JP5370792B2 - Valve device and high-pressure pump using the valve device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve device reducing a driving unit in size, and also to provide a high pressure pump using the valve device. <P>SOLUTION: A valve seat 78 has an inner passage 781 and outer passages 782. A suction valve member 74 has first passages 743 and a first projection portion 744 that guides, to the first passage 743, the fuel that flows from a pressure chamber at the time of valve opening. Therefore, an action force by the dynamic pressure applied to the suction valve member 74 in the valve closing direction, is reduced. An action force by the pressure of fuel that flows into pressure equalization grooves 746, 784 and 785, counterbalances the action force by the dynamic pressure of the suction valve member 74. Therefore, self-closing by the dynamic pressure is inhibited, and the maximum output of the electromagnetic driving unit is also reduced. Fuel flows through a passage radially outside the suction valve member 74 and the first passages 743. Compared with the constitution of only the radially outside passage of the suction valve member 74, an equivalent fluid passage area is secured even when the lift amount of the suction valve member 74 is small, and the maximum output of the electromagnetic driving unit is reduced. The size reduction of the electromagnetic driving unit is provided thereby. <P>COPYRIGHT: (C)2013,JPO&amp;INPIT

Description

  The present invention relates to a valve device capable of opening and closing a flow path and a high-pressure pump using the valve device.

  For example, a valve device is used to block the flow path through which the fluid flows. One type of the valve device includes a valve member that can approach and separate from a valve seat in the valve body. This type of valve device closes when the valve member abuts on the valve seat, and opens when the valve member moves away from the valve seat. The position of the valve member is controlled by the movable member of the drive unit. Examples of the driving method of the movable member include an electromagnetic type and an electric type.

  Further, the valve device includes a normally open type that opens when the drive unit is not operated, and a normally closed type that closes when the drive unit is not operated. In the normally open type, the valve member is urged in the valve opening direction by the urging member and separated from the valve seat when the drive unit is not operated. Further, the valve member is allowed to move toward the valve seat when the movable member moves in the valve closing direction against the urging force of the urging member when the drive unit is actuated.

  In the normally closed type, the valve member is urged in the valve closing direction by the urging member and abuts on the valve seat when the drive unit is not operated. The valve member is allowed to move to the opposite side of the valve seat when the movable member moves in the valve opening direction against the urging force of the urging member when the drive unit is actuated.

  The said valve apparatus is disclosed by patent documents 1-7, for example. The fuel intake valve of the high-pressure pump disclosed in Patent Documents 1 and 2 is a normally open type valve device having an electromagnetic drive unit. When the valve is opened, the outer wall surface outside the diameter of the valve member and the valve body The fuel flows through a passage between the inner wall surface. The valve member of Patent Document 1 receives the flow of fuel from the pressurizing chamber during metering of the high-pressure pump. At this time, the dynamic pressure applied to the valve member increases particularly during high-speed operation of the high-pressure pump. On the other hand, in the fuel intake valve of Patent Document 2, a stopper that restricts movement of the valve member in the valve opening direction is provided on the pressure chamber side with respect to the valve member, and fuel flowing from the pressure chamber directly hits the valve member. Is avoiding.

  The fuel intake valve of the high-pressure pump disclosed in Patent Document 3 is a normally closed valve device including an electromagnetic drive unit. This fuel intake valve is provided with a movable member at the axial center of a valve member having a plurality of first flow paths, and a flow path from the pressurizing chamber to the fuel gallery by lifting a plate made of an elastic member with the movable member. Is secured. The gas valves disclosed in Patent Documents 4 to 6 are normally open type and normally closed type valve devices each including an electromagnetic drive unit.

  The flow control valve disclosed in Patent Document 7 is a normally closed type and normally open type valve device including a drive unit including a piezoelectric actuator. In these valve devices of Patent Documents 3 to 7, when the valve is opened, fluid flows through the plurality of first flow paths of the valve member. At this time, dynamic pressure in the valve opening direction generated by the flow of fluid is applied to portions other than the first flow path of the valve member.

JP 2004-218633 A JP 2010-156264 A US Patent Application Publication No. US2010 / 0242922A1 US Patent Application Publication No. US2007 / 0057096A1 Specification US Pat. No. 7,124,998 B2 JP-A-11-311150 JP 2010-230159 A

  The valve member of Patent Document 1 is not configured to avoid dynamic pressure generated by the flow of fuel from the pressurizing chamber. Therefore, in order to prevent the so-called self-closing that the valve member is closed by the dynamic pressure, it is necessary to increase the urging force of the urging member that urges the valve member in the valve opening direction. Along with this, the attraction force of the electromagnet of the drive unit necessary for moving the movable member against the biasing force of the biasing member increases. Therefore, the problem that a drive part enlarges arises.

  Further, if the lift amount of the valve member from the valve seat is too small, a necessary flow passage area cannot be ensured, so there is a limit to reducing the lift amount. The electromagnet of the driving unit needs to generate an attractive force for attracting a movable member that is separated by a lift amount or more. This is also a factor that increases the size of the drive unit.

  In the fuel intake valve of Patent Document 2, ringing generated between the valve member and the stopper may adversely affect the valve closing response. Here, the ringing force acting on the valve member can be reduced by forming a communication hole communicating with the stopper from the inside to the outside. However, if the communication hole is too large, fuel flows into the stopper through the communication hole. This fuel flow acts on the valve member in the valve closing direction. Therefore, there is a problem that the self-closing of the valve member cannot be sufficiently suppressed. In addition, the tuning of the inner diameter of the communication hole depends on the kinematic viscosity of the fuel and the flow rate of the fuel, so it is necessary to change according to the recent world fuel compatibility and the cam specifications and the maximum pump speed required by the customer. There is also a problem.

  Since the valve devices of Patent Documents 3 to 7 increase the flow path area by forming a plurality of first flow paths in the valve member, the lift amount of the valve member from the valve seat can be reduced. However, the problem that the drive unit becomes large in relation to preventing the self-closing of the valve member is the same as in the case of Patent Document 1.

  This invention is made | formed in view of the above points, The objective is to provide the high-pressure pump using the valve apparatus which can miniaturize a drive part, and this valve apparatus.

The valve device according to the present invention includes a valve body, a valve seat, a valve member, and a drive unit. The valve seat has an inner channel located in the radial direction of the valve body and an outer channel located in the radial direction. The valve member can be brought into contact with and separated from the valve seat, and has a first flow path positioned between the inner flow path and the outer flow path in the radial direction.
The fluid passes through a radially outer flow path in a radially outward direction with respect to the valve member, a path reaching the outer flow path of the valve seat, a path reaching the outer flow path of the valve seat through the first flow path of the valve member, And flows through the first flow path of the member to the inner flow path of the valve seat.

  For this reason, even when the lift amount of the valve member from the valve seat is made smaller than that of a configuration having only an outer diameter flow path, an equivalent flow path area can be ensured. Therefore, the lift amount can be reduced, and the maximum output of the drive unit can be reduced. Thereby, size reduction of a drive part is implement | achieved. Furthermore, the effect of reducing the collision noise between the valve member and the movable member can be obtained by reducing the lift amount.

  In the present invention, the valve member forms an annular first seal portion, an annular second seal portion, and an annular third seal portion. The first seal portion seals between the inner flow path and the first flow path when the valve member and the valve seat come into contact with each other. The second seal portion seals between the first flow path and the outer flow path when the valve member and the valve seat come into contact with each other. The third seal portion seals between the outer flow path and the outer diameter flow path when the valve member and the valve seat come into contact with each other.

  The force due to the pressure of the fluid flowing between the valve seat and the valve member acts on each seal portion so as to open the valve member. The force in the valve opening direction acting on each of the seal portions acts on the valve member equally in the circumferential direction, and the valve closing force received by the valve member due to the flow of fluid from the opposite side of the valve seat to the valve member. Can be offset.

  Therefore, in the case of a normally open type valve device, for example, even if the urging force of the urging member that urges the valve member in the valve opening direction is reduced, self-closing of the valve member can be suppressed. Therefore, the urging force of the urging member can be reduced, and the maximum output of the drive unit that moves the movable member against the urging force of the urging member can be reduced. Thereby, further downsizing of the drive unit is realized.

  In the case of a normally closed type valve device, for example, the self-closing of the valve member can be suppressed even if the maximum output of the drive unit that presses the valve member in the valve opening direction is reduced. Therefore, the maximum output of the drive unit can be reduced, and the drive unit can be further downsized.

  Moreover, this invention suppresses that the flow of the fluid from the opposite side to a valve seat with respect to a valve member goes to an outer diameter flow path with a guide means. By suppressing the flow to the outer diameter flow path, the dynamic pressure applied to the outer peripheral portion of the valve member can be reduced. The guiding means guides the fluid to the first flow path. That is, the action of the dynamic pressure on the portion other than the first flow path of the valve member can be suppressed as much as possible. The fluid guided to the first flow path is supplied between the valve seat and the valve member, and generates a force that acts on the valve member in the valve opening direction as described above. Therefore, the guide means can reduce the maximum output of the drive unit and contribute to further miniaturization of the drive unit.

  As described above, by reducing the maximum output of the drive unit, an effect of reducing the applied current of the drive unit can be obtained. This eliminates the need for expensive elements in the drive circuit that controls the drive unit, thereby reducing the cost of the drive circuit.

It is sectional drawing of the high pressure pump by 1st Embodiment of this invention. It is the II-II sectional view taken on the line of FIG. It is the III-III sectional view taken on the line of FIG. FIG. 2 is an enlarged cross-sectional view illustrating an intake valve portion of the high-pressure pump in FIG. 1 when the intake valve portion is open. FIG. 5 is a diagram illustrating the second suction valve body of FIG. 4, (b) a longitudinal sectional view of the second suction valve body, (a) a diagram of the second suction valve body viewed from the direction of the arrow Va in the longitudinal sectional view, c) A view of the second intake valve body as seen in an arrow Vc arrow of the longitudinal sectional view. It is a figure which shows the intake valve member of FIG. 4, Comprising: (b) The longitudinal cross-sectional view of an intake valve member, (a) The figure which looked at the intake valve member from the arrow VIa direction of the longitudinal cross-sectional view, (c) The intake valve member It is the figure seen from the arrow VIc direction of a longitudinal cross-sectional view. FIG. 2 is an enlarged cross-sectional view showing an intake valve portion of the high-pressure pump shown in FIG. 1 when the intake valve portion is closed. It is a figure which shows the flow of the fuel of the suction valve part at the time of metering of the high pressure pump of FIG. It is sectional drawing of the suction valve part of the high pressure pump by 2nd Embodiment of this invention. It is sectional drawing of the suction valve part of the high pressure pump by 3rd Embodiment of this invention. It is a figure which shows the suction valve member of the high pressure pump by 4th Embodiment of this invention, Comprising: (b) The longitudinal cross-sectional view of a suction valve member, (a) The figure which looked at the suction valve member from the arrow XIa direction of the longitudinal cross-sectional view (C) It is the figure which looked at the suction valve member from the arrow XIc direction of the longitudinal cross-sectional view. It is a figure which shows the suction valve member of the high pressure pump by 5th Embodiment of this invention, Comprising: (b) The longitudinal cross-sectional view of a suction valve member, (a) The figure which looked at the suction valve member from the arrow XIIa direction of a longitudinal cross-sectional view (C) It is the figure which looked at the suction valve member from the arrow XIIc direction of a longitudinal cross-sectional view. It is a figure which shows the suction valve member of the high pressure pump by 6th Embodiment of this invention, Comprising: (b) The longitudinal cross-sectional view of a suction valve member, (a) The figure which looked at the suction valve member from the arrow XIIIa direction of a longitudinal cross-sectional view (C) It is the figure which looked at the suction valve member from the arrow XIIIc direction of a longitudinal cross-sectional view. It is a figure which shows the suction valve member of the high pressure pump by 7th Embodiment of this invention, Comprising: (b) The longitudinal cross-sectional view of a suction valve member, (a) The figure which looked at the suction valve member from the arrow XIVa direction of the longitudinal cross-sectional view (C) It is the figure which looked at the suction valve member from the arrow XIVc direction of the longitudinal cross-sectional view. It is sectional drawing of the suction valve part of the high pressure pump by 8th Embodiment of this invention. It is the front view of the 1st disc member of Drawing 15, Comprising: It is the figure which looked at the 1st disc member of Drawing 15 from the arrow Y direction. It is the front view of the 2nd disc member of Drawing 15, Comprising: It is the figure which looked at the 1st disc member of Drawing 15 from the arrow Y direction. It is sectional drawing of the suction valve part of the high pressure pump by 9th Embodiment of this invention. It is sectional drawing of the suction valve part of the high pressure pump by 10th Embodiment of this invention. It is sectional drawing of the suction valve part of the high pressure pump by 11th Embodiment of this invention. It is sectional drawing of the suction valve part of the high pressure pump by 12th Embodiment of this invention. It is sectional drawing of the suction valve part of the high pressure pump by the modification of 12th Embodiment of this invention. It is sectional drawing of the suction valve part of the high pressure pump by 13th Embodiment of this invention. It is the figure which looked at the stopper of FIG. 23 from the arrow XXIV direction. It is sectional drawing of the suction valve part of the high pressure pump by 14th Embodiment of this invention. It is a figure which shows the suction valve member of FIG. 25, Comprising: (a) The top view of a valve member, (b) It is the bb sectional view taken on the line of the top view of a valve member. It is a figure which shows the stopper of FIG. 25, Comprising: (b) The longitudinal cross-sectional view of a stopper, (a) The figure which looked at the stopper from the arrow a direction of the longitudinal cross-sectional view, (c) The stopper from the arrow c direction of a longitudinal cross-sectional view FIG. It is sectional drawing of the suction valve part of the high pressure pump by the modification of 14th Embodiment of this invention. It is a figure which shows the stopper of FIG. 28, Comprising: (a) The top view of a valve member, (b) The bb sectional view taken on the line of the top view of a valve member. It is sectional drawing of the suction valve part of the high pressure pump by 15th Embodiment of this invention. It is the figure which looked at the suction valve member of FIG. 30 from the arrow XXXI direction. It is the figure which looked at the 2nd intake valve body of FIG. 30 from the arrow XXXII direction. It is sectional drawing of the suction valve part of the high pressure pump by the modification of 15th Embodiment of this invention. It is the figure which looked at the suction valve member of FIG. 33 from the arrow XXXIV direction.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In the embodiments, substantially the same components are denoted by the same reference numerals and description thereof is omitted.
(First embodiment)
A high-pressure pump according to a first embodiment of the present invention is shown in FIGS. The high-pressure pump 1 is a fuel pump that pressurizes fuel supplied from a fuel tank (not shown) and discharges the pressurized fuel to a fuel rail. The high-pressure pump 1 includes a main body unit 10, a fuel supply unit 30, a plunger unit 20, a fuel suction unit 70, and a fuel discharge relief unit 90. The fuel suction portion 70 corresponds to a “valve device” described in the claims. In the following description, the upper part of FIG. 1 is described as “upper” and the lower part of FIG. 1 is described as “lower”.

The main body 10 includes a lower housing 11, a cylinder 13, and an upper housing 15.
The lower housing 11 includes a cylindrical cylinder holding portion 111, an annular flange portion 112 protruding radially outward from a lower portion of the cylinder holding portion 111, and a cylindrical engine fitting portion 113 protruding downward from the flange portion 112. Have. The inner diameter of the engine fitting portion 113 is larger than the outer diameter of the cylinder holding portion 111. The cylinder holding part 111 has a first press-fitting hole 121. The flange portion 112 has a through hole 114 at a position between the cylinder holding portion 111 and the engine fitting portion 113.

  The cylinder 13 includes a cylindrical portion 131 that slidably supports the plunger 21, a bottom portion 136 that closes the upper end of the cylindrical portion 131, and an annular protrusion 135 that protrudes radially outward below the cylinder holding portion 111. The cylinder 13 is fixed to the first press-fitting hole 121 of the cylinder holding part 111 by press-fitting. The protrusion 135 restricts the upward movement of the cylinder 13.

  The cylinder 13 has a pressurizing chamber 14 in which the inner wall of the cylindrical portion 131, the inner wall of the bottom portion 136, and the upper end surface 211 of the plunger 21 are defined. The volume of the pressurizing chamber 14 changes due to the reciprocating movement of the plunger 21. The cylinder part 131 has a suction hole 141 and a discharge hole 142 communicating with the pressurizing chamber 14. The suction hole 141 and the discharge hole 142 are positioned symmetrically with respect to the axis of the plunger 21.

  The upper housing 15 has a rectangular parallelepiped shape that is long in the direction connecting the suction hole 141 and the discharge hole 142. The upper housing 15 has a second press-fit hole 151 at the center in the longitudinal direction. The cylinder 13 is fixed to the second press-fitting hole 151 of the upper housing 15 by press-fitting.

  The upper housing 15 has a suction passage 152 communicating with the suction hole 141 of the cylinder 13 and a plurality of through holes 153 penetrating the upper housing 15 in and out. The fuel sucked by the pressurizing chamber 14 can flow through the suction passage 152. Further, the upper housing 15 has a discharge passage 154 communicating with the discharge hole 142 of the cylinder 13. The fuel discharged from the pressurizing chamber 14 can flow through the discharge passage 154.

The fuel supply unit 30 includes a cover 31, a pulsation damper 33, and a fuel inlet 35.
The cover 31 has a bottomed cylindrical shape and includes a cover bottom portion 311 and a cover tube portion 312. The cover bottom portion 311 closes the upper end of the cover cylinder portion 312. The lower end of the cover tube portion 312 is in contact with the flange portion 112 of the lower housing 11. The cover 31 accommodates the upper housing 15 and the upper part of the cylinder 13.

  The cover cylinder portion 312 has a first fitting hole 325, a second fitting hole 326, and a third fitting hole 327 that are separated from each other in the circumferential direction. The position of the first fitting hole 325 corresponds to the suction passage 152, and the position of the second fitting hole 326 corresponds to the discharge passage 154. The first intake valve body 72 is inserted from the outside of the cover 31 into the first fitting hole 325. The first discharge valve body 91 is inserted into the second fitting hole 326 from the outside of the cover 31.

  The cover 31 and the flange portion 112 are joined by welding. The first intake valve body 72, the first discharge valve body 91, and the fuel inlet 35 are joined to the cover 31 by welding. By this welding, the gap between the lower end of the cover 31 and the flange portion 112, the gap between the first fitting hole 325 and the first suction valve body 72, and the second fitting hole 326 and the first discharge valve body 91 are separated. The gap and the gap between the third fitting hole 327 and the fuel inlet 35 are sealed in a liquid-tight manner.

  A fuel gallery 32 defined by the cover 31 and the flange portion 112 is formed in the cover 31. The fuel supplied from the fuel inlet 35 to the fuel gallery 32 is supplied into the first intake valve body 72 via the through hole 153 and the like.

  A pulsation damper 33 is provided in the fuel gallery 32. The pulsation damper 33 is composed of two circular dish-shaped diaphragms 331 and 332 joined at outer edges, and seals a gas of a predetermined pressure inside. The pulsation damper 33 is fixed to the inner wall of the cover 31 so that the outer edge portion is sandwiched between the upper support 341 and the lower support 342. The pulsation damper 33 is elastically deformed according to a change in the pressure of the fuel in the fuel gallery 32 to reduce the pressure pulsation of the fuel in the fuel gallery 32.

The plunger portion 20 includes a plunger 21, an oil seal holder 22, a spring seat 23, a plunger spring 24, and the like.
The plunger 21 has a large diameter part 212 and a small diameter part 213. The large diameter portion 212 is supported by the cylinder 13 so as to be slidable in the axial direction. The small-diameter portion 213 extends downward from the large-diameter portion 212, and a lower end thereof can abut on a tappet or the like (not shown). The tappet makes an outer surface abut on a cam attached to a camshaft (not shown), and reciprocates in the axial direction according to the cam profile by the rotation of the camshaft.

  The oil seal holder 22 includes a fixed portion 222 fixed to the engine fitting portion 113 of the lower housing 11 and a cylindrical seal holding portion 221 that is positioned below the cylinder 13 and through which the small diameter portion 213 of the plunger 21 is inserted. Have. The seal holding part 221 holds the seal 223. The seal 223 includes a Teflon (registered trademark) ring on the inner diameter side and an O-ring on the outer diameter side, and adjusts the thickness of the fuel oil film around the small diameter portion 213. In addition, an oil seal 225 is fixed to the lower end portion of the seal holding portion 221. The oil seal 225 adjusts the thickness of the oil oil film around the small diameter portion 213.

  The spring seat 23 is fixed to the lower end portion of the plunger 21. One end of the plunger spring 24 is locked to the spring seat 23, and the other end is locked to the fixing portion 222 of the oil seal holder 22. The plunger spring 24 functions as a return spring for the plunger 21 and biases the plunger 21 so that the plunger 21 abuts against the tappet. The plunger unit 20 reciprocates the plunger 21 according to the rotation of the camshaft, and changes the volume of the pressurizing chamber 14.

The fuel discharge relief portion 90 includes a first discharge valve body 91, a second discharge valve body 92, a discharge valve member 94, a relief valve member 96, and the like.
The first discharge valve body 91 has a cylindrical shape and is fixed to the discharge passage 154 of the upper housing 15.
The second discharge valve body 92 is provided in the first discharge valve body 91. The second discharge valve body 92 has a bottomed cylindrical shape, and is sandwiched between the first discharge valve body 92 and the upper housing 15 in a state where the open end is located on the pressurizing chamber 14 side.

  The bottom of the second discharge valve body 92 includes a discharge passage 95 and a relief passage 97 that is not in communication with the discharge passage 95. The discharge passage 95 opens to the radially outer side of the wall surface of the bottom portion of the second discharge valve body 92 on the pressurizing chamber 14 side, and is formed on the wall surface on the opposite side of the pressurizing chamber 14 at the bottom portion of the second discharge valve body 92. The center is open. The relief passage 97 opens to the center of the wall surface of the bottom portion of the second discharge valve body 92 on the side of the pressurizing chamber 14 and the wall surface on the opposite side of the pressurizing chamber 14 on the bottom portion of the second discharge valve body 92. Open to the outside of the diameter.

  The discharge valve member 94 is located on the opposite side of the pressurizing chamber 14 with respect to the bottom of the second discharge valve body 92 and can open and close the discharge passage 95. The discharge valve member 94 is urged in the valve closing direction by a discharge valve spring 943 held by a discharge valve spring holder 945.

  The relief valve member 96 is located on the pressure chamber 14 side with respect to the bottom of the second discharge valve body 92 and can open and close the relief passage 97. The relief valve member 96 is urged in the valve closing direction by a relief valve spring 963 held by a relief valve spring holder 965.

The fuel suction part 70 is a normally open type, and is composed of a suction valve part 71 and an electromagnetic drive part 81. The fuel suction portion 70 corresponds to a “valve device” described in the claims. The electromagnetic drive unit 81 corresponds to a “drive unit” recited in the claims.
The intake valve portion 71 includes a first intake valve body 72, a second intake valve body 73, an intake valve member 74, a spring guide 75, and the like.

  The first suction valve body 72 has a cylindrical shape and is fixed to the inner wall of the suction passage 152. The first suction valve body 72 has a suction chamber 711 inside. The suction chamber 711 is provided with a second suction valve body 73. The second suction valve body 73 has a cylindrical shape and has a valve seat 78 formed of a partition wall that partitions the internal space. The second intake valve body 73 corresponds to a “valve body” recited in the claims.

  The suction valve member 74 has a disk shape, is located on the pressurizing chamber 14 side with respect to the valve seat 78, and can contact and separate from the valve seat 78. The suction valve member 74 communicates the suction chamber 711 and the pressurizing chamber 14 by being separated from the valve seat 78. Further, the suction valve member 74 is in contact with the valve seat 78 to shut off the suction chamber 711 and the pressurizing chamber 14. The suction valve member 74 corresponds to a “valve member” recited in the claims.

  The spring guide 75 has a bottomed cylindrical shape, and is provided on the pressurizing chamber 14 side with respect to the second suction valve body 73. The spring guide 75 corresponds to a “cover member” recited in the claims. A first spring 76 is provided between the spring guide 75 and the suction valve member 74. The first spring 76 biases the suction valve member 74 in the valve closing direction.

The electromagnetic drive unit 81 includes a movable core 84, a needle 86, a needle guide 85, an electromagnet 82, and the like.
The movable core 84 has a cylindrical shape and is provided so as to be movable in the axial direction within the first suction valve body 72. The movable core 84 is fixed to one end of the needle 86. The needle 86 is supported in the first suction valve body 72 so as to be movable in the axial direction by a needle guide 85. The needle 86 can move integrally with the movable core 84, and the other end can abut against the suction valve member 74. The movable core 84 and the needle 86 are movable members of the electromagnetic drive unit 81.

The needle 86 forms an annular stopper portion 861 that protrudes radially outward on the valve seat 78 side with respect to the needle guide 85. The needle 86 is movable toward the fixed core 83 until the stopper portion 861 contacts the needle guide 85.
One end portion of the needle guide 85 on the movable core 84 side forms a first flange portion 852 that protrudes in the radially inward direction. The needle 86 forms a second flange 862 that protrudes radially outward at a position corresponding to the other end of the needle guide 85.

  A second spring 88 is provided between the first flange 852 and the second flange 862. The second spring 88 urges the needle 86 in the valve opening direction (right direction in FIG. 1) with a force stronger than the force by which the first spring 76 urges the suction valve member 74 in the valve closing direction. The needle 86 receives the urging force of the second spring 88 and presses the suction valve member 74 in the valve opening direction.

  The electromagnet 82 includes a fixed core 83, a coil 87, and the like. The fixed core 83 is made of a magnetic material, and is provided on the side opposite to the suction valve member 74 with respect to the movable core 84. The coil 87 is provided in the radially outward direction with respect to the fixed core 83. When the coil 87 is energized, the fixed core 83 is magnetized. The magnetized fixed core 83 attracts the movable core 84 against the urging force of the second spring 88. The needle 86 moves together with the movable core 84 sucked by the fixed core 83. Thereby, the suction valve member 74 is allowed to move toward the valve seat 78. That is, the valve can be closed.

  The magnetic force of the fixed core 83 is lost when the power supply to the coil 87 is stopped. When the magnetic attraction force of the fixed core 83 is lost, the needle 86 moves to the suction valve member 74 by the urging force of the second spring 88. Thereby, the suction valve member 74 is restricted from moving toward the valve seat 78. That is, the valve is opened.

Next, the configuration of the intake valve portion 71 will be described in detail with reference to FIGS.
The valve seat 78 has an inner flow path 781 positioned on the inner side in the radial direction and an outer flow path 782 positioned on the outer side in the radial direction. The inner flow path 781 is provided coaxially with the needle 86. The outer flow path 782 is an arc-shaped hole extending in the circumferential direction. Three outer channels 782 are formed at equal intervals in the circumferential direction. The inner channel 781 and the outer channel 782 function as fuel channels. The inner flow path 781 also functions as an insertion hole for the needle 86.

  The suction valve member 74 has a fitting hole 741 into which one end of the first spring 76 is fitted at the center of the shaft. The fitting hole 741 is a non-through hole. Further, the suction valve member 74 has a plurality of bottomed holes 742 on the side opposite to the valve seat 78. Five bottomed holes 742 are formed at equal intervals in the circumferential direction. Further, the suction valve member 74 has a first flow path 743 that penetrates from the inside of the diameter to the valve seat 78 side in the bottom surface of the bottomed hole 742. The first flow path 743 is located between the inner flow path 781 and the outer flow path 782 in the radial direction. The first flow path 743 functions as a fuel flow path.

  The suction valve member 74 forms a first protrusion 744 that protrudes toward the pressurizing chamber 14 from the first flow path 743 in the radially outward direction with respect to the first flow path 743. The first protrusion 744 functions as a guide unit that guides the fuel from the pressurizing chamber 14 toward the suction valve member 74 to the first flow path 743.

  The spring guide 75 forms a fitting protrusion 753 into which the other end of the first spring 76 is fitted. Further, the spring guide 75 has a third flow path 754 that penetrates in the axial direction in the radially outward direction with respect to the fitting protrusion 753. A plurality of third flow paths 754 are provided at equal intervals in the circumferential direction.

  The first wall 745 of the suction valve member 74 and the second wall 783 of the valve seat 78 facing each other have a flat surface. The first wall 745 of the suction valve member 74 has an annular first pressure equalizing groove 746 that communicates with the first flow path 743 and surrounds the inner flow path 781. The second wall 783 of the valve seat 78 has an annular first pressure equalizing groove 784 that communicates with the first flow path 743 and surrounds the inner flow path 781 both when the valve is opened and when the valve is closed, and an outer flow path 782. An annular second pressure equalizing groove 785 that communicates and surrounds the first flow path 743, the first pressure equalizing groove 746, and the first pressure equalizing groove 784 is provided. The first pressure equalizing groove 746 and the first pressure equalizing groove 784 are formed so as to overlap each other in the radial direction. Further, the second wall 783 of the valve seat 78 has an annular groove 786 at a position facing the outer peripheral portion of the first wall 745 of the suction valve member 74.

  The second wall 783 includes a first seal portion 787, a second seal portion 788, and a third seal portion 789. The first seal portion 787 seals between the inner flow path 781, the first flow path 743, and the first pressure equalizing grooves 746 and 784 when the suction valve member 74 and the valve seat 78 are in contact with each other. When the suction valve member 74 and the valve seat 78 are brought into contact with each other, the second seal portion 788 includes the first flow path 743, the first pressure equalizing groove 746, the first pressure equalizing groove 784, the outer flow path 782, and the second pressure equalizing groove 784. The space between the pressure grooves 785 is sealed. When the suction valve member 74 and the valve seat 78 are brought into contact with each other, the third seal portion 789 has an outer diameter flow path 80 that is located radially outward with respect to the outer flow path 782 and the second pressure equalization groove 785 and the suction valve member 74. Seal between. The intake valve portion 71 is a multi-seat valve having a plurality of seal portions.

Next, the operation of the high pressure pump 1 will be described.
(I) Suction stroke When the plunger 21 descends from the top dead center toward the bottom dead center due to the rotation of the camshaft, the volume of the pressurizing chamber 14 increases and the pressure of the fuel in the pressurizing chamber 14 decreases. . At this time, the discharge passage 95 is blocked by the discharge valve member 94. When energization of the coil 87 is stopped, the needle 86 moves to the suction valve member 74 side by the urging force of the second spring 88. Thereby, the needle 86 presses the suction valve member 74, and the suction valve portion 71 is opened. As a result, fuel is sucked into the pressurizing chamber 14 from the suction chamber 711 via the suction hole 141.

(II) Metering stroke When the plunger 21 rises from the bottom dead center toward the top dead center due to the rotation of the camshaft, the volume of the pressurizing chamber 14 decreases. At that time, energization of the coil 87 is stopped until a predetermined time, and the intake valve portion 71 is opened. For this reason, part of the low-pressure fuel sucked into the pressurizing chamber 14 in the suction stroke returns to the fuel supply side via the suction valve portion 71. At this time, the fuel passes through the first flow path 743, the first pressure equalization groove 746, and the first pressure equalization groove 784 to the inner flow path 781 as shown by the solid arrows in FIG. As indicated by the broken line arrows, the first flow path 743, the first pressure equalizing groove 746 and the path leading to the outer flow path 782 through the first pressure equalizing groove 784 and the suction as shown by the dashed line arrow in FIG. It flows through a passage outside the diameter of the valve member 74 and a path reaching the outer flow path 782 through the second pressure equalizing groove 785.

  At this time, the force due to the pressure of the fuel flowing into the first pressure equalizing groove 746, the first pressure equalizing groove 784, and the second pressure equalizing groove 785 acts on the intake valve member 74 in the valve opening direction. The force in the valve opening direction acts equally on the suction valve member 74 in the circumferential direction, and cancels out the force received by the suction valve member 74 from the flow of fuel in the valve closing direction toward the suction valve member 74.

  Then, a magnetic attractive force is generated between the fixed core 83 and the movable core 84 by energizing the coil 87 at a predetermined time while the plunger 21 is rising. When the magnetic attractive force becomes larger than the resultant force obtained by subtracting the urging force of the first spring 76 from the urging force of the second spring 88, the movable core 84 and the needle 86 move to the fixed core 83 side. As a result, the pressing force of the needle 86 on the suction valve member 74 is released. As a result, the suction valve member 74 comes into contact with the valve seat 78 by the urging force of the first spring 76 and the dynamic pressure generated by the flow of fuel, and the suction valve portion 71 is closed.

(III) Pressurization stroke After the intake valve portion 71 is closed, the volume of the pressurizing chamber 14 decreases as the plunger 21 rises, and the fuel pressure in the pressurizing chamber 14 increases. When the force acting on the discharge valve member 94 due to the fuel pressure in the pressurizing chamber 14 becomes larger than the sum of the biasing force of the discharge valve spring 943 and the force acting on the discharge valve member 94 due to the fuel pressure on the fuel discharge port 99 side, The valve member 94 is opened. Thereby, the pressurized fuel pressurized in the pressurizing chamber 14 is discharged from the fuel discharge port 99 through the discharge hole 142 and the like.
The high-pressure pump 1 repeats the intake stroke, the metering stroke, and the pressurization stroke, measures and pressurizes the sucked fuel, and discharges it from the fuel discharge port 99.

  As described above, in the first embodiment, the valve seat 78 has the inner flow path 781 positioned inside in the radial direction and the outer flow path 782 positioned outside. The suction valve member 74 has a first flow path 743 that penetrates from the bottom surface of the bottomed hole 742 to the valve seat 78 side. The first channel 743 is formed between the inner channel 781 and the outer channel 782 in the radial direction. The first flow path 743, the inner flow path 781, and the outer flow path 782 function as fuel flow paths.

  Therefore, compared with the configuration having only the outer diameter flow path 80, the same flow path area is ensured even if the lift amount L (see FIG. 4) of the intake valve member 74 from the valve seat 78 at the time of valve opening is reduced. can do. Therefore, the lift amount L can be reduced, and the output of the electromagnetic drive unit 81, that is, the attractive force can be reduced. Therefore, the electromagnetic drive unit 81 can be reduced in size by reducing the size of the coil 87 or the like. Further, since the applied current of the coil 87 is reduced, the power consumption is reduced and the operating noise is also reduced. In addition, the drive circuit that controls energization to the coil 87 does not require an expensive element, so that the manufacturing cost is reduced.

  In the first embodiment, the first wall 745 of the suction valve member 74 has an annular first pressure equalizing groove 746 that communicates with the first flow path 743 and surrounds the inner flow path 781. The second wall 783 of the valve seat 78 has an annular first pressure equalizing groove 784 that communicates with the first flow path 743 and surrounds the inner flow path 781 both when the valve is opened and when the valve is closed, and an outer flow path 782. An annular second pressure equalizing groove 785 that communicates and surrounds the first flow path 743, the first pressure equalizing groove 746, and the first pressure equalizing groove 784 is provided. Force due to the pressure of the fuel flowing into the first pressure equalizing groove 746, the first pressure equalizing groove 784, and the second pressure equalizing groove 785 during metering acts on the intake valve member 74 in the valve opening direction. The force in the valve opening direction acts equally on the suction valve member 74 in the circumferential direction, and cancels out the force received by the suction valve member 74 from the flow of fuel in the valve closing direction toward the suction valve member 74.

  Therefore, even if the urging force of the second spring 88 is small, so-called self-closing that closes due to the influence of dynamic pressure generated with the flow of fuel can be suppressed. Therefore, since the attractive force of the electromagnetic drive unit 81 that moves the needle 86 against the urging force of the second spring 88 can be reduced, the electromagnetic drive unit 81 can be further reduced in size.

  In the first embodiment, the first flow path 743 is located on the inner diameter side of the bottom surface of the bottomed hole 742. The suction valve member 74 forms a first protrusion 744 that protrudes closer to the pressurizing chamber 14 than the first flow path 743 outside the first flow path 743. The first protrusion 744 functions as a guide unit that guides fuel from the pressurizing chamber 14 toward the suction valve member 74 to the first flow path 743. The first projecting portion 744 guides the fuel toward the suction valve member 74 to the first flow path 743, so that the acting force due to the dynamic pressure acting on the suction valve member 74 along with the fuel flow can be reduced.

  Therefore, even if the urging force of the second spring 88 is reduced, the valve closing due to the influence of the dynamic pressure can be suppressed. Therefore, since the attractive force of the electromagnetic drive unit 81 that moves the needle 86 against the urging force of the second spring 88 can be reduced, the electromagnetic drive unit 81 can be further reduced in size.

  In the first embodiment, the second wall 783 of the valve seat 78 has an annular groove 786 at a position facing the outer peripheral portion of the first wall 745 of the intake valve member 74. The pressure of the fuel in the annular groove 786 acts on the intake valve member 74 in the valve opening direction. Therefore, the valve closing due to the influence of the dynamic pressure can be further suppressed, and the electromagnetic drive unit 81 can be further downsized.

  In the first embodiment, the first flow paths 743 are formed at equal intervals in the circumferential direction. Therefore, the fuel flowing into the first pressure equalizing groove 746, the first pressure equalizing groove 784, and the second pressure equalizing groove 785 can be made uniform in the circumferential direction.

  In the first embodiment, the first wall 745 and the second wall 783 are formed in parallel and in a plane. Therefore, the sealing performance between the suction valve member 74 and the valve seat 78 can be ensured, and the first seal portion 787, the second seal portion 788, and the third seal portion 789 can be processed at low cost.

(Second Embodiment)
A suction valve portion according to a second embodiment of the present invention will be described with reference to FIG. The first pressure equalizing groove 421 and the second pressure equalizing groove 422 of the suction valve portion 41 are formed in the suction valve member 42. Therefore, the suction valve member 42 is reduced in weight as compared with the first embodiment, so that the suction force of the electromagnetic drive unit can be reduced. Therefore, miniaturization of the electromagnetic drive unit is realized. Further, the processing cost of the second intake valve body 43 can be reduced.

(Third embodiment)
A suction valve portion according to a third embodiment of the present invention will be described with reference to FIG. The inner diameter wall of the first protrusion 451 of the intake valve member 45 of the intake valve portion 44 approaches the first flow path 743 toward the valve seat 78 side. Therefore, the fuel from the pressurizing chamber side toward the first protrusion 451 is guided in the radially inward direction along the radially inner wall of the first protrusion 451. Therefore, the fuel from the pressurizing chamber toward the suction valve member 45 can be smoothly guided to the first flow path 743 during metering.

(Fourth embodiment)
A suction valve member of the suction valve portion according to the fourth embodiment of the present invention will be described with reference to FIG. The suction valve member 46 is formed by laminating a first disk member 461 and a second disk member 462. The intake valve member 46 forms a first protrusion 463. The first protrusion 463 functions as a guide means. The first disk member 461 and the second disk member 462 are formed by, for example, pressing or the like, and then bonded by adhesion, welding, diffusion bonding, or the like. Further, since the second disk member 462 does not contribute to the contact between the seal portions, it may be constituted by a resin mold. Therefore, it is possible to manufacture the suction valve member 46 at a low cost by reducing the cutting process with high processing cost.

(Fifth embodiment)
A suction valve member of a suction valve portion according to a fifth embodiment of the present invention will be described with reference to FIG. The suction valve member 47 is formed by combining a first disk member 471 and a second disk member 472. The intake valve member 47 has a first flow path 473 that functions as a fuel flow path. Further, the suction valve member 47 forms a first protrusion 474 that is annular with respect to the first flow path 473 in the radially outward direction. The first protrusion 474 functions as a guide means. The first disk member 471 and the second disk member 472 are formed by, for example, press working or the like, and then joined by press-fitting, adhesion, welding, diffusion bonding, or the like. Further, since the second disk member 472 does not contribute to the contact between the seal portions, it may be constituted by a resin mold. Therefore, the suction valve member 47 can be manufactured at a low cost by reducing the number of cutting steps with high processing costs as in the fourth embodiment.

(Sixth embodiment)
A suction valve member of the suction valve portion according to the sixth embodiment of the present invention will be described with reference to FIG. The suction valve member 48 is formed by laminating a first disk member 481 and a second disk member 482. The intake valve member 48 has a first flow path 483 that functions as a fuel flow path. In addition, the suction valve member 48 forms a first protrusion 484 radially outward with respect to the first flow path 483. The first protrusion 484 functions as a guide means. The first disk member 481 and the second disk member 482 are formed by, for example, pressing or the like, and then bonded by adhesion, welding, diffusion bonding, or the like. Further, the second disk member 482 does not contribute to the contact between the seal portions, and may be configured by a resin mold. Therefore, like the fourth embodiment, it is possible to reduce the cutting process with high processing cost and to manufacture the suction valve member 48 at a low cost.

(Seventh embodiment)
A suction valve member of the suction valve portion according to the seventh embodiment of the present invention will be described with reference to FIG. The suction valve member 49 is formed by laminating a disc member 491, a first annular member 492, and a second annular member 493. The intake valve member 49 has a first flow path 494 that functions as a fuel flow path. Further, the suction valve member 49 forms a first protrusion 495 in the radially outward direction with respect to the first flow path 494. The first protrusion 495 functions as a guide means. The disc member 491, the first annular member 492, and the second annular member 493 are formed by, for example, pressing or the like, and then joined by adhesion, welding, diffusion bonding, or the like. Further, since the second annular member 492 does not contribute to the contact between the seal portions, it may be configured by a resin mold.

  Therefore, like the fourth embodiment, it is possible to reduce the number of cutting steps with high processing costs and to manufacture the suction valve member 49 at a low cost. Further, the second annular member 492 and the third annular member 493 are simple in shape and easy to manufacture as compared with the second circular member 482 of the sixth embodiment having the same function.

(Eighth embodiment)
An intake valve portion according to an eighth embodiment of the present invention will be described with reference to FIGS. The valve seat 51 of the suction valve unit 50 is formed by laminating a first disk member 511 and a second disk member 512. The first disk member 511 and the second disk member 512 are formed by, for example, pressing or the like, and then bonded by adhesion, welding, diffusion bonding, or the like. Therefore, it is possible to manufacture the valve seat 51 at a low cost by reducing a cutting process with a high processing cost.

(Ninth embodiment)
A suction valve portion according to a ninth embodiment of the present invention will be described with reference to FIG. The suction valve member 53 of the suction valve portion 52 forms an annular pin guide portion 531 that protrudes toward the spring guide 54 side. The spring guide 54 forms an annular pin guide portion 541 that protrudes toward the suction valve member 53. The pin guide parts 531 and 541 are fitted with positioning pins 55 as “guide members”. The suction valve member 53 is restricted from moving in the radial direction by the positioning pin 55 and can move stably in the axial direction.

  The spring guide 54 forms an annular second protrusion 542 that protrudes toward the suction valve member 53 in the radially outward direction with respect to the first flow path 743. The tip of the second protrusion 542 can abut on the first protrusion 744 of the intake valve member 53 when the valve is opened. The second protrusion 542 functions as a restricting means for restricting the movement of the suction valve member 53 to the side opposite to the valve seat 78, and the first flow of fuel from the pressurizing chamber toward the suction valve member 53 during metering. It functions as a guide means for guiding to the path 743.

(10th Embodiment)
An intake valve portion according to a tenth embodiment of the present invention will be described with reference to FIG. The suction valve member 57 of the suction valve portion 56 has the same configuration as the suction valve member 74 of the first embodiment except that the first protrusion 744 is not formed. The spring guide 58 forms an annular second protrusion 581 that protrudes toward the suction valve member 57 in the radially outward direction with respect to the first flow path 743. The second protrusion 581 functions as a restricting means for restricting the movement of the suction valve member 57 to the side opposite to the valve seat 78, and also causes the fuel flowing from the pressurizing chamber to the suction valve member 57 during the metering to flow into the first flow. It functions as a guide means for guiding to the path 743.

(Eleventh embodiment)
An intake valve portion according to an eleventh embodiment of the present invention will be described with reference to FIG. The tip end of the second protrusion 601 formed by the spring guide 60 of the suction valve portion 59 is located in the radially inward direction with respect to the outer flow path 782. Therefore, the tip of the second protrusion 601 is provided at a position approaching the first flow path 743. Therefore, the fuel from the pressurizing chamber toward the suction valve member 61 at the time of metering is smoothly guided to the first flow path 743 by the second protrusion 601.

(Twelfth embodiment)
A suction valve portion according to a twelfth embodiment of the present invention will be described with reference to FIG. The suction valve member 63 of the suction valve portion 62 has a fitting hole 631 for the first spring 65. The spring guide 64 forms a fitting protrusion 641 into which the first spring 65 is fitted. The first spring 65 interposed between the suction valve member 63 and the spring guide 64 is provided so as to surround the first flow path 743 and the third flow path 754. The fuel flowing into the spring guide 64 from the pressurizing chamber through the third flow path 754 during metering is suppressed by the first spring 65 in the radially outward direction. For this reason, the first spring 65 functions as a guide means for guiding the fuel from the pressurizing chamber toward the suction valve member 63 to the first flow path 743.

(Modification of the twelfth embodiment)
A suction valve portion according to a modification of the twelfth embodiment will be described with reference to FIG. The third flow path 671 of the spring guide 67 of the suction valve portion 66 is different from the third flow path 754 of the spring guide 64 of the twelfth embodiment. The third flow path 671 is provided at the axial center of the spring guide 67. The fuel flowing into the spring guide 67 through the third flow path 671 is restrained from flowing radially outward by the first spring 65 as in the twelfth embodiment.

(13th Embodiment)
A suction valve portion according to a thirteenth embodiment of the present invention will be described with reference to FIGS. The intake valve portion 68 has a stopper 69 located on the opposite side of the valve seat 78 with respect to the intake valve member 74. The stopper 69 has a disk shape, contacts the suction valve member 74 when the valve is opened, and restricts the movement of the suction valve member 74 in the valve opening direction. The stopper 69 has a groove 691 extending in the circumferential direction outside the diameter. Three grooves 691 are formed at equal intervals in the circumferential direction and function as a fuel flow path. In the stopper 69, the shaft center portion 692 protrudes on the side opposite to the suction valve member 74. The first spring 76 is provided between the suction valve member 74 and the shaft center portion 692 of the stopper 69. The stopper 69 has a through hole 693 at a position overlapping the first flow path 743 of the suction valve member 74 when viewed in the axial direction. Three through holes 693 are provided at equal intervals in the circumferential direction.

  Fuel from the pressurizing chamber toward the suction valve member 74 during metering flows between the stopper 69 and the suction valve member 74 through the through hole 693. The fuel flowing between the stopper 69 and the intake valve member 74 is prevented from flowing out in the radially outward direction by the first protrusion 744 and the stopper 69, and is guided to the first flow path 743. In the thirteenth embodiment, the stopper 69 and the first protrusion 744 function as guide means for guiding the fuel to the first flow path 743.

(14th Embodiment)
A suction valve portion according to a fourteenth embodiment of the present invention will be described with reference to FIGS. The suction valve unit 25 includes a suction valve member 26 and a stopper 27.
The suction valve member 26 is positioned on the pressurizing chamber 14 side with respect to the valve seat 430 and can be brought into contact with and separated from the valve seat 430. The suction valve member 26 makes the suction chamber 711 and the pressurizing chamber 14 communicate with each other by separating from the valve seat 430, and shuts the suction chamber 711 and the pressurizing chamber 14 by making contact with the valve seat 430.

  The suction valve member 26 forms a protruding portion 261 that protrudes in the radially outward direction so as to restrict the radially outer flow path 262 located in the radially outward direction with respect to the suction valve member 26. Three protrusions 261 are formed at equal intervals in the circumferential direction. The radially outer wall of the projecting portion 261 is slidable on the inner wall of the second suction valve body 73.

  The intake valve member 26 forms a fitting protrusion 263 in which one end of the first spring 76 is fitted at the center of the shaft. Further, the suction valve member 26 has a notch groove 264 that is notched from the radially outer side at a circumferential position corresponding to the radially outer flow path 262 in the wall on the side opposite to the valve seat 430. The notch grooves 264 are formed at equal intervals in the circumferential direction.

  The first wall 265 of the suction valve member 26 that opposes the second wall 783 of the valve seat 78 is located between the inner channel 781 and the outer channel 782 in the radial direction, and has an annular first shape that surrounds the inner channel 781. One equalizing groove 266 is provided.

  The suction valve member 26 has a first flow path 267 that allows the first pressure equalizing groove 266 and the cutout groove 264 to communicate with each other. The first channel 267 is located between the inner channel 781 and the outer channel 782 in the radial direction. The first flow path 267 functions as a fuel flow path and also functions as an inlet for introducing fuel into each pressure equalizing groove.

  The protruding portion 261 functions as a guide unit that suppresses the fuel flowing from the pressurizing chamber 14 toward the suction valve member 26 toward the outer diameter flow path 262 and guides the fuel to the first flow path 267. The fuel that flows from the pressurizing chamber 14 to the suction valve member 26 side flows more easily into the first flow path 267 than the outer diameter flow path 262 constricted by the protruding portion 261.

  The stopper 27 is provided on the pressurizing chamber 14 side with respect to the second suction valve body 73. The stopper 27 forms a flange portion 271 that protrudes radially outward, and the flange portion 271 is fixed by being sandwiched between the second suction valve body 73 and the upper housing 15.

  The stopper 27 has a housing hole 272 that houses the first spring 76 and an annular groove 273 that surrounds the housing hole 272 on the wall facing the suction valve member 26. An inner contact portion 274 that can contact the inside of the diameter of the suction valve member 26 is formed between the accommodation hole 272 and the annular groove 273 in the radial direction. Further, an outer abutting portion 275 that can abut on the outside of the diameter of the suction valve member 26 is formed in the radially outward direction of the annular groove 273. The stopper 27 restricts the movement of the suction valve member 26 to the side opposite to the valve seat 430 when the inner contact portion 274 and the outer contact portion 275 contact the suction valve member 26.

  The stopper 27 has a second flow path 276 that penetrates from the bottom surface of the annular groove 273 toward the suction valve member 26 at a position between the inner contact portion 274 and the outer contact portion 275 in the radial direction. Four second flow paths 276 are formed at equal intervals in the circumferential direction.

  In the fourteenth embodiment, the stopper 27 has an inner contact portion 274 that can contact the inside of the diameter of the suction valve member 26 and an outer contact portion 275 that can contact the outside of the diameter of the suction valve member 26. Therefore, when the suction valve member 26 comes into contact with the stopper 27, the pressing force of the suction valve member 26 acts on the entire stopper 27 without being concentrated only on the inside of the diameter of the stopper 27. Further, the reaction force of the pressing force acts on the entire suction valve member 26 without acting on only the outside of the diameter of the suction valve member 26.

  Therefore, the required strength of the intake valve member 26 and the stopper 27 is reduced, and the size of the intake valve portion 25 can be reduced by configuring the intake valve member 26 and the stopper 27 to be small. Further, since the intake valve member 26 is configured to be lightweight, pump efficiency is improved and generation of vibration and noise is suppressed. Further, the axial deflection of the intake valve member 26 when the valve is opened is suppressed, and the pump efficiency is improved.

  In the fourteenth embodiment, the stopper 27 includes the second flow path 276 at a position between the inner contact portion 274 and the outer contact portion 275 of the stopper 27 in the radial direction. As a result, the fuel from the pressurizing chamber 14 toward the stopper 27 side is guided to the first flow path 267 of the intake valve member 26 via the second flow path 276.

  In the fourteenth embodiment, the first spring 76 is provided in the radially inward direction of the inner contact portion 274 of the stopper 27. Therefore, it is possible to arrange the first spring 76 by effectively utilizing the space in the radial inner direction with respect to the inner contact portion 274 without separately forming a space for accommodating the first spring 76.

(Modification of 14th Embodiment)
A suction valve portion according to a modification of the fourteenth embodiment will be described with reference to FIGS. The stopper 29 of the suction valve portion 28 has a second flow path 291 instead of the annular groove 273 and the second flow path 276 as compared with the stopper 27 of the fourteenth embodiment. Six second flow paths 291 penetrate in the axial direction and are formed at equal intervals in the circumferential direction. The inner diameter of the second channel 291 is larger than the inner diameter of the second channel 276 of the fourteenth embodiment. When the suction valve member 26 comes into contact with the stopper 29, any one or more of the six second flow paths 291 communicate with each other.

  In the modification of the fourteenth embodiment, when the suction valve member 26 abuts against the stopper 29, the fuel can flow through any one or more of the six second flow paths 291 in communication. It is. Further, compared to the embodiment in which the annular groove 273 is formed as in the fourteenth embodiment, the strength of the stopper 29 is high, the shape of the stopper 29 is simple, and the manufacture of the stopper 29 is easy.

(Fifteenth embodiment)
A suction valve portion according to a fifteenth embodiment of the present invention will be described with reference to FIGS. The suction valve unit 16 includes a second suction valve body 17 and a suction valve member 18.
The second intake valve body 17 has a cylindrical outer shell 171 and a valve seat 172 that closes an end of the outer shell 171. The second suction valve body 17 is held between the first suction valve body 72 and the stopper 27. The second intake valve body 17 corresponds to a “valve body” recited in the claims.

  The valve seat 172 includes an inner channel 173 that penetrates in the axial direction at the center in the radial direction and an outer channel 174 that penetrates in the axial direction in the radially outer direction with respect to the inner channel 173. Ten outer channels 174 are formed at equal intervals in the circumferential direction. The inner channel 173 and the outer channel 174 function as fuel channels. The inner flow path 173 also functions as an insertion hole for the needle 86.

  The suction valve member 18 has a plate shape, is positioned on the pressurizing chamber 14 side with respect to the valve seat 172, and can contact and separate from the valve seat 172. The suction valve member 18 communicates with the suction chamber 711 and the pressurization chamber 14 by being separated from the valve seat 172, and shuts off the suction chamber 711 and the pressurization chamber 14 by being in contact with the valve seat 172.

The suction valve member 18 has a first flow path 181 that penetrates in the axial direction at a position between the inner flow path 173 and the outer flow path 174 in the radial direction. Eight first flow paths 181 are formed at equal intervals in the circumferential direction. The first flow path 181 functions as a fuel flow path.
One end of the first spring 76 is locked in the fitting hole 182 in the central portion of the suction valve member 18.

The intake valve member 18 has a protruding portion 183 that protrudes in the radially outward direction so as to restrict the radially outer flow path 19 positioned in the radially outward direction with respect to the intake valve member 18. Three protrusions 183 are formed at equal intervals in the circumferential direction. The radially outer wall of the protrusion 183 is slidable on the inner wall of the second suction valve body 17.
The protrusion 183 functions as a guide unit that suppresses the fuel flowing from the pressurizing chamber 14 toward the suction valve member 18 toward the outer diameter flow path 19 and guides the fuel to the first flow path 181.

  The intake valve member 18 forms a first seal portion 184, a second seal portion 185, and a third seal portion 186 that contact the valve seat 172 when the valve is closed. The first seal portion 184 is located between the inner flow path 173 and the first flow path 181 in the radial direction. The first seal portion 184 seals between the inner flow path 173 and the first flow path 181 when the suction valve member 18 and the valve seat 172 are in contact with each other.

The second seal portion 185 is located between the first flow path 181 and the outer flow path 174 in the radial direction. The second seal portion 185 seals between the first flow path 181 and the outer flow path 174 when the suction valve member 18 and the valve seat 172 are in contact with each other.
The third seal portion 186 is located between the outer channel 174 and the outer channel 19 in the radial direction. The third seal portion 186 seals between the outer flow path 174 and the outer diameter flow path 19 when the suction valve member 18 and the valve seat 172 are in contact with each other.

  In the fifteenth embodiment, the force due to the pressure of the fuel flowing between the valve seat 172 and the intake valve member 18 acts on the seal portions 184, 185, 186 of the intake valve member 18 in the valve opening direction. The force in the valve opening direction acts equally on the suction valve member 18 in the circumferential direction, and cancels the force in the valve closing direction received by the suction valve member 18 by the flow of fuel from the pressurizing chamber 14 toward the suction valve member 18. Can do.

  Therefore, each seal part 184, 185, 186 functions as a sealing unit that seals between the flow paths when the valve is closed, and also functions as a self-closing suppression unit that suppresses the self-closing of the suction valve member 18. . Therefore, even if the urging force of the spring that urges the suction valve member 18 in the valve opening direction is reduced, the self-closing of the suction valve member 18 can be suppressed. Therefore, the electromagnetic drive unit can reduce the maximum output and realize miniaturization.

  In the fifteenth embodiment, eight first flow paths 181 are formed at equal intervals in the circumferential direction. Therefore, the rigidity of the suction valve member 18 can be made uniform in the circumferential direction, and a gap between the suction valve member 18 and the valve seat 172 can be suppressed in the circumferential direction when the valve is closed. Therefore, liquid leakage when the valve is closed can be suppressed, and pump efficiency can be improved.

(Modification of the fifteenth embodiment)
A suction valve portion according to a modification of the fifteenth embodiment will be described with reference to FIGS. The suction valve member 37 of the suction valve portion 36 differs from the suction valve member 18 of the fifteenth embodiment in the first flow path 371 and the protruding portion 372.

  Nine first flow paths 371 are formed at equal intervals in the circumferential direction. Further, three protrusions 372 are formed at equal intervals in the circumferential direction. The modification of 15th Embodiment has the same effect as 15th Embodiment.

(Other embodiments)
In another embodiment of the present invention, the number of first flow paths of the suction valve member may be 7 or less, or 10 or more.
In another embodiment of the present invention, the number of outer flow paths of the valve seat may be 9 or less, or 11 or more.
In another embodiment of the present invention, the first suction valve body and the second suction valve body may be formed of the same member.
In another embodiment of the present invention, the valve device may be applied to, for example, another device of a vehicle, an industrial robot, a machine tool, or the like. Further, the fluid flowing through the flow path opened and closed by the valve device is not limited to fuel, but may be other liquid or gas.

  In another embodiment of the present invention, the valve device may be a normally closed type. Further, the needle and the valve member may be integrally formed. Further, the drive unit is not limited to the electromagnetic type, and other drive types such as an electric type may be employed. The specifications other than the suction valve portion of the high-pressure pump are not limited to those of the above-described embodiment.

  Thus, the present invention is not limited to the above-described embodiments, and can be applied to various forms without departing from the gist thereof.

17, 43, 73 ... second suction valve body (valve body)
173, 781 ... inner flow path 174, 782 ... outer flow path 18, 26, 37, 42, 45, 46, 47, 48, 49, 53, 57, 61, 63, 74 ... suction valve Member (valve member)
181, 267, 371, 473, 483, 494, 743... First flow path 183, 261, 372... Projection (guide means)
184 ... first seal portion 185 ... second seal portion 186 ... third seal portion 265,745 ... first wall 266,421,746,784 ... first pressure equalizing groove 422 785 ... second pressure equalizing groove 451, 463, 474, 484, 495, 744 ... first protrusion (guide means)
51, 78, 172, 430 ... valve seat 542, 581, 601 ... second protrusion (guide means)
65 ... 1st spring (guide means)
69 ... Stopper (guide means)
783 ... Second wall 81 ... Electromagnetic drive unit (drive unit)

Claims (19)

A valve body;
An inner passage positioned in the radially inward direction of the valve body, and a valve seat having an outer passage positioned in the radially outward direction of the valve body;
A valve member provided so as to be able to contact and separate from the valve seat, and having a first flow path positioned between the inner flow path and the outer flow path in a radial direction;
A drive unit capable of regulating movement of the valve member toward the valve seat;
With
The valve member includes an annular first seal portion that seals between the inner flow path and the first flow path when the valve member is in contact with the valve seat, and the first flow path and the outer flow path. Forming an annular second seal portion that seals between, and a third seal portion that seals between the outer flow path and the outer diameter flow path positioned radially outward with respect to the valve member,
It further comprises guide means for suppressing the flow of fluid from the opposite side of the valve seat to the valve member toward the outer diameter flow path and guiding the fluid to the first flow path of the valve member. Characteristic valve device.   The valve device according to claim 1, wherein a plurality of the first flow paths are provided at equal intervals in the circumferential direction. The valve member forms a plurality of projecting portions projecting in the radially outward direction so as to throttle the outside diameter channel so as to throttle the outside diameter channel,
The valve device according to claim 1, wherein the protrusion functions as the guide unit.   An inner contact portion that is located on the opposite side of the valve member from the valve seat and that can contact the inside of the diameter of the valve member and an outer contact portion that can contact the outside of the diameter of the valve member are formed. The valve device according to any one of claims 1 to 3, further comprising a stopper that restricts movement of the valve member to a side opposite to the valve seat.   5. The valve device according to claim 4, wherein the stopper has a second flow path that penetrates in an axial direction at a position between the inner contact portion and the outer contact portion in a radial direction.   6. The valve device according to claim 4, further comprising a spring that is positioned radially inward with respect to the inner contact portion of the stopper and biases the valve member toward the valve seat. The valve member forms a first protrusion protruding outward from the valve seat in a radially outward direction with respect to the first flow path,
The valve device according to claim 1, wherein the first protrusion functions as the guide unit.   The valve device according to claim 7, wherein the radially inner wall of the first protrusion approaches the first flow path toward the valve seat side. A second protrusion that is located on the opposite side of the valve seat with respect to the valve member, has a third flow path that penetrates in the axial direction, and protrudes toward the valve member in a radially outward direction with respect to the first flow path. A cover member for forming
The valve device according to claim 1, wherein the second protrusion functions as the guide unit.   The valve device according to claim 9, wherein the second protrusion functions as a restricting unit that restricts movement of the valve member toward the cover member.   11. The valve device according to claim 9, wherein a tip end of the second protrusion is positioned radially inward with respect to the outer flow path. A spring located between the cover member and the valve member, provided to surround the first flow path and the third flow path, and further biasing the valve member toward the valve seat;
The valve device according to any one of claims 9 to 11, wherein the spring functions as the guide means. A cover member that is located on the opposite side to the valve seat with respect to the valve member and has a third flow path that penetrates in the axial direction;
A spring that is located between the cover member and the valve member, is provided so as to surround the first flow path and the third flow path, and biases the valve member toward the valve seat;
Further comprising
The valve device according to claim 1, wherein the spring functions as the guide unit. One or both of the first wall of the valve member and the second wall of the valve seat facing each other have an annular first pressure equalizing groove that communicates with the first flow path and surrounds the inner flow path. ,
One or both of the first wall and the second wall have an annular second pressure equalizing groove that communicates with the outer flow path and surrounds the first pressure equalizing groove and the first flow path. The valve device according to any one of claims 1 to 13.   The valve device according to claim 14, wherein the first pressure equalizing groove and the second pressure equalizing groove are included in the valve member.   The valve device according to any one of claims 1 to 15, further comprising a guide member that restricts the radial movement of the valve member while allowing the axial movement of the valve member.   The valve device according to any one of claims 1 to 16, wherein the valve member is formed by laminating a plurality of members.   The valve device according to any one of claims 1 to 17, wherein the valve seat is formed by laminating a plurality of members. A plunger,
A cylinder with a bottom, which supports the plunger so as to be capable of reciprocating in the axial direction, and has a pressure chamber whose volume changes when the plunger moves;
The valve device according to any one of claims 1 to 18, wherein when the plunger is lowered, the valve member is opened to supply fuel to the pressurizing chamber, and when the plunger starts to rise or rises. A fuel suction section that closes the valve member in the middle and enables pressurization of fuel in the pressurizing chamber;
A high pressure pump comprising:

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