embodiment in the configuration of the coil 60 .

In this embodiment, the coil 60 includes one virtual outer cylindrical surface 600 passing through the outer peripheral surface of the winding portion 62 and a virtual inner cylindrical surface 600 passing through the inner peripheral surface of the winding portion 62 and having different diameters. It has an inner cylindrical surface 601 , an inner cylindrical surface 602 and an inner cylindrical surface 603 .

The outer cylindrical surface 600 is formed in a substantially cylindrical shape. The inner cylindrical surface 601 is formed in a substantially cylindrical shape and is located inside the portion of the outer cylindrical surface 600 opposite to the pressurizing chamber 200 . The inner cylindrical surface 602 is formed in a substantially cylindrical shape and is positioned on the pressure chamber 200 side with respect to the inner cylindrical surface 601 inside the outer cylindrical surface 600 . The inner cylindrical surface 603 is formed in a substantially cylindrical shape and is positioned on the pressure chamber 200 side with respect to the inner cylindrical surface 602 inside the portion of the outer cylindrical surface 600 on the pressure chamber 200 side.

The diameter of inner cylindrical surface 602 is larger than the diameter of inner cylindrical surface 601 . Also, the diameter of the inner cylindrical surface 603 is larger than the diameter of the inner cylindrical surface 602 . Inner cylindrical surface 601 , inner cylindrical surface 602 and inner cylindrical surface 603 are located on the outer peripheral wall of spool 61 . In other words, the spool 61 has different outer diameters at a portion on the pressurizing chamber 200 side in the axial direction and a portion on the opposite side from the pressurizing chamber 200 .

The coil 60 has a virtual connecting surface 605 connecting the inner cylindrical surface 601 and the inner cylindrical surface 602, and a virtual connecting surface 606 connecting the inner cylindrical surface 602 and the inner cylindrical surface 603. have. The connecting surface 605 and the connecting surface 606 are positioned on the outer peripheral wall of the spool 61 and formed so that at least a portion thereof is perpendicular to the axis of the spool 61 . The winding 620 is wound on the outer peripheral wall of the spool 61, that is, on the radially outer side of the inner cylindrical surface 601, the inner cylindrical surface 602, the inner cylindrical surface 603, the connecting surface 605, and the connecting surface 606. A winding portion 62 is formed.

In this embodiment, when the coil 60 is not energized, the end surface 551 of the movable core 55 opposite to the pressurizing chamber 200, that is, the fixed core 57 side is the inner cylindrical surface 601 having the smallest diameter. and the axial center Co1 of the outer cylindrical surface 600. Further, the end surface 552 of the movable core 55 on the pressure chamber 200 side is located on the fixed core 57 side with respect to the end surface 621 of the winding portion 62 on the pressure chamber 200 side.

In addition, in the present embodiment, the end portion of the first tubular portion 511 of the tubular member 51 on the second tubular portion 512 side is positioned inside the inner tubular surface 603 . The second cylindrical portion 512 is located inside the connecting surface 606 . The third tubular portion 513 is positioned inside the inner tubular surface 602 .

Also in the fifteenth embodiment, the same effect as in the first embodiment can be obtained. In addition, in the fifteenth embodiment, the number of windings of the wire 620 can be increased without increasing the diameter of the outer cylindrical surface 600 as compared with the first embodiment.

(16th embodiment)
<B-3> FIG. 65 shows part of the high-pressure pump according to the sixteenth embodiment. The sixteenth embodiment differs from the first embodiment in the configuration of the coil 60 .

In this embodiment, the coil 60 does not have the connecting surface 605 shown in the first embodiment. The end portion of the inner cylindrical surface 601 on the pressurizing chamber 200 side and the end portion of the inner cylindrical surface 602 on the side opposite to the pressurizing chamber 200 are connected.

All portions of the inner cylindrical surface 602 are formed in a tapered shape so as to approach the axis of the spool 61 from the side of the pressurizing chamber 200 toward the side opposite to the pressurizing chamber 200 . That is, the diameter of the inner cylindrical surface 602 increases toward the pressure chamber 200 side.

Inner cylindrical surface 601 and inner cylindrical surface 602 are located on the outer peripheral wall of spool 61 .
The winding 620 is wound on the outer peripheral wall of the spool 61 , that is, on the radially outer side of the inner cylindrical surface 601 and the inner cylindrical surface 602 to form a cylindrical winding portion 62 .

In this embodiment, when the coil 60 is not energized, the end surface 551 of the movable core 55 opposite to the pressurizing chamber 200, that is, the fixed core 57 side is the inner cylindrical surface 601 having the smallest diameter. and the axial center Co1 of the outer cylindrical surface 600. Further, the end surface 552 of the movable core 55 on the pressure chamber 200 side is located on the fixed core 57 side with respect to the end surface 621 of the winding portion 62 on the pressure chamber 200 side.

Further, in the present embodiment, the portion of the second tubular portion 512 of the tubular member 51 on the third tubular portion 513 side is located inside the inner tubular surface 602 . The third tubular portion 513 is located inside the connecting portion between the inner tubular surface 601 and the inner tubular surface 602 . The outer peripheral wall of the third cylindrical portion 513 side of the second cylindrical portion 512 is tapered so as to approach the axis of the second cylindrical portion 512 as it goes from the pressure chamber 200 side to the side opposite to the pressure chamber 200. is formed in

Also in the sixteenth embodiment, the same effect as in the first embodiment can be obtained. In addition, in the sixteenth embodiment, the number of windings of the wire 620 can be increased without increasing the diameter of the outer cylindrical surface 600 as compared with the first embodiment and the fifteenth embodiment.

(17th embodiment)
<B-4> FIG. 66 shows part of the high-pressure pump according to the seventeenth embodiment. The seventeenth embodiment differs from the first embodiment in the configuration of the fixed core 57 and the like.

In this embodiment, the stationary core 57 has a stationary core hole 575 . The fixed core hole portion 575 is formed in a substantially cylindrical shape so as to extend from the center of the end face 571 of the fixed core 57 on the pressurizing chamber 200 side to the side opposite to the pressurizing chamber 200 . The stationary core hole portion 575 is formed substantially coaxially with the stationary core small diameter portion 573 and the stationary core large diameter portion 574 .

The needle 53 does not have the locking portion 532 shown in the first embodiment. The spring 54 is provided in the fixed core hole portion 575 . The spring 54 has one end in contact with the bottom surface of the fixed core hole portion 575 and the other end in contact with the end surface of the needle body 531 on the side opposite to the pressure chamber 200 . That is, the bottom surface of the fixed core hole portion 575 locks one end of the spring 54 . A spring 54 biases the needle 53 toward the pressure chamber 200 . In this embodiment, the needle 53 does not need the locking portion 532 for locking the end of the spring 54, so the weight of the needle 53 can be reduced. Thereby, NV can be reduced.

(18th embodiment)
<B-5> FIG. 67 shows part of the high-pressure pump according to the eighteenth embodiment. The eighteenth embodiment differs from the seventeenth embodiment in the configuration near the spring 54 .

This embodiment further includes a locking member 576 . The locking member 576 is made of a material having a hardness higher than that of the fixed core 57 and has a substantially cylindrical shape. The hardness of the locking member 576 is set in the range of HRc56-64, for example.

The outer diameter of locking member 576 is slightly smaller than the inner diameter of fixed core hole portion 575 . The locking member 576 is provided substantially coaxially with the fixed core hole portion 575 so that one end surface thereof contacts the bottom surface of the fixed core hole portion 575 . One end of the spring 54 is in contact with the other end surface of the locking member 576 . That is, the locking member 576 locks one end of the spring 54 .

Due to the reciprocating movement of the movable core 55 and the needle 53 , pressure fluctuations occur on the side of the fixed core hole portion 575 facing the pressure chamber 200 . This pressure fluctuation is transmitted to the end of the fixed core hole portion 575 opposite to the pressurizing chamber 200 with a delay. Therefore, cavitation is likely to occur at the end portion of the fixed core hole portion 575 opposite to the pressure chamber 200 .

In this embodiment, a locking member 576 is provided on the bottom surface of the fixed core hole portion 575 . Therefore, even if cavitation occurs at the end of the fixed core hole portion 575 opposite to the pressurizing chamber 200, the locking member 576 erodes the bottom surface of the fixed core hole portion 575 and its periphery by cavitation erosion. can be suppressed.

(19th embodiment)
<C-01> FIG. 68 shows part of the high-pressure pump according to the nineteenth embodiment. The nineteenth embodiment differs from the first embodiment in the configuration of the discharge joint 70 .

In this embodiment, the channel area of the lateral hole portion 702 is smaller than the channel area of the relief hole 87 when the relief valve 91 is fully opened. That is, in the present embodiment, the passage area of the lateral hole portion 702 on the downstream side of the lateral relief hole 852 that functions as a variable orifice is smaller than the passage area of the relief hole 87 on the upstream side of the lateral relief hole 852 . Therefore, when the pressure of the fuel on the high-pressure fuel pipe 8 side reaches an abnormal value, the fuel on the high-pressure fuel pipe 8 side can be prevented from flowing too much to the fuel chamber 260 side. As a result, it is possible to suppress the occurrence of a pressure spike on the low-pressure fuel chamber 260 side. Moreover, this can suppress the behavior of the relief valve 91 from becoming unstable.

In addition to reducing the inner diameter of the lateral hole portion 702 as described above, as means for reducing the flow passage area on the downstream side of the lateral relief hole 852 that functions as a variable orifice, the depth of the relief outer peripheral concave portion 851 may be decreased. Alternatively, an orifice member may be provided in the relief lateral hole 852, or the like.

(Twentieth embodiment)
<D-1> FIG. 69 shows a high-pressure pump according to the twentieth embodiment. The twentieth embodiment differs from the first embodiment in the arrangement of the supply passage portion 29, the electromagnetic driving portion 500, the discharge passage portion 700, and the like.

In this embodiment, the axes of the suction hole portions 212 and 213 are orthogonal to the axes of the discharge hole portions 214 and 215 (see FIG. 72). Also, the axis of the suction hole 232 and the axis of the discharge hole 233 are perpendicular to the axis Ax1 of the cylindrical inner peripheral wall 230 of the cylinder hole portion 231 . Also, the axis of the suction hole 232 and the axis of the discharge hole 233 are perpendicular to each other.

The cover hole portion 265, the cover hole portion 266, and the cover hole portion 267 are each formed in a substantially cylindrical shape so as to connect the inner peripheral wall of the cover cylindrical portion 261 and the outer peripheral wall, that is, the flat portion 281 of the cover outer peripheral wall 280. .

Here, the cover hole portion 265 is formed in the plane portion 281 between the plane portion 281 in which the cover hole portion 266 is formed and the plane portion 281 in which the cover hole portion 267 is formed. That is, the cover hole portion 266, the cover hole portion 265, and the cover hole portion 267 are formed in the cover 26 so as to be arranged in this order in the circumferential direction of the cover outer peripheral wall 280 (see FIG. 72).

In this embodiment, the supply passage portion 29 is provided so that one end thereof is connected to the outer wall around the cover hole portion 265 of the cover cylindrical portion 261 , that is, the flat portion 281 of the cover outer peripheral wall 280 . The supply passage portion 29 is provided such that the inner space communicates with the fuel chamber 260 via the cover hole portion 265 . Here, the supply passage portion 29 and the planar portion 281 of the cover outer peripheral wall 280 are welded over the entire circumferential region of the supply passage portion 29 . A supply fuel pipe 7 is connected to the other end of the supply passage portion 29 . As a result, the fuel discharged from the fuel pump flows into the fuel chamber 260 via the fuel supply pipe 7 and the supply passage portion 29 .

Next, the cylinder 23 of this embodiment will be described more specifically.
As shown in FIGS. 70 and 71, the cylinder 23 has a tapered surface 234 and an outer peripheral recess 235. As shown in FIGS.

The tapered surface 234 is formed at the end of the suction hole 232 opposite to the pressure chamber 200 . The tapered surface 234 is formed in a tapered shape so as to separate from the axis of the suction hole 232 as it goes from the pressurizing chamber 200 side toward the side opposite to the pressurizing chamber 200 .

The outer peripheral recessed portion 235 is formed so as to be recessed to a predetermined depth from the outer peripheral wall of the cylinder 23 radially inward. The outer peripheral recessed portion 235 is formed in a range that includes all of the suction hole 232, that is, the tapered surface 234 and the discharge hole 233 in the circumferential direction of the cylinder 23 (see FIGS. 70 and 71). In addition, when viewed from the axial direction of the suction hole 232 , the outer peripheral recessed portion 235 extends from a position slightly on the bottom side of the cylinder 23 with respect to the axis of the suction hole 232 to the lower end of the tapered surface 234 in the axial direction of the cylinder 23 . It is formed in a range up to a position a predetermined distance away from the bottom of 23 (see FIG. 70). In addition, when viewed from the axial direction of the discharge hole 233 , the outer peripheral concave portion 235 extends from a position slightly on the bottom side of the cylinder 23 with respect to the axis of the discharge hole 233 to the lower end of the discharge hole 233 in the axial direction of the cylinder 23 . is formed in a range up to a position a predetermined distance away from the bottom of the (see FIG. 71). At least a part of the outer peripheral concave portion 235 is formed in a range that overlaps with the sliding surface 230a in the axially lower portion of the cylinder 23 when viewed from the axial direction of the suction hole 232 or the discharge hole 233 (Fig. 70, 71).

In addition, when viewed from the axial direction of the suction hole 232 or the discharge hole 233, the outer peripheral recessed portion 235 is formed in a range that leaves a fitting portion with the upper housing 21, i. formed (see FIGS. 70 and 71).

As described above, when the cylindrical member 51 of the electromagnetic drive unit 500 is screwed to the suction hole portion 212 of the upper housing 21, the stepped surface between the suction hole portions 213 and 212 has the stopper small diameter portion 36 and the stopper small diameter portion 36. An axial force directed toward the pressurizing chamber 200 side acts from the stepped surface between the large-diameter portion 37 of the stopper. Therefore, the inner peripheral wall of the hole portion 211 of the upper housing 21 may slightly deform radially inward around the suction hole portion 213 . However, in this embodiment, since the outer peripheral recessed portion 235 is formed in the outer peripheral wall of the cylinder 23 at a position corresponding to the suction hole portion 213, even if the inner peripheral wall of the hole portion 211 of the upper housing 21 is deformed radially inward, Also, it is possible to suppress the surface pressure caused by the deformation acting on the outer peripheral wall of the cylinder 23 . As a result, it is possible to suppress radially inward deformation of the cylindrical inner peripheral wall 230 of the cylinder hole portion 231 . Therefore, the clearance between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be kept constant, and uneven wear and seizure between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be suppressed.

Further, when the discharge joint 70 of the discharge passage portion 700 is screwed to the discharge hole portion 214 of the upper housing 21 , pressure is applied from the inner projection 722 and the outer projection 723 around the discharge hole portion 215 on the bottom surface of the discharge hole portion 214 . An axial force directed toward the chamber 200 acts. Therefore, the inner peripheral wall of the hole portion 211 of the upper housing 21 may slightly deform radially inward around the discharge hole portion 215 . However, in this embodiment, since the outer peripheral recessed portion 235 is formed in the outer peripheral wall of the cylinder 23 at a position corresponding to the discharge hole portion 215, even if the inner peripheral wall of the hole portion 211 of the upper housing 21 is deformed radially inward, Also, it is possible to suppress the surface pressure caused by the deformation acting on the outer peripheral wall of the cylinder 23 . As a result, it is possible to suppress radially inward deformation of the cylindrical inner peripheral wall 230 of the cylinder hole portion 231 . Therefore, the clearance between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be kept constant, and uneven wear and seizure between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be suppressed.

Further, the axial force described above causes the inner peripheral wall of the hole 211 of the upper housing 21 to deform radially inward, thereby increasing the surface pressure at the boundary of the outer peripheral recessed portion 235 of the cylinder 23 . It becomes easy to cope with high pressure.

Next, the arrangement and the like of the electromagnetic driving portion 500 and the discharge passage portion 700 will be described.

As shown in FIG. 72 , two bolt holes 250 are formed at equal intervals in the circumferential direction on the radially outer side of the housing outer peripheral wall 270 when viewed from the direction of the axis Ax1 of the cylindrical inner peripheral wall 230 . That is, the angle formed by the two straight lines connecting the axis Ax1 of the cylindrical inner peripheral wall 230 and the respective axes of the two bolt holes 250 is 180 degrees. Further, the bolt hole 250 is formed such that its axis is substantially parallel to the axis Ax1 of the cylindrical inner peripheral wall 230 of the cylinder 23 .

The electromagnetic drive portion 500 is provided so as to protrude radially outward from the housing outer peripheral wall 270 . The discharge passage portion 700 is provided so as to protrude radially outward from the housing outer peripheral wall 270 . The supply passage portion 29 is provided so as to protrude from the cover 26 toward the outside in the radial direction of the housing outer peripheral wall 270 .

When the high-pressure pump 10 is divided into two regions, a first region T1 and a second region T2, by a virtual plane VS0 including the axes of two adjacent bolt holes 250 and the axis Ax1 of the cylindrical inner peripheral wall 230, the electromagnetic drive unit 500, the supply passage portion 29, and the discharge passage portion 700 are all located in the first region T1. Here, the virtual surface VS0 is formed in a planar shape.

In this embodiment, the axis of the supply passage portion 29 is orthogonal to the virtual plane VS0. The angle between the central axis Axc1 of the electromagnetic drive portion 500 and the central axis Axc2 of the discharge passage portion 700 is approximately 90 degrees. Further, the angle between the central axis Axc1 of the electromagnetic driving portion 500 and the central axis Axc2 of the discharge passage portion 700 and the virtual plane VS0 is approximately 45 degrees.

In addition, the supply passage portion 29 is within 180 degrees from the electromagnetic drive portion 500 to the discharge passage portion 700 side, or within 180 degrees from the discharge passage portion 700 to the electromagnetic drive portion 500 side in the circumferential direction of the housing outer peripheral wall 270. located in

Further, three flat portions 271 of the housing outer peripheral wall 270 are formed in the first region T1. That is, three plane portions 271 are formed in the first region T1, and the electromagnetic driving portion 500, the discharge passage portion 700, and the supply passage portion 29 are arranged so as to correspond to each of them. Note that three flat portions 271 are formed in the second region T2.

In the present embodiment, it can also be said that three plane portions 271 are formed in the first region T1 so as not to straddle the plane VS1 that is parallel to the virtual plane VS0 and in contact with the two bolt holes 250 . The electromagnetic driving portion 500, the discharge passage portion 700, and the supply passage portion 29 are arranged so as to correspond to the three plane portions 271 (see FIG. 72).

In this embodiment, it can also be said that three plane portions 271 are formed between two plane portions 271 facing each of the two bolt holes 250 . The electromagnetic driving portion 500, the discharge passage portion 700, and the supply passage portion 29 are arranged so as to correspond to the three plane portions 271 (see FIG. 72).

As described above, in this embodiment, the electromagnetic driving portion 500, the discharge passage portion 700, and the supply passage portion 29 are collectively arranged in the first region T1, which is a specific portion of the upper housing 21 in the circumferential direction. Here, when viewed from the direction of the axis Ax1 of the cylindrical inner peripheral wall 230, the bolt hole 250, the electromagnetic drive portion 500 and the discharge passage portion 700 do not overlap.

FIG. 73 shows a high-pressure pump 10 according to a comparative embodiment. The high-pressure pump 10 according to the comparative embodiment differs from the twentieth embodiment in the arrangement of the electromagnetic drive section 500 . In the high-pressure pump 10 according to the comparative embodiment, the electromagnetic drive portion 500 is provided in the upper housing 21 so as to be coaxial with the discharge passage portion 700 . That is, the central axis Axc1 of the electromagnetic drive portion 500 and the central axis Axc2 of the discharge passage portion 700 are aligned. Therefore, the discharge passage portion 700 is positioned in the first region T1, and the electromagnetic driving portion 500 is positioned in the second region T2.

In the high-pressure pump 10 according to the comparative embodiment, the electromagnetic drive portion 500, the discharge passage portion 700, and the supply passage portion 29 are not collectively arranged at a specific portion in the circumferential direction of the upper housing 21. As shown in FIG. Therefore, when viewed from the direction of the axis Ax1 of the cylindrical inner peripheral wall 230, the circle C1 enclosing the entire high-pressure pump 10 according to the comparative embodiment is larger than the circle C0 enclosing the entire high-pressure pump 10 according to the twentieth embodiment. 72, 73). Here, assuming that the diameter of the circle C0 is 1, the diameter of the circle C1 is approximately 1.1. Therefore, it can be seen that the high-pressure pump 10 according to the twentieth embodiment is smaller than the high-pressure pump 10 of the comparative embodiment.

Next, attachment of the high-pressure pump 10 to the engine 1 will be described.

In this embodiment, the high-pressure pump 10 is attached to the engine 1 such that the holder support portion 24 is inserted into the attachment hole portion 3 of the engine head 2 (see FIG. 69). The high-pressure pump 10 is fixed to the engine 1 by fixing the fixed portion 25 to the engine head 2 with bolts 100 . Here, the high-pressure pump 10 is attached to the engine 1 in such a posture that the axis Ax1 of the cylindrical inner peripheral wall 230 of the cylinder 23 is along the vertical direction.

The high-pressure pump 10 is attached to the engine 1 by, for example, the following steps. First, the lifter 5 is attached to the end of the small diameter portion 112 of the plunger 11 opposite to the large diameter portion 111 . Subsequently, the holder support portion 24 of the high-pressure pump 10 is inserted into the mounting hole portion 3 of the engine head 2 together with the lifter 5 . Here, the position of the bolt hole 250 of the fixed portion 25 and the position of the fixing hole portion 120 of the engine head 2 are made to correspond.

Subsequently, the bolt 100 is inserted through the bolt hole 250 and screwed into the fixing hole portion 120 . At this time, a tool (not shown) corresponding to the head portion 102 of the bolt 100 is used to screw the bolt 100 and the fixing hole portion 120 together. As a result, the fixed portion 25 is fixed to the engine head 2 . Thus, the attachment of the high-pressure pump 10 to the engine 1 is completed.

In the present embodiment, the electromagnetic driving portion 500, the discharge passage portion 700, and the supply passage portion 29 are collectively arranged in the first region T1, which is a specific portion of the upper housing 21 in the circumferential direction. When the fixing portion 25 is fixed to the engine head 2 of the engine 1 and the high-pressure pump 10 is attached to the engine 1, the bolt 100 and a tool for screwing the bolt 100 into the fixing hole portion 120 are attached to the electromagnetic drive portion 500, the discharge Interference with the passage portion 700 and the supply passage portion 29 can be suppressed.

As described above, (D1) the present embodiment is a high-pressure pump 10 attached to an engine 1 to pressurize fuel and supply it to the engine 1. The cylinder 23 and the plunger 11 as pressurizing chamber forming portions are provided. It has an upper housing 21 as a housing, a valve member 40 , an electromagnetic drive portion 500 , a discharge passage portion 700 and a fixed portion 25 . The cylinder 23 has a cylindrical inner peripheral wall 230 that forms a pressure chamber 200 in which fuel is pressurized.

The plunger 11 is provided inside the cylindrical inner peripheral wall 230 so that one end is located in the pressurization chamber 200, and can pressurize the fuel in the pressurization chamber 200 by moving in the axial direction. The upper housing 21 has a tubular outer peripheral wall 270 of which at least a portion is located radially outside the pressurizing chamber 200 . The valve member 40 can allow or regulate the flow of fuel sucked into the pressurization chamber 200 by opening or closing the valve.

The electromagnetic drive unit 500 is provided so as to protrude radially outward from the outer peripheral wall 270 of the housing, and can control opening and closing of the valve member 40 . The discharge passage portion 700 is provided so as to protrude radially outward from the outer peripheral wall 270 of the housing, and the fuel pressurized in the pressurization chamber 200 and discharged to the engine 1 flows. The fixed portion 25 is provided to be connected to the upper housing 21 , has a bolt hole 250 , and is fixed to the engine 1 by a bolt 100 provided corresponding to the bolt hole 250 .

Two bolt holes 250 are formed radially outward of the housing outer peripheral wall 270 when viewed from the direction of the axis Ax1 of the cylindrical inner peripheral wall 230 . When the high-pressure pump 10 is divided into two regions, a first region T1 and a second region T2, by a virtual plane VS0 including the axes of two adjacent bolt holes 250 and the axis Ax1 of the cylindrical inner peripheral wall 230, the electromagnetic drive unit 500 and discharge passage portion 700 are both located in first region T1. Therefore, the electromagnetic driving portion 500 and the discharge passage portion 700 can be collectively arranged at a specific portion in the circumferential direction of the housing outer peripheral wall 270 . As a result, the degree of freedom of the mounting position of the high-pressure pump 10 to the engine 1 can be improved.

A harness 6 as wiring is connected to the electromagnetic drive portion 500 of the high-pressure pump 10 , and a high-pressure fuel pipe 8 as a steel pipe is connected to the discharge passage portion 700 . In the present embodiment, the electromagnetic driving portion 500 and the discharge passage portion 700 can be collectively arranged at a specific portion in the circumferential direction of the housing outer peripheral wall 270. It is easy to attach the high-pressure pump 10 to the engine 1 so as not to contact the fuel pipe 8 . Therefore, the mountability of the high-pressure pump 10 can be improved.

(D2) In the present embodiment, two bolt holes 250 are formed at equal intervals in the circumferential direction of the housing outer peripheral wall 270 . The angle formed by the two straight lines connecting the axis Ax1 of the cylindrical inner peripheral wall 230 and the respective axes of the two bolt holes 250 is 180 degrees. Therefore, the high-pressure pump 10 can be equally divided into the first region T1 and the second region T2, and the electromagnetic drive section 500 and the discharge passage section 700 can be arranged in the first region T1. In other words, the electromagnetic driving portion 500 and the discharge passage portion 700 can be collectively arranged on one side of the area evenly dividing the high-pressure pump 10 into two. Therefore, the mountability of the high-pressure pump 10 can be improved.

Further, (D3) in the present embodiment, the housing outer peripheral wall 270 has a plurality of planar flat portions 271 . Three plane portions 271 are formed in the first region T1. Therefore, the suction hole portion 212 and the discharge hole portion 214, which are holes for providing the electromagnetic drive portion 500 and the discharge passage portion 700, can be easily formed in the flat plane portion 271, respectively.

Further, (D4) In the present embodiment, the central axis Axc1 of the electromagnetic drive portion 500 and the central axis Axc2 of the discharge passage portion 700 are located on the same plane. Therefore, it is possible to suppress the increase in size of the high-pressure pump 10 in the direction of the axis Ax1 of the cylindrical inner peripheral wall 230 of the cylinder 23 .

In addition, (D5) this embodiment further includes a supply passage portion 29 . The supply passage portion 29 is provided so as to protrude radially outward of the housing outer peripheral wall 270 . Fuel sucked into the pressurization chamber 200 flows through the supply passage portion 29 . The supply passage portion 29 is positioned within 180 degrees from the electromagnetic drive portion 500 to the discharge passage portion 700 side, or within 180 degrees from the discharge passage portion 700 to the electromagnetic drive portion 500 side in the circumferential direction of the housing outer peripheral wall 270. is doing. Therefore, in the high-pressure pump 10 including the supply passage portion 29 in addition to the electromagnetic drive portion 500 and the discharge passage portion 700, the electromagnetic drive portion 500, the discharge passage portion 700, and the supply passage portion 29 are arranged in a specific circumferential direction of the housing outer peripheral wall 270. They can be collectively arranged on one side of the high-pressure pump 10 .

Further, (D6) In the present embodiment, three plane portions 271 are formed in the first region T1 so as not to straddle the plane VS1 that is parallel to the virtual plane VS0 and in contact with the two bolt holes 250 . Therefore, the electromagnetic drive portion 500, the discharge passage portion 700, and the supply passage portion 29 can be easily concentrated in the first region T1, which is a specific portion in the circumferential direction of the housing outer peripheral wall 270, that is, on one side of the high-pressure pump 10. can do.

(D7) In the present embodiment, three flat portions 271 are formed between the two flat portions 271 facing the two bolt holes 250 respectively. Therefore, the electromagnetic drive portion 500 , the discharge passage portion 700 , and the supply passage portion 29 can be easily concentrated and arranged at a specific portion in the circumferential direction of the housing outer peripheral wall 270 , that is, at one side of the high-pressure pump 10 .

(21st embodiment)
<D-2> FIG. 74 shows a high-pressure pump according to the twenty-first embodiment. The twenty-first embodiment differs from the twentieth embodiment in the configurations of the upper housing 21 and the cover 26, and the like.

In this embodiment, the upper housing 21 is formed such that the outer peripheral wall 270 of the housing has a nine-sided cylindrical shape. Further, the cover 26 is formed so that the cover outer peripheral wall 280 corresponds to the housing outer peripheral wall 270 and has a nine-sided tubular shape.

The angle between the central axis Axc1 of the electromagnetic drive portion 500 and the central axis Axc2 of the discharge passage portion 700 is smaller than 90 degrees. Therefore, the electromagnetic driving portion 500 and the discharge passage portion 700 can be collectively arranged in a narrower range at a specific portion in the circumferential direction of the housing outer peripheral wall 270 .

Further, three flat portions 271 of the housing outer peripheral wall 270 are formed in the first region T1. That is, three plane portions 271 are formed in the first region T1, and the electromagnetic driving portion 500, the discharge passage portion 700, and the supply passage portion 29 are arranged so as to correspond to each of them. Note that four flat portions 271 are formed in the second region T2. Also in the twenty-first embodiment, the same effect as in the twentieth embodiment can be obtained.

(22nd embodiment)
<D-3> FIG. 75 shows a high-pressure pump according to the twenty-second embodiment. The twenty-second embodiment differs from the twentieth embodiment in the configurations of the upper housing 21 and the cover 26, and the like.

In this embodiment, the upper housing 21 is formed such that the outer peripheral wall 270 of the housing is decagonal. Further, the cover 26 is formed so that the outer peripheral wall 280 of the cover corresponds to the outer peripheral wall 270 of the housing and has a decagonal tubular shape.

The angle between the central axis Axc1 of the electromagnetic drive portion 500 and the central axis Axc2 of the discharge passage portion 700 is smaller than 90 degrees. Therefore, the electromagnetic driving portion 500 and the discharge passage portion 700 can be collectively arranged in a narrower range at a specific portion in the circumferential direction of the housing outer peripheral wall 270 .

Further, five flat portions 271 of the housing outer peripheral wall 270 are formed in the first region T1. That is, five flat portions 271 are formed in the first region T1, and the electromagnetic driving portion 500, the discharge passage portion 700, and the supply passage portion 29 are arranged so as to correspond to three of the flat portions 271, respectively. Five flat portions 271 are formed in the second region T2. Also in the twenty-second embodiment, the same effect as in the twentieth embodiment can be obtained.

(23rd embodiment)
<D-4> FIG. 76 shows a high-pressure pump according to the twenty-third embodiment. The twenty-third embodiment differs from the twentieth embodiment in the configurations of the upper housing 21 and the cover 26, and the like.

In this embodiment, the upper housing 21 is formed such that the housing outer peripheral wall 270 has a substantially cylindrical shape in the second region T2. The shape of the upper housing 21 in the first region T1 is the same as in the twentieth embodiment.

The cover 26 is formed so that the cover outer peripheral wall 280 corresponds to the housing outer peripheral wall 270 and has a substantially cylindrical shape in the second region T2. The shape of the cover 26 in the first region T1 is the same as in the twentieth embodiment.

The twenty-third embodiment has the same configuration as the twentieth embodiment except for the points described above. Also in the twenty-third embodiment, the same effect as in the twentieth embodiment can be obtained.

(24th embodiment)
<D-5> FIG. 77 shows a high-pressure pump according to the twenty-fourth embodiment. The twenty-fourth embodiment differs from the twentieth embodiment in the configurations of the upper housing 21 and the cover 26, and the like.

In this embodiment, the upper housing 21 is formed such that the housing outer peripheral wall 270 has a substantially cylindrical shape.

In addition, the cover 26 is formed such that the outer peripheral wall 280 of the cover 280 is substantially cylindrical except for the portions where the cover hole 265, the cover hole 266, and the cover hole 267 are formed. Note that portions of the cover outer peripheral wall 280 where the cover hole 265, the cover hole 266, and the cover hole 267 are formed are formed flat.

The twenty-fourth embodiment has the same configuration as the twentieth embodiment except for the points described above. Also in the twenty-fourth embodiment, the same effect as in the twentieth embodiment can be obtained.

(25th embodiment)
<D-6> FIG. 78 shows a high-pressure pump according to the twenty-fifth embodiment. The twenty-fifth embodiment differs from the twentieth embodiment in the configurations of the upper housing 21 and the cover 26, and the like.

In this embodiment, the upper housing 21 is formed such that the housing outer peripheral wall 270 forms part of a rectangular tube in the second region T2. The shape of the upper housing 21 in the first region T1 is the same as in the twentieth embodiment.

The cover 26 is formed so that the cover outer peripheral wall 280 corresponds to the housing outer peripheral wall 270 and forms a part of the rectangular cylinder in the second region T2. The shape of the cover 26 in the first region T1 is the same as in the twentieth embodiment.

The twenty-fifth embodiment has the same configuration as the twentieth embodiment except for the points described above. Also in the twenty-fifth embodiment, the same effect as in the twentieth embodiment can be obtained.

(26th embodiment)
<D-7> FIG. 79 shows a high-pressure pump according to the twenty-sixth embodiment. The twenty-sixth embodiment differs from the twentieth embodiment in the positional relationship between the electromagnetic driving portion 500 and the discharge passage portion 700 and the bolt hole 250 .

In the present embodiment, as compared with the twentieth embodiment, the upper housing 21 and the cover 26 provided with the electromagnetic driving portion 500, the discharge passage portion 700, and the supply passage portion 29 are positioned relative to the fixed portion 25. It is arranged to rotate about the axis Ax1 of the shaped inner peripheral wall 230 by a predetermined angle.

Here, the distance between the electromagnetic driving part 500 and the axis of the bolt hole 250 is smaller than the distance between the discharge passage part 700 and the axis of the bolt hole 250 . However, when viewed from the direction of axis Ax1 of cylindrical inner peripheral wall 230, bolt hole 250 and bolt 100 do not overlap with electromagnetic drive portion 500. As shown in FIG. Therefore, when high-pressure pump 10 is attached to engine 1 , bolt 100 and a tool for screwing bolt 100 into fixing hole 120 can be prevented from interfering with electromagnetic drive unit 500 .

The twenty-sixth embodiment has the same configuration as the twentieth embodiment except for the points described above. Also in the twenty-sixth embodiment, the same effect as in the twentieth embodiment can be obtained.

(27th embodiment)
<D-8> FIG. 80 shows a high-pressure pump according to the twenty-seventh embodiment. The twenty-seventh embodiment differs from the twentieth embodiment in the positional relationship between the electromagnetic driving portion 500 and the discharge passage portion 700 and the bolt hole 250 .

In the present embodiment, as compared with the twentieth embodiment, the upper housing 21 and the cover 26 provided with the electromagnetic driving portion 500, the discharge passage portion 700, and the supply passage portion 29 are positioned relative to the fixed portion 25. It is arranged to rotate about the axis Ax1 of the shaped inner peripheral wall 230 by a predetermined angle.

Here, the distance between the discharge passage part 700 and the axis of the bolt hole 250 is smaller than the distance between the electromagnetic driving part 500 and the axis of the bolt hole 250 . However, when viewed from the axis Ax1 direction of cylindrical inner peripheral wall 230 , bolt hole 250 and bolt 100 do not overlap discharge passage portion 700 . Therefore, when high-pressure pump 10 is attached to engine 1 , bolt 100 and a tool for screwing bolt 100 into fixing hole 120 can be prevented from interfering with discharge passage 700 .

The twenty-seventh embodiment has the same configuration as the twentieth embodiment except for the points described above. Also in the twenty-seventh embodiment, the same effect as in the twentieth embodiment can be obtained.

(28th embodiment)
<D-9> A high-pressure pump according to the twenty-eighth embodiment is shown in FIGS. The twenty-eighth embodiment differs from the twentieth embodiment in the positional relationship among the electromagnetic driving portion 500, the discharge passage portion 700, and the supply passage portion 29, and the like.

In this embodiment, the angle formed by the central axis Axc1 of the electromagnetic drive section 500 and the central axis Axc2 of the discharge passage section 700 is smaller than 90 degrees, for example, about 45 degrees. Therefore, the electromagnetic driving portion 500 and the discharge passage portion 700 can be collectively arranged in a narrower range at a specific portion in the circumferential direction of the housing outer peripheral wall 270 .

Further, the supply passage portion 29 is provided at the end portion of the cover outer peripheral wall 280 on the cover bottom portion 262 side. Here, the cover hole portion 265 is formed at the end portion of the cover cylinder portion 261 on the cover bottom portion 262 side (see FIG. 82).

The position of the supply passage portion 29 in the circumferential direction of the cover outer peripheral wall 280 is between the central axis Axc1 of the electromagnetic drive portion 500 and the central axis Axc2 of the discharge passage portion 700 . Also, the supply passage portion 29 and the electromagnetic driving portion 500 are provided so as not to come into contact with each other.

The twenty-eighth embodiment has the same configuration as the twentieth embodiment except for the points described above. Also in the twenty-eighth embodiment, the same effect as in the twentieth embodiment can be obtained.

(29th embodiment)
<D-10> FIG. 83 shows a high-pressure pump according to the twenty-ninth embodiment. The twenty-ninth embodiment differs from the twentieth embodiment in the arrangement of the supply passage portion 29 and the like.

In this embodiment, the cover hole portion 265 is formed in a substantially cylindrical shape so as to pass through the center of the cover bottom portion 262 in the plate thickness direction. The supply passage portion 29 is provided so that one end thereof is connected to the outer wall surrounding the cover hole portion 265 of the cover bottom portion 262 . That is, the supply passage portion 29 is provided so as to protrude upward in the vertical direction of the cylindrical inner peripheral wall 230 in the direction of the axis Ax1 from the upper housing 21 side.

The twenty-ninth embodiment has the same configuration as the twentieth embodiment except for the points described above. Also in the twenty-ninth embodiment, the same effect as in the twentieth embodiment can be obtained.

(30th embodiment)
<D-11> FIG. 84 shows a high-pressure pump according to the thirtieth embodiment. The thirtieth embodiment differs from the twentieth embodiment in the configuration near the cover bottom portion 262 .

This embodiment further includes an upper case 181 and a lower case 182 . The upper case 181 and the lower case 182 are each formed of metal, for example, in a cylindrical shape with a bottom. The inner and outer diameters of upper case 181 and lower case 182 are the same. The upper case 181 and the lower case 182 are integrally provided so that their open ends are joined to each other.

The upper case 181 and the lower case 182 form an in-case fuel chamber 180 inside. In this embodiment, the pulsation damper 15 , the upper support 171 and the lower support 172 are provided in the case-internal fuel chamber 180 . That is, the pulsation damper 15, the upper support 171, and the lower support 172 are not provided in the fuel chamber 260 inside the cover 26. FIG. Here, the upper case 181 , the lower case 182 , the pulsation damper 15 , the upper support 171 and the lower support 172 constitute the pulsation damper section 19 .

The lower case 182 is formed with a case hole 183 penetrating through the center of the bottom. Further, the cover 26 is formed with a cover hole 268 penetrating through the center of the cover bottom 262 . The pulsation damper portion 19 is provided on the opposite side of the cover bottom portion 262 to the cover cylinder portion 261 so that the case hole portion 183 and the cover hole portion 268 communicate with each other. Here, the lower case 182 and the cover bottom portion 262 are joined by welding, for example.

The in-case fuel chamber 180 communicates with the fuel chamber 260 via a case hole portion 183 and a cover hole portion 268 . Therefore, even if pressure pulsation occurs in the fuel in the fuel chamber 260 , the pressure pulsation can be reduced by the pulsation damper 15 of the in-case fuel chamber 180 .

As described above, the present embodiment further includes the pulsation damper section 19 capable of reducing pressure pulsation of the fuel in the fuel chamber 260 , that is, the fuel sucked into the pressurization chamber 200 . The pulsation damper portion 19 is provided so as to protrude upward in the vertical direction of the cylindrical inner peripheral wall 230 in the direction of the axis Ax1 from the upper housing 21 side.

The thirtieth embodiment has the same configuration as the twentieth embodiment except for the points described above. Also in the thirtieth embodiment, the same effect as in the twentieth embodiment can be obtained.

(31st Embodiment)
<D-12> A part of the high-pressure pump according to the thirty-first embodiment is shown in FIGS. The thirty-first embodiment differs from the twentieth embodiment in the configuration of the cylinder 23 .

In this embodiment, when viewed from the axial direction of the suction hole 232 , the outer peripheral recessed portion 235 extends from a position slightly closer to the bottom side of the cylinder 23 than the upper end of the tapered surface 234 in the axial direction of the cylinder 23 to the lower end of the tapered surface 234 . is formed in a range up to a position a predetermined distance away from the bottom of the cylinder 23 (see FIG. 85). In addition, when viewed from the axial direction of the discharge hole 233 , the outer peripheral recessed portion 235 extends from a position slightly on the bottom side of the cylinder 23 with respect to the upper end of the discharge hole 233 to the lower end of the discharge hole 233 in the axial direction of the cylinder 23 . is formed in a range up to a position a predetermined distance away from the bottom of the (see FIG. 86).

That is, the outer peripheral concave portion 235 of this embodiment is formed so as to include the entire tapered surface 234 inside when viewed from the axial direction of the suction hole 232, and inside when viewed from the axial direction of the discharge hole 233. 233 and is larger in the axial direction of the cylinder 23 than the outer peripheral recessed portion 235 of the twentieth embodiment. At least a part of the outer peripheral concave portion 235 is formed in a range that overlaps with the sliding surface 230a in the axially lower portion of the cylinder 23 when viewed from the axial direction of the suction hole 232 or the discharge hole 233 (Fig. 85, 86).

As in the twentieth embodiment, the outer peripheral concave portion 235 is a fitting portion with the upper housing 21, i.e., shrink-fitting, at the upper portion in the axial direction of the cylinder 23 when viewed from the axial direction of the suction hole 232 or the discharge hole 233. 85 and 86). However, the size of the fitting portion with the upper housing 21 is smaller than that of the twentieth embodiment.

In this embodiment, as in the twentieth embodiment, since the outer peripheral wall of the cylinder 23 is formed with the outer peripheral recess 235, when the cylindrical member 51 of the electromagnetic drive unit 500 is screwed to the suction hole 212 of the upper housing 21, , and when the discharge joint 70 of the discharge passage portion 700 is screwed to the discharge hole portion 214 of the upper housing 21, even if the inner peripheral wall of the hole portion 211 of the upper housing 21 is deformed radially inward, the deformation is accompanied by the deformation. It is possible to suppress the surface pressure acting on the outer peripheral wall of the cylinder 23 . Therefore, the clearance between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be kept constant, and uneven wear and seizure between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11 can be suppressed.

In addition, since the outer peripheral recessed portion 235 of the present embodiment is larger than the outer peripheral recessed portion 235 of the twentieth embodiment, the effect of "suppressing uneven wear and seizure between the cylindrical inner peripheral wall 230 and the outer peripheral wall of the plunger 11" according to the present embodiment. is higher.

(32nd embodiment)
<D-01> FIG. 87 shows part of the high-pressure pump according to the thirty-second embodiment. The thirty-second embodiment differs from the twentieth embodiment in the arrangement of the discharge passage portion 700 and the like.

In the present embodiment, the discharge hole 233, the discharge hole portions 214 and 215, and the cover hole portion 267 are arranged around the axis Ax1 in the circumferential direction of the housing outer peripheral wall 270, compared to the twentieth embodiment. 212 and 213 are formed at positions rotated 45 degrees to the opposite side of the cover hole 266 . Therefore, the angle between the axes of the suction hole portions 212 and 213 and the axes of the discharge hole portions 214 and 215 is 135 degrees.

The angle between the central axis Axc1 of the electromagnetic drive portion 500 provided in the suction hole portion 212 and the central axis Axc2 of the discharge passage portion 700 provided in the discharge hole portion 214 is about 135 degrees.

Compared to the twentieth embodiment, the fixed portion 25 is formed at a position rotated by a predetermined angle toward the electromagnetic drive portion 500 about the axis Ax1 in the circumferential direction of the housing outer peripheral wall 270 . The inner diameter of the bolt hole 250 formed in the fixed portion 25 is smaller than that of the twentieth embodiment. Also, the outer diameter of the shaft portion 101 of the bolt 100 inserted through the bolt hole 250 is smaller than that of the twentieth embodiment.

In the present embodiment, part of the electromagnetic driving portion 500 and the discharge passage portion 700 are located in the second region T2, but most of the supply passage portion 29, the electromagnetic driving portion 500 and the discharge passage portion 700 are located in the first region T1. positioned. In particular, substantially all of the supply passage portion 29, the electromagnetic drive portion 500, and the discharge passage portion 700 are located on the radially outer side of the cover outer peripheral wall 280 in the first region T1.

Further, in the present embodiment, when viewed from the direction of the axis Ax1 of the cylindrical inner peripheral wall 230, the bolt hole 250, the electromagnetic drive section 500 and the discharge passage section 700 do not overlap.

The thirty-second embodiment has the same configuration as the twentieth embodiment except for the points described above. Also in the thirty-second embodiment, the same effect as in the twentieth embodiment can be obtained.

(33rd Embodiment)
<D-02> FIG. 88 shows part of the high-pressure pump according to the thirty-third embodiment. The thirty-third embodiment differs from the twenty-ninth embodiment in the configurations of the upper housing 21 and the cover 26, and the like.

In this embodiment, the upper housing 21 is formed so that the outer peripheral wall 270 of the housing expands radially outward compared to the twenty-ninth embodiment. Further, the cylindrical cover portion 261 has a shorter length in the axial direction than in the twentieth embodiment, and the end opposite to the cover bottom portion 262 contacts the end surface of the upper housing 21 opposite to the lower housing 22 . ing. Here, the end portion of the cover tubular portion 261 and the upper housing 21 are joined over the entire circumferential direction by, for example, welding.

As described above, in this embodiment, the cylindrical cover portion 261 is not positioned radially outward of the upper housing 21 , and forms the fuel chamber 260 between the upper housing 21 and the end surface of the upper housing 21 opposite to the lower housing 22 . there is

The weld ring 519 is formed so that the end on the pressurizing chamber 200 side expands radially outward, and abuts around the suction hole portion 212 of the flat portion 271 of the housing outer peripheral wall 270 . The weld ring 519 is welded to the flat portion 271 of the housing outer peripheral wall 270 over the entire circumferential range at the end on the side of the pressure chamber 200 , and over the entire circumferential range at the portion opposite to the pressure chamber 200 . It is welded to the outer peripheral wall of the first tubular portion 511 . This prevents the fuel inside the suction hole portion 212 from leaking to the outside of the upper housing 21 through the gap between the inner peripheral wall of the suction hole portion 212 and the outer peripheral wall of the first cylindrical portion 511 . .

The weld ring 709 is formed so that the end on the pressurizing chamber 200 side expands radially outward, and abuts around the discharge hole portion 214 of the flat portion 271 of the housing outer peripheral wall 270 . The weld ring 709 is welded to the flat portion 271 of the housing outer peripheral wall 270 over the entire circumferential range at the end on the side of the pressure chamber 200 , and over the entire circumferential range at the portion opposite to the pressure chamber 200 . It is welded to the outer peripheral wall of the discharge joint 70 . This prevents the fuel inside the discharge hole 214 from leaking to the outside of the upper housing 21 through the gap between the inner peripheral wall of the discharge hole 214 and the outer peripheral wall of the discharge joint 70 .

In this embodiment, passages 204 and 205 are formed in the upper housing 21 . A passage 204 is formed in the upper housing 21 so as to communicate between the fuel chamber 260 and the pressurization chamber 200 . A passage 205 is formed in the upper housing 21 so as to communicate between the fuel chamber 260 and the lateral hole portion 702 . A hole portion 222 is formed in the upper housing 21 and the lower housing 22 so as to allow the fuel chamber 260 and the annular space 202 to communicate with each other.

The thirty-third embodiment has the same configuration as the twenty-ninth embodiment except for the points described above. Also in the thirty-third embodiment, the same effect as in the twenty-ninth embodiment can be obtained.

(34th embodiment)
<D-03> A part of the high-pressure pump according to the thirty-fourth embodiment is shown in FIGS. The thirty-fourth embodiment differs from the twentieth embodiment in the configuration of the supply passage portion 29 .

In this embodiment, the supply passage portion 29 has a supply cylinder portion 291 , a projecting portion 292 , an enlarged portion 293 and a flange portion 294 . The supply tube portion 291 is formed in a substantially cylindrical shape. The inner diameter of one end of the supply cylinder part 291 is larger than the inner diameter of the other end.

The projecting portion 292 is formed integrally with the supply cylinder portion 291 so as to protrude radially outward from the outer peripheral wall of the supply cylinder portion 291 . The projecting portion 292 is formed in an annular shape.

The enlarged portion 293 is formed integrally with the supply tube portion 291 so as to protrude radially outward from the outer peripheral wall of one end of the supply tube portion 291 . The enlarged portion 293 is formed in a substantially cylindrical shape. The flange portion 294 is formed integrally with the enlarged portion 293 so as to protrude radially outward from the outer peripheral wall of one end of the enlarged portion 293 . The flange portion 294 is formed in an annular shape.

In the present embodiment, one end of the supply passage portion 29 extends from the outer wall around the cover hole portion 265 of the cover cylindrical portion 261 , that is, the outer periphery of the cover so that the inner space communicates with the fuel chamber 260 via the cover hole portion 265 . It is provided so as to be connected to the flat portion 281 of the wall 280 . Here, the flange portion 294 and the flat portion 281 of the cover outer peripheral wall 280 are welded over the entire circumferential region of the supply passage portion 29 .

A fuel supply pipe 7 is connected to the side of the supply tubular portion 291 opposite to the flange portion 294 . The projecting portion 292 can lock the end of the fuel supply pipe 7 .

(Other embodiments)
<A> In the above-described embodiment, when h is the number of communication holes 44 and g is the number of guide portions 43, the inner edge portion of one of the tapered portions 42 divided by the guide portions 43 into a plurality of tapered portions 42 An example in which the number of communicating holes 44 facing to is h/g is shown. On the other hand, in other embodiments, the number of communication holes 44 may not be h/g. Further, the number of communication holes 44 facing the inner edge of one of the tapered portions 42 divided by the guide portion 43 may be one.

In another embodiment, the valve member 40 has a surface 401 on the side of the seat member 31 whose curvature amount QC1 is the same as that of the valve member 40 and the seat member 31 when the valve member 40 is separated from the seat member 31 . may be set to be the same as the minimum value DL1 of the distance from .

In another embodiment, the rigidity of the member is changed by making the valve member 40 or the seat member 31 have a convex shape, or by making the plate thickness of the center side of the valve member 40 thicker than that of the outer edge portion. , the sealing performance may be enhanced so that the valve member 40 deforms following the seat member 31 .

<B> In the sixteenth embodiment described above, the inner cylindrical surface 602 is formed in a tapered shape so as to approach the axis of the spool 61 as it goes from the pressurizing chamber 200 side toward the side opposite to the pressurizing chamber 200. Indicated. Here, in another embodiment, in a cross section along a virtual plane that includes the axis of the spool 61, the minor angle among the angles formed by the inner cylindrical surface 601, which is the inner cylindrical surface with the smallest diameter, and the inner cylindrical surface 602, is the minor angle. may be 120 degrees. In this case, positional displacement of the winding 620 can be suppressed particularly at the connecting portion between the inner cylindrical surface 601 and the inner cylindrical surface 602 .

In the eighteenth embodiment described above, the locking member 576 having higher hardness than the fixed core 57 is provided in the fixed core hole portion 575 to lock the spring 54 . On the other hand, in another embodiment, for example, while setting the hardness of the locking member 576 to be equal to or lower than that of the fixed core 57, the surface of the locking member 576 is provided with a Cr plating layer, a DLC layer, or the like. may Of course, a Cr plating layer, a DLC layer, or the like may be provided on the surface of the locking member 576 having a hardness higher than that of the fixed core 57 .

In another embodiment, the end surface 552 of the movable core 55 on the pressure chamber 200 side may be located on the side opposite to the fixed core 57 with respect to the end surface 621 of the winding portion 62 on the pressure chamber 200 side. good.

Also, in other embodiments, the connecting surfaces 605 and 606 may be formed so that all portions are perpendicular to the axis of the spool 61 . Further, all of the connecting surfaces 605 and 606 may be formed in a tapered shape so as to approach the axis of the spool 61 as they go from the pressurizing chamber 200 side toward the opposite side of the pressurizing chamber 200 . Also, the connecting surfaces 605 and 606 may be configured by a combination of steps having the same height as the winding 620 instead of being tapered.

Further, in another embodiment, the angle formed by the inner cylindrical surface 601 and the connecting surface 605 may be set to other than 120 degrees in the cross section along the virtual plane VP1 including the axis of the spool 61 .

In another embodiment, the winding 620 differs in the number of axial turns in the first layer and the number of axial turns in the second layer extending radially outward from the inner cylindrical surface having the smallest diameter. may Moreover, between the inner cylindrical surface with the smallest diameter and the inner cylindrical surface with the largest diameter, the number of turns in the axial direction for each layer of winding may not be the same for all layers.

Further, in the above-described embodiment, an example in which the winding portion 62 is formed by winding the winding 620 around the spool 61 as the winding forming portion has been described. On the other hand, in another embodiment, the winding portion 62 may be formed by using a part of the resin member forming the connector 65 as the winding forming portion and winding the winding 620 around the winding forming portion. good.

<C> In the above-described embodiment, the annular groove 800 connecting the first flow path 83 and the second flow path 89 is formed in the intermediate member 81 on the surfaces of the intermediate member main body 82 and the relief member main body 86 facing each other. formed. On the other hand, in other embodiments, the annular groove 800 may be formed not only in the intermediate member 81 but also in the relief sheet member 85 only, or in both the intermediate member 81 and the relief sheet member 85.

Also, in another embodiment, the number of second flow paths 89 may be greater than the number of first flow paths 83 and an annular groove 800 may be formed in the relief member main body 86 . Further, in this case, for example, the number of first flow paths 83 may be four and the number of second flow paths 89 may be five.

Also, in another embodiment, the number of second flow paths 89 may be greater than the number of first flow paths 83 and the length of the second flow paths 89 may be shorter than the length of the first flow paths 83 . That is, the axial length of the relief member main body 86 may be shorter than the axial length of the intermediate member main body 82 .

Also, in another embodiment, one first flow path 83 may be formed in the intermediate member main body 82 . Also, one second flow path 89 may be formed in the relief member main body 86 . Moreover, the first flow path 83 and the second flow path 89 may be formed in plural and in the same number. Moreover, in other embodiments, the number of the first flow paths 83 and the number of the second flow paths 89 are not limited to being coprime, and may have any relationship.

In another embodiment, the discharge joint 70 is not provided. For example, the discharge passageway is formed by providing the discharge sheet member 71 and the intermediate member 81 in the discharge hole portion 214 and screwing the relief sheet member 85 to the discharge hole portion 214 . The unit 700 may also be configured.

Also, in other embodiments, the locking member 95 may not be provided. In this case, it is conceivable that the ends of the spring 99 are locked by the intermediate member 81 .

<D> In the above-described embodiment, two bolt holes 250 are formed at equal intervals in the circumferential direction on the radially outer side of the housing outer peripheral wall 270 when viewed from the direction of the axis Ax1 of the cylindrical inner peripheral wall 230. Indicated. In contrast, in other embodiments, the bolt holes 250 may not be formed at equal intervals in the circumferential direction of the housing outer peripheral wall 270 .

In another embodiment, three or more bolt holes 250 may be formed in the circumferential direction on the radially outer side of the housing outer peripheral wall 270 when viewed from the axis Ax1 direction of the cylindrical inner peripheral wall 230 . In this case, it is desirable that the bolt holes 250 are formed at equal intervals in the circumferential direction of the housing outer peripheral wall 270 .

Further, in another embodiment, the housing outer peripheral wall 270 does not have to have the planar flat portion 271 . Further, in another embodiment, the central axis Axc1 of the electromagnetic drive portion 500 and the central axis Axc2 of the discharge passage portion 700 do not have to be positioned on the same plane.

In another embodiment, a pressure sensor capable of detecting the pressure of fuel sucked into the pressurizing chamber 200, a temperature sensor capable of detecting the temperature of fuel sucked into the pressurizing chamber 200, the upper housing 21 or the cover 26 At least one of a vibration sensor capable of detecting the vibration of the cover 26 and a branch passage portion connecting the space inside the cover 26 and the space outside the cover 26 may be further provided. Here, a low-pressure fuel pipe communicating with an injector that injects and supplies low-pressure fuel to the internal combustion engine is connected to the branch passage.

The pressure sensor, the temperature sensor, the vibration sensor, and the branch passage are provided, for example, so as to protrude radially outward from the housing outer wall 270, and extend from the electromagnetic drive unit 500 to the discharge passage in the circumferential direction of the housing outer wall 270. It may be positioned within 180 degrees toward the 700 side, or within 180 degrees toward the electromagnetic drive section 500 side from the discharge passage portion 700 .

The pressure sensor, the temperature sensor, the vibration sensor, and the branch passage are provided on the cover bottom 262 so as to protrude vertically upward in the direction of the axis Ax1 of the cylindrical inner peripheral wall 230 from the upper housing 21 side. may be

In the eleventh embodiment described above, the pulsation damper portion 19 is provided on the cover bottom portion 262 so as to protrude upward in the vertical direction of the cylindrical inner peripheral wall 230 in the direction of the axis Ax1 from the upper housing 21 side. rice field. On the other hand, in another embodiment, the pulsation damper portion 19 is provided, for example, so as to protrude radially outward from the housing outer peripheral wall 270 , and extends from the electromagnetic drive portion 500 in the circumferential direction of the housing outer peripheral wall 270 . It may be located within 180 degrees toward the portion 700 side, or within 180 degrees toward the electromagnetic drive portion 500 side from the discharge passage portion 700 .

Also, in other embodiments, the cover 26 may not be provided. In this case, for example, the supply passage portion 29 may be provided in the upper housing 21 so that the inside of the supply passage portion 29 and the suction passage 216 communicate with each other.

Further, in the above-described embodiment, an example in which the cover tubular portion 261 is formed in a regular octagonal tubular shape is shown. On the other hand, in another embodiment, the cover cylinder part 261 may be formed in a deformed octagonal cylinder shape such that the length of each side is alternately different. Thereby, resonance can be suppressed by changing the eigenvalue, and NV can be reduced.

Moreover, in another embodiment, at least two of the cylinder 23, the upper housing 21, and the lower housing 22 may be integrally formed. Also, in another embodiment, at least two of the upper housing 21, the seat member 31, and the stopper 35 may be integrally formed.

Also, in other embodiments, the high-pressure pump may be applied to internal combustion engines other than gasoline engines, such as diesel engines. Also, the high-pressure pump may be used as a fuel pump that discharges fuel toward a device other than the engine of the vehicle.

Thus, the present disclosure is not limited to the above embodiments, and can be embodied in various forms without departing from the scope of the present disclosure.

The first technical idea of the above invention will be described below.

<A> Conventionally, there is known a high-pressure pump that pressurizes fuel and supplies it to an internal combustion engine. High-pressure pumps generally include a valve member on the low-pressure side of the pressurization chamber. When the valve member is separated from the valve seat, the valve opens to allow the flow of fuel sucked into the pressurizing chamber. do. For example, in the high-pressure pump disclosed in Japanese Patent Application Laid-Open No. 2016-133010, when the plunger descends so as to increase the volume of the pressurizing chamber, the valve member opens and fuel is sucked into the pressurizing chamber. When the plunger rises to reduce the volume of the pressurizing chamber while the valve member is open, the fuel is returned from the pressurizing chamber to the low pressure side, and the fuel pressurized in the pressurizing chamber is metered. be. Further, when the plunger is raised to reduce the volume of the pressurization chamber with the valve member closed, the fuel in the pressurization chamber is pressurized.

In the high-pressure pump disclosed in the patent document (Japanese Patent Application Laid-Open No. 2016-133010), the valve member has a plurality of communication holes on a virtual circle centered on the axis. Further, Patent Literature (JP-A-2016-133010) discloses a valve member having a guide portion capable of guiding axial movement of the valve member by sliding on a member forming the suction passage. . In this valve member, three guide portions are formed in the circumferential direction of the valve member. In addition, three inclined surfaces inclined with respect to the axis of the valve member are formed in the circumferential direction on the outer edge of the surface of the valve member facing the pressure chamber. This inclined surface is formed between the guide portions.

In the high-pressure pump disclosed in the patent document (Japanese Patent Application Laid-Open No. 2016-133010), the inclined surface is formed linearly at the edge of the valve member on the shaft side. Therefore, the distance between both ends of the rim and the communication hole is large, and there is a risk that the both ends of the rim will act as resistance to the fuel flowing on the surface of the valve member. As a result, there is a risk that a sufficient flow rate of fuel sucked into the pressurization chamber or fuel returned from the pressurization chamber to the low pressure side cannot be ensured.

SUMMARY OF THE INVENTION An object of the present invention is to provide a high-pressure pump capable of ensuring a sufficient flow rate of fuel sucked into a pressurizing chamber.

The second technical idea of the above invention will be described below.

<B> Conventionally, a high-pressure pump for pressurizing fuel and supplying it to an internal combustion engine is known. High-pressure pumps generally include a valve member on the low-pressure side of the pressurization chamber. When the valve member is separated from the valve seat, the valve opens to allow the flow of fuel sucked into the pressurizing chamber. do. For example, in the high-pressure pump disclosed in the patent document (U.S. Pat. No. 8,925,525), an electromagnetic drive section is provided on the opposite side of the valve member to the pressurizing chamber to control opening and closing of the valve member, It controls the amount of fuel pressurized by the high pressure pump and the amount of fuel discharged from the high pressure pump.

In general, the magnetic flux density is maximum at the axial center of the coil of the electromagnetic drive unit. All magnetic flux directions are parallel to the axis of the coil and directed from the pressurizing chamber to the fixed core side. Therefore, the closer the end surface of the movable core on the fixed core side is to the center of the coil in the axial direction, the greater the attractive force acting on the movable core when the coil is energized.

However, in the high-pressure pump disclosed in the patent document (U.S. Pat. No. 8,925,525), the end face of the movable core on the fixed core side is located on the pressurizing chamber side with respect to the axial center of the coil, and the movable core is pressurized. The end face on the pressure chamber side is located on the pressure chamber side with respect to the end face on the pressure chamber side of the coil. Therefore, when the coil is energized, the attractive force acting on the movable core may decrease. This may reduce the responsiveness of the movable core. Here, if the current flowing through the coil is increased in order to ensure the responsiveness of the movable core, the power consumption of the electromagnetic drive unit may increase.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a high-pressure pump in which an electromagnetic drive section is highly responsive.

The third technical idea of the above invention will be described below.

<C> Conventionally, a high-pressure pump that pressurizes fuel and supplies it to an internal combustion engine has a relief valve that releases fuel to a pressurization chamber or a low-pressure chamber when the pressure of the fuel discharged from the pressurization chamber exceeds a predetermined value. high pressure pumps are known. For example, in the high-pressure pump disclosed in Japanese Patent Application Laid-Open No. 2004-197834, the relief valve is configured to release fuel to the low-pressure chamber.

2. Description of the Related Art In recent years, there has been a demand for higher pressure fuel to be supplied to an internal combustion engine due to a higher fuel pressure required by an engine system. In order to increase the pressure of the fuel discharged and supplied from the high-pressure pump to the internal combustion engine, it is effective to reduce the dead volume that communicates with the pressurization chamber and becomes a high-pressure space during pressurization. In the high-pressure pump of Patent Document 1, the discharge valve is arranged near the pressurizing chamber, and the relief valve is arranged on the side opposite to the pressurizing chamber with respect to the discharge valve. This makes it possible to reduce the dead volume.

However, in the high-pressure pump disclosed in the patent document (Japanese Patent Application Laid-Open No. 2004-197834), the relief valve is arranged at a position radially displaced from the axis of the discharge valve, and a pressure pulsation reducer is provided between the discharge valve and the relief valve. are provided. Furthermore, a flow path through which the discharged fuel that has passed through the discharge valve flows is formed radially outside the relief valve and the pressure pulsation reducer. Therefore, there is a possibility that the parts including the discharge valve and the relief valve may become large.

SUMMARY OF THE INVENTION An object of the present invention is to provide a compact high-pressure pump.

The fourth technical idea of the above invention will be described below.

<D> Conventionally, a high-pressure pump for pressurizing fuel and supplying it to an internal combustion engine is known. High-pressure pumps generally include a valve member on the low-pressure side of the pressurization chamber. When the valve member is separated from the valve seat, the valve opens to allow the flow of fuel sucked into the pressurizing chamber. do. For example, in the high-pressure pump disclosed in the patent document (European Patent No. 1479903), an electromagnetic drive section is provided on the opposite side of the valve member to the pressurizing chamber to control the opening and closing of the valve member, It controls the amount of fuel pressurized by the high pressure pump and the amount of fuel discharged from the high pressure pump.

In the high-pressure pump of the patent document (European Patent No. 1479903), the electromagnetic drive portion is provided so as to protrude radially outward from the outer peripheral wall of the housing that forms the pressure chamber. Further, a discharge passage through which fuel discharged from the pressurizing chamber flows is provided so as to protrude radially outward from the outer peripheral wall of the housing.

Since the high-pressure pump is attached to the internal combustion engine, a rotating object such as a pulley may be positioned near the high-pressure pump depending on the location where the high-pressure pump is attached. A wire is connected to the electromagnetic drive portion of the high-pressure pump, and a steel pipe is connected to the discharge passage portion. Therefore, depending on the position where the high-pressure pump is installed, there is a risk that the rotating object will come into contact with the wiring and steel pipes, damaging the wiring and steel pipes.

Also, the high-pressure pump of the patent document (European Patent No. 1479903) has a fixed portion that has a plurality of bolt holes and is fixed to the internal combustion engine. Three bolt holes are formed at equal intervals in the circumferential direction on the radially outer side of the outer peripheral wall of the housing when viewed from the axial direction of the cylindrical inner peripheral wall forming the pressure chamber. Here, the electromagnetic drive portion, the discharge passage portion, and the supply passage portion through which the fuel supplied to the pressurizing chamber flows are arranged respectively between the three bolt holes. When the fixed portion is fixed to the internal combustion engine and the high-pressure pump is attached to the internal combustion engine, the bolt is inserted through the bolt hole. At this time, it is necessary to prevent the bolt and the tool for tightening the bolt from interfering with the electromagnetic drive section, the discharge passage section, or the supply passage section. Cannot be placed on an axis. Therefore, the electromagnetic drive portion, the discharge passage portion, and the supply passage portion cannot be collectively arranged at a specific portion in the circumferential direction of the housing. Therefore, there is a possibility that the degree of freedom of the mounting position of the high-pressure pump to the internal combustion engine may be reduced.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a high-pressure pump that has a high degree of freedom in mounting position to an internal combustion engine.

10 high pressure pump 23 cylinder (pressure chamber forming portion) 200 pressure chamber 21 upper housing (suction passage forming portion, housing) 35 stopper (suction passage forming portion) 216 suction passage 31 seat member 32 series passage (inner communicating passage), 33 communicating passage (outer communicating passage), 40 valve member, 41 valve body, 44, 441, 442, 443 communicating hole, 42 tapered portion, 43 guide portion, VC1 virtual circle, B1 boundary line, CC1 concentric circles,
51 cylindrical member, 53 needle, 55 movable core, 54 spring (biasing member), 57 fixed core, 60 coil, 61 spool (winding forming part), 62 winding part, 620 winding, 600 outer cylindrical surface, 601, 602, 603 inner cylindrical surface,
217 Discharge passage 71 Discharge seat member 72 Discharge member main body 73 Discharge hole 74 Discharge valve seat 81 Intermediate member 82 Intermediate member main body 83 First flow path 85 Relief sheet member 86 Relief member main body 87 Relief hole, 88 relief valve seat, 89 second flow path, 75 discharge valve, 91 relief valve, 800 annular groove,
1 engine (internal combustion engine), 230 cylindrical inner peripheral wall, 11 plunger, 270 housing outer peripheral wall, 500 electromagnetic drive part, 700 discharge passage part, 25 fixed part, 250 bolt hole, 100 bolt, VS0 virtual plane, T1 first first area, T2 second area

Claims (9)

a pressurization chamber forming part (23) that forms a pressurization chamber (200) in which fuel is pressurized;
suction passage forming portions (21, 35) forming a suction passage (216) through which fuel sucked into the pressurization chamber flows;
an inner communication passage (32) provided in the suction passage and positioned radially inward of the suction passage and communicating between one surface and the other surface; a sheet member (31) provided with an outer communication passage (33) communicating between one surface and the other surface;
A valve member ( 40 ) and
The valve member includes a plate-like valve body (41), a plurality of communication holes ( 44, 441, 442, 443), the surface on the pressure chamber side provided on the radially outer side of the valve body approaches the axis (Ax2) of the valve body as it goes from the seat member side toward the pressure chamber side. a taper portion (42) formed in a tapered shape, and a taper portion (42) protruding radially outward from the valve body so as to divide the taper portion into a plurality of pieces in the circumferential direction, and sliding on the intake passage forming portion to slide the valve member; has a plurality of guide portions (43) capable of guiding the movement of
the plurality of communication holes are arranged on a virtual circle (VC1) centered on the axis of the valve body,
A boundary line (B1) between the inner edge of the tapered portion and the outer edge of the valve body is formed along a concentric circle (CC1) with respect to the virtual circle ,
A high-pressure pump (10) , wherein a boundary line between the guide portion and the taper portion is curved . 2. The high-pressure pump according to claim 1, wherein a boundary line between the guide portion and the tapered portion is formed to be convex with respect to a straight line (L11) extending from the center of the valve body and passing through the center of the guide portion. . Assuming that the number of the communication holes is h and the number of the guide portions is g,
3. The high-pressure pump according to claim 1, wherein the number of said communication holes facing the inner edge of one of said tapered portions divided by said guide portion is equal to h/g. A boundary line between the inner edge of one tapered portion sandwiched by the two guide portions and the outer edge of the valve body extends from the center of the valve body, and the inner edges of the tapered portions face each other. 3. A high-pressure pump according to claim 1 or 2, which is formed in a range between two straight lines (LC11) passing through the centers of the end communication holes (441, 443), which are the communication holes at both ends of the communication holes. In the guide portion, the sliding portion (430), which is a portion that slides on the suction passage forming portion, extends from the center of the valve body and extends along two tangent lines that pass through the outer edges of the two adjacent communication holes facing each other. The high pressure pump according to any one of claims 1 to 4, wherein the high pressure pump is formed in a range between (LT21). The valve member according to any one of claims 1 to 5, wherein the surface (401) on the side of the seat member is curved in a cross section along a virtual plane (VP1) including the axis of the valve body. high pressure pump. The valve member is formed so as to curve toward the pressure chamber side or the seat member side as it goes radially outward from the center of the surface on the side of the seat member, and extends axially on the pressure chamber side of the seat member. The amount of curvature (QC1), which is the distance between the center of the surface on the seat member side in the axial direction of the valve member and the outer edge portion, is the same as that when the valve member is separated from the seat member. 7. The high-pressure pump according to claim 6, wherein the distance between the valve member and the seat member is set equal to or smaller than the minimum value (DL1). 8. The high-pressure pump according to claim 6, wherein the valve member is formed such that a surface on the side of the seat member is convex toward the side of the seat member. Applied to a fuel supply system (9) having a fuel injection valve (138) for supplying fuel to an internal combustion engine (1),
In the fuel supply system in which the maximum injection pressure of the fuel injected by the fuel injection valve is 20 MPa or more,
The valve member has an annular seal portion (413) that seals between the outer communication passage and the outer flow passage (45) positioned radially outward with respect to the valve member,
If the diameter of the seal portion is D, the plate thickness of the valve member is t, and the plate thickness ratio is t/D,
The high-pressure pump according to any one of claims 1 to 8, wherein 0.06≤t/D≤0.13.

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