Valve device and high-pressure pump with this

Abstract

Valve device with: a valve body (43) which has a central axis; a valve seat (430) with an inner passage (781) arranged inside in a radial direction with respect to the central axis of the valve body (43), and outer passages (782) arranged outside in the radial direction; a valve component (26) with a first passage (267) which is provided to be able to come into contact with the valve seat (430) and to be able to move away from it, wherein the first passage (267) is arranged in the radial direction between the inner passage (781) and the outer passages (782); and a drive unit (81) which can prevent movement of the valve component (26) in the direction of the valve seat (430), wherein: the valve component (26) is provided with a first annular sealing section that seals between the inner passage (781) and the first passage (267) at a time of contact with the valve seat (430), a second annular sealing section that seals between the first passage (267) and the outer passages (782), and a third sealing section that seals between the outer passages (782) and a radially outside passage (262) that is arranged on the outer side of the valve component (26) that is radial to the central axis; the valve component (26) is further provided with a guide section to prevent the flow of fluid from a side opposite to the valve seat (430) with respect to the valve component (26) in the direction of the radially outer passage (262) and to guide the fluid to the first passage (267) of the valve component (26), and the valve device is characterized in that the guide section has a plurality of projection sections (261) that project radially outwards with respect to the central axis in order to narrow the radially outer passage (262); the projecting sections (261) that are adjacent to each other in a circumferential direction define the radially outer passage (262) between them; and The outer walls of the projection sections (261) are designed to slide along an inner wall of the valve body (43).

Description

TECHNICAL AREA

[0001] The present invention relates to a valve device that can open and close passages, and a high-pressure pump with this valve device. STATE OF THE ART

[0002] Valve devices are used to block a passage through which a fluid flows. Such valve devices have a valve component that is movable towards and away from a valve seat within a valve body. In this type of valve device, the valve component comes into contact with the valve seat to close the valve, and the valve component moves away from the valve seat to open the valve. The position of the valve component is controlled by a movable component of an actuator. For example, the valve component may be electromagnetically actuated.

[0003] The valve devices comprise a normally open valve, in which the valve is open when an actuator is not operating, and a normally closed valve, in which the valve is closed when an actuator is not operating. In the normally open valve, when an actuator is not operating, a valve component is biased in the valve opening direction by a biasing element to move away from a valve seat. A movable component moves in the valve closing direction against the biasing force of the biasing element to allow the valve component to move toward the valve seat when the actuator is operating.

[0004] In the normally closed design, when an actuator is not in operation, a valve component is pre-tensioned in the valve closing direction by a pre-tensioning component to ensure contact with a valve seat. When the actuator is in operation, a movable component moves in the valve opening direction against the pre-tensioning force of the pre-tensioning component to allow movement of the valve component in the opposite direction to the valve seat.

[0005] The aforementioned valve device is disclosed, for example, in patent documents 1 to 7. A fuel intake valve of a high-pressure pump, disclosed in patent documents 1 and 2, is a normally open valve equipped with an electromagnetic actuator. As a valve component moves away from a valve seat, fuel flows through a passage between a radially outer wall surface of the valve component and an inner wall surface of a valve body. The valve component shown in patent document 1 receives a fuel flow from a pressurization chamber during a metering stroke of the high-pressure pump. At this time, a dynamic pressure is exerted on the valve component, particularly during high-speed operation of the high-pressure pump.Furthermore, in a fuel intake valve shown in patent document 2, a stop is provided on a pressurization chamber to prevent fuel flowing from the pressurization chamber from directly hitting the valve component, thus preventing movement of a valve component in the valve opening direction.

[0006] A fuel intake valve of the high-pressure pump disclosed in patent document 3 is a normally closed valve equipped with an electromagnetic actuator. The fuel intake valve has a movable component at its axial center. An elastic plate component is displaced by the movable component to ensure passage from a pressurization chamber to a fuel channel. Gas valves disclosed in patent documents 4 to 6 are a normally open valve and a normally closed valve, both equipped with an electromagnetic actuator.

[0007] Flow control valves disclosed in patent document 7 comprise a normally closed valve device and a normally open valve device, both equipped with a drive unit formed by a piezoelectric actuator. In the valve devices shown in patent documents 3 to 7, fluid flows through the multiple first passages of the valve component at the time of valve opening. At this time, a dynamic pressure in a valve opening direction, generated by the flow of fluid, is applied to sections that are different from the first passages of the valve component. Patent document 1: JP 2004- 218 633 A Patent document 2: JP 2010- 156 264 A Patent document 3: US 2010 0 242 922 A1 Patent document 4: US 2007 / 0 057 096 A1 Patent document 5: US 7,124,998 B2 Patent document 6: JP 11-311 150 A Patent document 7: JP 2010- 230 159 A

[0008] US 2010 / 0 243 076 A1 discloses a valve device according to the preamble of claim 1. Further valve devices are known from DE 199 08 875 A1 and DE 10 2009 055 003 A1.

[0009] The valve component shown in patent document 1 is not designed to prevent the dynamic pressure generated by the flow of fuel from the pressurization chamber. Therefore, to prevent self-closing (where the valve component is closed by the dynamic pressure), a large preload force may be required to hold the valve component in the opening direction. Consequently, the attractive force of an electromagnet in the actuator unit increases, forcing the movable component to move against the preload force. This results in a disadvantage: the actuator unit has a large size.

[0010] If the stroke of the valve component from the valve seat is too small, the required fluid flow area cannot be guaranteed. Therefore, minimizing the stroke can be difficult. The electromagnet of the actuator unit may need to generate an attractive force greater than the stroke to engage the moving component. This also necessitates a larger actuator unit.

[0011] In the fuel intake valve shown in patent document 2, twisting generated between the valve component and the stop can impair the valve closing response. The twisting force on the valve component can be reduced by forming a connecting hole in the stop. However, if the connecting hole is too large, fuel flows into the stop through the connecting hole. This fuel flow is applied to the valve component in the valve closing direction. Therefore, it is difficult to adequately prevent self-closing of the valve component. Since adjusting or tuning the inner diameter of the connecting hole depends on the kinetic viscosity and flow velocity of the fuel, the adjustment may need to be modified in response to a cam specification and a maximum pump speed required by an operator.

[0012] In the valve devices described in patent documents 3 to 7, the multiple first passages on the valve component are designed to maximize the passage area. As a consequence, the stroke of the valve component from the valve seat can be reduced. However, the actuator unit is enlarged to prevent the valve component from closing automatically. SUMMARY

[0013] It is an object of the present disclosure to provide a valve device in which a drive unit can be made smaller, and a high-pressure pump with this.

[0014] The object of the invention is achieved with a valve device according to claim 1 and a high-pressure pump according to claim 8.

[0015] A valve device of the present disclosure is provided with a valve body having a central axis, a valve seat, a valve component, and an actuating unit. The valve seat has an inner passage located radially inwards with respect to the central axis of the valve body, and outer passages located radially outwards. The valve component can come into contact with and move away from the valve seat and has a first passage located radially between the inner passage and the outer passages.

[0016] A fluid flows through a passage that passes through a radially outside passage, arranged radially outside with respect to the central axis, to the outer passages of the valve seat, a passage that passes through the first passage of the valve component to the outer passages of the valve seat, and a passage that passes through the first passage of the valve component to the inner passage of the valve seat.

[0017] Therefore, compared to a design where a fluid flows only through a radially external passage, the valve device can ensure the same flow area as the design, even if the stroke of the valve component relative to the valve seat is reduced. Consequently, the stroke can be minimized, and the maximum power of the actuator can be reduced. This results in a smaller actuator unit. Furthermore, the reduced stroke also leads to quieter impact noise from the valve component and the moving part.

[0018] The valve component forms a first annular sealing section, a second annular sealing section, and a third annular sealing section. The first sealing section seals between the inner passage and the first passage when the valve component is in contact with the valve seat. The second sealing section seals between the first passage and the outer passages when the valve component is in contact with the valve seat. The third sealing section seals between the outer passages and the radially outer passage when the valve component is in contact with the valve seat.

[0019] The force exerted by the pressure of the fluid flowing between the valve seat and the valve component is applied to each of the sealing sections to open the valve component. The force in the valve opening direction, applied to each of the aforementioned sealing sections, is distributed evenly across the valve component in the circumferential direction and can counteract the force in the valve closing direction received by the valve component from the fluid flow from the opposite side to the valve seat relative to the valve component.

[0020] Therefore, for example, in a normally open valve, even if the preload force of a preloading component used to preload the valve in the valve opening direction is reduced, self-closing of the valve component can be prevented. Consequently, the preload force of the preloading component can be reduced, and the maximum power of the drive unit required to move the movable component against this preload force can be decreased. As a result, the drive unit can be further miniaturized.

[0021] In a normally closed valve assembly, even if the maximum power of an actuator unit that pushes a valve component in the valve opening direction is reduced, self-closing of the valve component can be prevented. Therefore, the maximum power of the actuator unit can be reduced, and a further miniaturization of the actuator unit is achieved.

[0022] A guide section prevents fluid from flowing from the side opposite the valve seat, relative to the valve component, towards the radially outer passage. By preventing flow towards the radially outer passage, the dynamic pressure on the circumferential section of the valve component can be reduced. The guide section directs fluid to the first passage. This means that the application of dynamic pressure to sections other than the first passage of the valve component can be prevented. The fluid directed to the first passage is supplied between the valve seat and the valve component and generates a force that is applied to the valve component in the valve opening direction, as described above. Therefore, the guide section can reduce the maximum power of the actuator and contributes to a further miniaturization of the actuator.

[0023] As described above, reducing the maximum power of the drive unit yields a beneficial effect, resulting in a smaller current draw. Consequently, expensive components for the drive circuit are unnecessary, thus reducing the overall cost of the drive unit. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] The foregoing and other features and advantages of the present disclosure will be evident from the following detailed description, which is made with reference to the accompanying drawings. Fig. 1 is a sectional view of a high-pressure pump according to an embodiment which is not claimed but serves to understand the invention; Fig. 2 is a sectional view along a line II-II of Fig. 1; Fig. 3 is a sectional view along a line III-III of Fig. 1; Fig. Figure 4 is an enlarged sectional view of an intake valve section of the high-pressure pump when the intake valve section is open; Fig. 5A is a view showing a second intake valve body from the perspective of an arrow “Va” in a longitudinal section view of the second intake valve body; Fig. 5B is a longitudinal section view of the second intake valve body; Fig. 5C is a view showing the second intake valve body from the perspective of an arrow “Vc” in the longitudinal section view; Fig. 6A is a view showing the intake valve component from the perspective of arrow “VIb” in a longitudinal section view of the intake valve component; Fig. Figure 6B is a longitudinal section view of the intake valve component; Fig. 6C is a view showing the intake valve component from the perspective of an arrow “VIc” from the longitudinal section view; Fig. Figure 7 is an enlarged sectional view of an enlarged intake valve section of the high-pressure pump when the intake valve section is closed; Fig. Figure 8 shows a flow of fuel from the intake valve section at the time of metering by the high-pressure pump. Fig. 1; Fig. Figure 9 is a sectional view of an intake valve section of a high-pressure pump of a second embodiment, which is not claimed but serves to illustrate the invention; Fig. 10 is a sectional view of an intake valve section of a high-pressure pump of a third embodiment, which is not claimed but serves to understand the invention; Fig. 11A is a view showing an intake valve component from the perspective of an arrow “XIa” of a longitudinal section view of the intake valve component according to a fourth embodiment which is not claimed but serves to illustrate the invention; Fig. 11B is a longitudinal section view of the intake valve component; Fig. 11C is a view showing the intake valve component from the perspective of arrow “XIc” in the longitudinal section view; Fig. 12A is a view showing an intake valve component from the perspective of an arrow “XIIa” of a longitudinal section view of the intake valve component according to a fifth embodiment which is not claimed but serves to illustrate the invention; Fig. Figure 12B is a longitudinal section view of the intake valve component; Fig. 12C is a view showing the intake valve component from the perspective of arrow “XIIc” in the longitudinal section view; Fig. 13A is a view showing an intake valve component from the perspective of an arrow “XIIa” of a longitudinal section view of the intake valve component according to a sixth embodiment which is not claimed but serves to illustrate the invention; Fig. Figure 13B is a longitudinal section view of the intake valve component; Fig. 13C is a view showing the intake valve component from the perspective of arrow “XIIc” in the longitudinal section view; Fig. Figure 14A is a view showing an intake valve component from the perspective of an arrow “XVa” of a longitudinal section view of the intake valve component according to a seventh embodiment, which is not claimed but serves to illustrate the invention; Fig. Figure 14B is a longitudinal section view of the intake valve component; Fig. 14C is a view showing the intake valve component from the perspective of arrow “XIc” in the longitudinal section view; Fig. 15 is a sectional view of an intake valve section of a high-pressure pump of an eighth embodiment, which is not claimed but serves to understand the invention; Fig. Figure 16 is a front view of a first disc component from the perspective of an arrow “Y” in Fig. 15; Fig. Figure 17 is a front view of a second disc component from the perspective of an arrow “Y” in Fig. 15; Fig. Figure 18 is a sectional view of an intake valve section of a high-pressure pump of a ninth embodiment, which is not claimed but serves to understand the invention; Fig. Figure 19 is a sectional view of an intake valve section of a high-pressure pump of a tenth embodiment, which is not claimed but serves to understand the invention; Fig. Figure 20 is a sectional view of an intake valve section of a high-pressure pump of an eleventh embodiment, which is not claimed but serves to understand the invention; Fig. 21 is a sectional view of an intake valve section of a high-pressure pump of a twelfth embodiment, which is not claimed but serves to understand the invention; Fig. 22 is a sectional view of an intake valve section of a high-pressure pump of a modification of the twelfth embodiment, which is not claimed but serves to understand the invention; Fig. Figure 23 is a sectional view of an intake valve section of a high-pressure pump of a thirteenth embodiment, which is not claimed but serves to understand the invention; Fig. 24 is an attack from the perspective of an arrow “XXIV” in Fig. 23; Fig. 25 is a sectional view of an intake valve section of a high-pressure pump of a fourteenth embodiment according to the present invention; Fig. 26A is a view showing a stop from the perspective of an arrow “a” in a longitudinal section view of the stop according to a fourteenth embodiment; Fig. 26B is a longitudinal section view of the stop; Fig. 26C is a view showing the stop from the perspective of an arrow “c” in the longitudinal section view; Fig. 27A is a top view of the intake valve component; Fig. 27B is a sectional view of the intake valve component; Fig. 28 is a sectional view showing an intake valve section of a high-pressure pump according to a modification of the fourteenth embodiment according to the present invention; Fig. 29A is a top view showing a valve component; Fig. 29B is a sectional view along a line “bb” in Fig. 29A; Fig. 30 is a sectional view of an intake valve section of a high-pressure pump according to a fifteenth embodiment, which is not claimed but serves to understand the invention; Fig. Figure 31 is a view of the intake valve component from the perspective of an arrow “XXXI” in Fig. 30; Fig. Figure 32 is a view of the second intake valve body from the perspective of an arrow “XXXII” in Fig. 30; Fig. 33 is a sectional view of an intake valve section of a high-pressure pump according to a modification of a fifteenth embodiment, which is not claimed but serves to illustrate the invention; and Fig. 34 is a view of the intake valve component from the perspective of an arrow “XXXIV” in Fig. 33. DETAILED DESCRIPTION

[0025] Several embodiments are described below with reference to the drawings. Essentially the same components in the embodiments are designated by the same reference numerals, and their descriptions are not repeated. [First embodiment]

[0026] A high-pressure pump of an unclaimed first embodiment is in Fig. Figures 1 to 3 are shown. A high-pressure pump 1 is a fuel pump that pressurizes fuel supplied from a fuel tank (not shown) and delivers this pressurized fuel to a fuel rail. The high-pressure pump 1 is provided with a body section 10, a fuel supply section 30, a piston section 20, a fuel intake section 70, and a fuel discharge relief section 90. The fuel intake section 70 corresponds to a "valve assembly." In the following description, reference is made to the upper side of Fig. 1 is interpreted as "above", "upwards" or "upper" and refers to the lower side of the Fig. 1 is used as a reference to "below", "downwards" or "lower".

[0027] The body section 10 has a lower housing 11, a cylinder 13, and an upper housing 15. The lower housing 11 has a cylindrical cylinder holding section 111, an annular flange section 112 projecting radially outward from the lower section of the cylinder holding section 111, and a cylindrical machine pass section 113 projecting downward from the flange section 112. The inner diameter of the machine pass section 113 is larger than the outer diameter of the cylinder holding section 111. The cylinder holding section 111 has a first press fit hole 121. The flange section 112 has a through hole 114 between the cylinder holding section 111 and the machine pass section 113.

[0028] The cylinder 13 has a cylindrical section 131 that slidably supports a piston 21, a bottom section 136 that covers the upper end of the cylindrical section 131, and an annular projection 135 that extends radially outward below the cylinder holding section 111. The cylinder 13 is press-fitted to the first press-fit hole 121 of the cylinder holding section 111. The projection 135 restricts upward movement of the cylinder 13.

[0029] The cylinder 13 has a pressurization chamber 14, which is defined by the inner wall of the cylindrical section 131, the inner wall of the bottom section 136, and an upper end face 211 of the piston 21. The volumetric capacity of the pressurization chamber 14 changes due to the reciprocating motion of the piston 21. The cylindrical section 131 has an inlet port 141 and an outlet port 142, which are connected to the pressurization chamber 14. The inlet port 141 and the outlet port 142 are arranged symmetrically with respect to the axis of the piston 21.

[0030] The upper housing 15 has a rectangular shape, elongated in the direction between the inlet port 141 and the outlet port 142. The upper housing 15 has a second press fit 151 in its longitudinal center. The cylinder 13 is press-fitted to the second press fit 151 of the upper housing 15.

[0031] The upper housing 15 has an intake passage 152, which is connected to the inlet port 141 of the cylinder 13, and several through-holes 153 that extend through the upper housing 15. Fuel introduced into the pressurization chamber 14 can pass through the intake passage 152. The upper housing 15 has a discharge passage 154, which is connected to the outlet port 142 of the cylinder 13. Fuel discharged from the pressurization chamber 14 can pass through the discharge passage 154.

[0032] The fuel supply section 30 has a cover 31, a pulsation damper 33, and a fuel inlet 35. The cover 31 is cylindrical with a base and comprises a cover base section 311 and a cover cylinder section 312. The cover base section 311 covers the upper end of the cover cylinder section 312. The lower end of the cover cylinder section 312 is in contact with the flange section 112 of the lower housing 11. The cover 31 houses the upper sections of the upper housing 15 and the cylinder 13.

[0033] The cover cylinder section 312 has a first locating hole 325, a second locating hole 326, and a third locating hole 327, which are circumferentially separated from one another. One position of the first locating hole 325 corresponds to the intake passage 152, and one position of the second locating hole 326 corresponds to the discharge passage 154. A first intake valve body 72 is inserted into the first locating hole 325 from outside the cover 31. A first discharge valve body 91 is inserted into the second locating hole 326 from outside the cover 31.

[0034] The cover 31 is joined to the flange section 112 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. A gap between the lower end of the cover 31 and the flange section 112, a gap between the first locating hole 325 and the first intake valve body 72, a gap between the second locating hole 326 and the first discharge valve body 91, and a gap between the third locating hole 327 and the fuel inlet 35 are sealed fluid-tight.

[0035] A fuel channel 32, defined by the cover 31 and the flange section 112, is formed in the cover 31. Fuel supplied from the fuel inlet 35 to the fuel channel 32 is fed into the first intake valve body 72 via the through-hole 153 and the like.

[0036] The pulsation damper 33 is formed in the fuel channel 32. The pulsation damper 33 has two circular, domed diaphragms 331 and 332, the outer edges of which are joined together to encapsulate a gas at a predetermined pressure. The pulsation damper 33 has an outer edge that is sandwiched between an upper support body 341 and a lower support body 342 to be attached to the inner wall of the cover 31. The pulsation damper 33 deforms elastically in response to pressure changes in the fuel in the fuel channel 32, thereby reducing pressure pulsations of the fuel in the fuel channel 32.

[0037] The piston section 20 comprises the piston 21, an oil seal holder 22, a spring seat 23, and a piston spring 24. The piston 21 has a large-diameter section 212 and a small-diameter section 213. The large-diameter section 212 is axially supported by the cylinder 13. The small-diameter section 213 extends downward from the large-diameter section 212 and has a lower end that can bear against, for example, a tappet (not shown). The outer surface of the tappet is in contact with a cam mounted on a camshaft (not shown), and the tappet moves axially back and forth in response to a cam profile as the camshaft rotates.

[0038] The oil seal holder 22 has a mounting section 222, which is attached to the machine pass section 113 of the lower housing 11, and a cylindrical seal holding section 221, which is located below the cylinder 13 to accommodate the small-diameter section 213 of the piston 21. The seal holding section 221 holds a seal 223. The seal 223 has a Teflon ring (registered trademark) on its radial inner surface and an O-ring on its radial outer surface to adjust the thickness of a fuel-oil film around the small-diameter section 213. An oil seal 225 is attached to the lower end of the seal holding section 221. The oil seal 225 adjusts the thickness of an oil film around the small-diameter section 213.

[0039] The spring seat 23 is attached to the lower end of the piston 21. One end of the piston spring 24 engages with the spring seat 23, and the other end engages with the attached section 222 of the oil seal holder 22. The piston spring 24 acts as a return spring for the piston 21, pre-tensioning it. Consequently, the piston 21 rests against the tappet. The piston section 20 moves the piston 21 back and forth in response to a rotation of the camshaft, thus changing the volumetric capacity of the pressurizing chamber 14.

[0040] The fuel discharge relief section 90 comprises a first discharge valve body 91, a second discharge valve body 92, a discharge valve component 94, and a relief valve component 96. The first discharge valve body 91 is cylindrical and attached to the discharge passage 154 of the upper housing 15. The second discharge valve body 92 is integrated within the first discharge valve body 91. The second discharge valve body 92 is cylindrical with a base and is sandwiched between the first discharge valve body 91 and the upper housing 15, with an opening end of the second discharge valve body 92 located on the side of the pressurization chamber 14.

[0041] The base section of the second dispensing valve body 92 has a dispensing passage 95 and a relief passage 97, which are not connected to the dispensing passage 95. The dispensing passage 95 opens radially outward on a wall surface of the base section of the second dispensing valve body 92 from the side of the pressurization chamber 14 and opens at the center of a wall surface of the base section of the second dispensing valve body 92 opposite to the pressurization chamber 14. The relief passage 97 opens at the center of the wall surface of the base section of the second dispensing valve body 92 and opens radially outward on the wall surface of the base section of the second dispensing valve body 92 opposite to the pressurization chamber 14.

[0042] The discharge valve component 94 is arranged opposite the pressurization chamber 14 with respect to the bottom section of the second discharge valve body 92 in order to open and close the discharge passage 95. The discharge valve component 94 is biased in the valve closing direction by a discharge valve spring 943, which is held by a discharge valve spring retainer 945.

[0043] The relief valve component 96 is arranged on the side of the pressurization chamber 14 with respect to the bottom section of the second discharge valve body 92 in order to open and close the relief passage 97. The relief valve component 96 is biased in the valve closing direction by a relief valve spring 963, which is held by a relief valve spring retainer 965.

[0044] The fuel intake section 70 is of a normally open design and has an intake valve section 71 and an electromagnetic actuator unit 81. The fuel intake section 70 corresponds to a "valve assembly." The electromagnetic actuator unit 81 corresponds to an "actuator unit." The intake valve section 71 has a first intake valve body 72, a second intake valve body 73, an intake valve component 74, and a spring guide 75.

[0045] The first intake valve body 72 is cylindrical and attached to the inner wall of the intake passage 152. The first intake valve body 72 has an intake chamber 711 within it. The second intake valve body 73 is provided on the intake chamber 711. The second intake valve body 73 is cylindrical and has a valve seat 78 that defines the interior of the intake chamber 711. The second intake valve body 73 corresponds to a "valve body".

[0046] The intake valve component 74 is disc-shaped, located on the side of the pressurization chamber 14 with respect to the valve seat 78, and can come into contact with and move away from the valve seat 78. The intake valve component 74 moves away from the valve seat 78 to connect the intake chamber 711 to the pressurization chamber 14. The intake valve component 74 rests against the valve seat 78 to shut off the intake chamber 711 from the pressurization chamber 14. The intake valve component 74 corresponds to a "valve component".

[0047] The spring guide 75 has the form of a cylinder with a base and is provided on the side with a pressurization chamber 14 in relation to the second intake valve body 73. The spring guide 75 corresponds to a "cover component". A first spring 76 is provided between the spring guide 75 and the intake valve component 74. The first spring 76 pre-tensions the intake valve component 74 in the valve closing direction.

[0048] The electromagnetic drive unit 81 has a movable core 84, a needle 86, a needle guide 85, and an electromagnet 82. The movable core 84 is cylindrical and designed to be axially movable within the first intake valve body 72. The movable core 84 is attached to one end of the needle 86. The needle 86 is supported by the needle guide 85 to allow axial movement within the first intake valve body 72. The needle 86 is movable together with the movable core 84, and its other end can rest against the intake valve body 72. The movable core 84 and the needle 86 are movable components of the electromagnetic drive unit 81.

[0049] The needle 86 forms an annular stop section 861, which projects radially outward on the side of the valve seat 78 with respect to the needle guide 85. The needle 86 is movable toward the fixed core 83 until the stop section 861 abuts the needle guide 85. One end of the needle guide 85 on the side of the movable core 84 forms a first collar 852, which projects radially inward. The needle 86 forms a second collar 862, which projects radially outward at a position corresponding to the other end of the needle guide 85.

[0050] A second spring 88 is provided between the first collar 852 and the second collar 862. The second spring 88 pre-tensions the needle 86 in the valve opening direction with a greater force than the first spring 86, which pre-tensions the intake valve component 74 in the valve closing direction (to the right). Fig. 1) Preloaded. The needle 86 receives the preload force from the second spring 88 and pushes the intake valve component 74 in the valve opening direction.

[0051] The electromagnet 82 has a fixed core 83, a coil 87, and the like. The fixed core 83 is made of a magnetic material and is positioned opposite the intake valve component 74 with respect to the movable core 84. The coil 87 is located radially outside the movable core 83. The coil 87 is energized to magnetize the fixed core 83. The magnetized fixed core 83 attracts the movable core 84 against the preload force of the second spring 88. The needle 86 moves together with the movable core 84, which is attracted by the fixed core 83. Consequently, the intake valve component 74 is allowed to move towards the valve seat 78, thus enabling the valve to close.

[0052] The magnetic force of the solid core 83 is lost when the coil 87 is no longer energized. The needle 86 moves towards the intake valve component 74 due to the preload force of the second spring 88 when the magnetic attraction of the solid core 83 is lost. Consequently, the intake valve component 74 is prevented from moving towards the valve seat 78. This means that the valve opens.

[0053] Next, a detailed construction of the intake valve section 71 will be described with reference to Fig. 4 to 7 explained.

[0054] The valve seat 78 has an inner passage 781, arranged radially inwards, and outer passages 782, arranged radially outwards. The inner passage 781 is coaxial with the needle 86. The outer passages 782 are curved holes extending circumferentially. Three outer passages 782 are formed at equal intervals in the circumferential direction. The inner passage 781 and the outer passages 782 function as fuel passages. The inner passage 781 also functions as an insertion hole for the needle 86.

[0055] The intake valve component 74 has a locating hole 741 at its axial center for securing one end of the first spring 76. The locating hole 741 is a blind hole. The intake valve component 74 has several holes 742 with bottoms facing away from the valve seat 78. Five holes 742 with bottoms are formed at equal intervals in the circumferential direction. The intake valve component 74 has first passages 743 extending from the radially inner sections of the bottom surfaces of the holes 742 with bottoms to the valve seat 78. The first passages 743 are arranged radially between the inner passage 781 and the outer passages 782. The first passages 743 function as a fuel passage.

[0056] The intake valve component 74 forms a first projecting section 744, which is arranged radially outside the first passages 743. The first projecting section 744 extends towards the pressurization chamber 14 with respect to the first passages 743. The first projecting section 744 functions as a guide section, directing the fuel flowing from the pressurization chamber 14 towards the intake valve component 74 into the first passages 743.

[0057] The spring guide 75 forms a mating section 753 for inserting the other end of the first spring 76. The spring guide 75 has third passages 754 that extend axially through the mating section 753 radially outside. Several third passages 754 are formed at equal intervals in the circumferential direction.

[0058] A first wall 745 of the intake valve component 74 and a second wall 783 of the valve seat 78 face each other and have flat surfaces. The first wall 745 of the intake valve component 74 has an annular first pressure equalization groove 746, which is connected to the first passages 743 and surrounds the inner passage 781. The second wall 783 of the valve seat 78 has: an annular first pressure equalization groove 784, which is connected to the first passages 743 during both valve opening and valve closing, and which surrounds the inner passage 781; and an annular second pressure equalization groove 785, which is connected to the outer passages 782 and surrounds the first passages 743, the first pressure equalization groove 746, and the first pressure equalization groove 784. The first pressure equalization groove 746 and the first pressure equalization groove 784 are designed to overlap radially with each other.The second wall 783 of the valve seat 78 has an annular groove 786 corresponding to the outer circumference of the first wall 745 of the intake valve component 74.

[0059] The second wall 783 has a first sealing section 787, a second sealing section 788, and a third sealing section 789. The first sealing section 787 seals between the inner passage 781 and the first passages 743, the first pressure equalization groove 746, and the first pressure equalization groove 784 when the intake valve component 74 is in contact with the valve seat 78. The second sealing section 788 seals between the first passages 743, the first pressure equalization groove 746, and the first pressure equalization groove 784, and between the outer passages 782 and the second pressure equalization grooves 785 when the intake component 74 is in contact with the valve seat 78. The third sealing section 789 seals between the outer passages 782 and the second pressure equalization groove 785 and a radially outer passage 80, which is arranged radially outside of the intake valve component 74 when the intake valve component 74 is in contact with the valve seat 78.The intake valve section 71 is a multi-blade valve with several sealing sections.

[0060] Next, the operation of high-pressure pump 1 will be explained. (I) Intake stroke

[0061] As the piston 21 moves downwards from top dead center towards bottom dead center, the volumetric capacity of the pressurization chamber 14 increases, and the fuel pressure in the pressurization chamber 14 decreases. At this time, the discharge passage 95 is blocked by the discharge valve component 94. When the energy supply to the coil 87 is stopped, the needle 86 moves towards the second intake valve component 74 by the second spring 88. Consequently, the needle 86 pushes the intake valve component 74 to open the intake valve section 71. As a result, fuel is introduced into the pressurization chamber 14 from the intake chamber 711 via the inlet port 141. (II) Dosing stroke

[0062] As the piston 21 moves upwards from bottom dead center towards top dead center due to the rotation of the camshaft, the volumetric capacity of the pressurization chamber 14 decreases. In this case, the excitation of the coil 87 is stopped until a predetermined time has elapsed, and the intake valve section 71 opens. Therefore, a portion of the low-pressure fuel introduced into the pressurization chamber 14 returns to the fuel supply side via the intake valve section 71 during the intake stroke. At this time, the fuel flows to the inner passage 781 through the first passages 743, the first pressure equalization groove 746, and the first pressure equalization groove 784, as indicated by the continuous arrow in the figure. Fig. As shown in Figure 8, the flow to the outer passages 782 passes through the first passages 743, the first pressure equalization groove 746 and the first pressure equalization groove 784, as indicated by the dotted arrow in Figure 8. Fig. 8 is shown, and flows to the outer passages 782 through a passage radially outside the intake valve component 74 and the second pressure equalization groove 785, as indicated by the dashed arrow in Fig. 8 is shown.

[0063] At this time, force is applied to the intake valve component 74 in the valve opening direction by pressure from the fuel flowing into the first pressure equalization groove 746, the first pressure equalization groove 784, and the second pressure equalization groove 785. The force in the valve opening direction is applied uniformly to the intake valve component 74 in the circumferential direction and balances the force received by the intake valve component 74 from the fuel flow in the direction of valve closing.

[0064] A magnetic attraction is then generated between the fixed core 83 and the movable core 84 by energizing the coil 87 at a predetermined time midway through the upward stroke of the piston 21. When this magnetic attraction exceeds a resultant force, which is the preload force obtained by subtracting the preload force of the first spring 76 from that of the second spring 88, the movable core 84 and the needle 86 move towards the fixed core 83. Consequently, a force is released from the needle 86 to the intake valve component 74. As a result, the intake valve 74, due to the preload force of the first spring 76 and the dynamic pressure generated by the fuel flow, comes into contact with the valve seat 78, thereby closing the intake valve section 71. (III) Pressurization stroke

[0065] After the intake valve section 71 has closed, the volumetric capacity of the pressurization chamber 14 decreases in conjunction with an upward movement of the piston 21, and the fuel pressure in the pressurization chamber 14 increases. When the force exerted on the discharge valve component 94 by the fuel pressure in the pressurization chamber 14 becomes greater than the sum of the preload force of the discharge valve spring 943 and the force exerted on the discharge valve component 94 by the fuel pressure at the side of a fuel outlet 99, the discharge valve component 94 opens. Consequently, the pressurized fuel, which has been pressurized in the pressurization chamber 14, is discharged from the fuel outlet 99 via the outlet port 142.The high-pressure pump 1 repeats the suction stroke, the metering stroke and the pressure stroke, meters and pressurizes the introduced fuel, and discharges the fuel from the fuel outlet 99.

[0066] As explained above, in the first embodiment, the valve seat 78 has the inner passage 781, which is arranged radially inside, and the outer passages 782, which are arranged radially outside. The intake valve component 74 has the first passages 743, which extend from the bottom surface of the holes 742 towards the valve seat 78. The first passages 743 are formed radially between the inner passage 781 and the outer passages 782. The first passages 743, the inner passage 781, and the outer passages 782 function as the fuel passages.

[0067] As a consequence, the same passage area as in the setup with only the radially outer passage 80 can be obtained, even if a stroke amount L (see Fig. 4) The opening of the valve seat 78 of the intake valve component 74 is reduced. Therefore, the stroke L can be reduced, and the power consumption of the electromagnetic drive unit 81, namely the attracting force, can be reduced. Therefore, the electromagnetic drive unit can be made more compact by reducing the size of the coil 87. Furthermore, the power consumption decreases due to the lower current applied to the coil 87, and the operating noise also becomes quieter. Since a drive circuit controlling the excitation of the coil 87 does not require expensive components, the manufacturing costs are reduced.

[0068] In the first embodiment, the first wall 745 of the intake valve component 74 has the annular first pressure equalization groove 746, which is connected to the first passages 743 and surrounds the inner passage 781. The second wall 783 of the valve seat 78 has: the annular first pressure equalization groove 784, which is connected to the first passages 743 and surrounds the inner passage 781 during both valve opening and valve closing; and the annular second pressure equalization groove 785, which is connected to the outer passages 782 and surrounds the first passages 743, the first pressure equalization groove 746, and the first pressure equalization groove 784. The force from the pressure of the fuel flowing into the first pressure equalization groove 746, the first pressure equalization groove 784 and the second pressure equalization groove 785 at the time of metering is applied to the intake valve component 74 in the valve opening direction.The force in the valve opening direction is applied uniformly in the circumferential direction to the intake valve component 74 and compensates for the force received by the intake valve component 74 from the flow of fuel towards the intake valve component 74 in the valve closing direction.

[0069] Therefore, self-closing can be prevented even if the preload force of the second spring 88 is small. Because the attractive force of the electromagnetic drive unit 81, which moves the needle 86 against the preload force of the second spring 88, can be reduced, the electromagnetic drive unit 81 can be made more compact.

[0070] In the first embodiment, the first passages 743 are arranged radially inside the bottom surfaces of the holes 742. The intake valve component 74 forms the first projecting section 744, which projects radially outward from the first passages 743 in the direction of the pressurization chamber 14. The first projecting section 744 acts as a guide, directing the fuel from the pressurization chamber 14 toward the intake valve component 74 and the first passages 743. The first projecting section 744 guides the fuel toward the intake valve component 74 and the first passages 743, thus reducing the force exerted by the dynamic pressure on the intake valve component 74 in conjunction with the fuel flow.

[0071] Therefore, even if the preload force of the second spring 88 is reduced, valve closure due to dynamic pressure may be prevented. Therefore, since the attractive force of the electromagnetic drive unit 81 to move the needle 86 against the preload force of the second spring 88 can be reduced, the electromagnetic drive unit 81 can be made more compact.

[0072] In the first embodiment, the second wall 783 of the valve seat 78 has the annular groove 786 corresponding to the circumferential section of the first wall 745 of the intake valve component 74. The pressure of the fuel in the annular groove 786 is applied to the intake valve component 74 in the valve opening direction. Therefore, since valve closing can be further prevented due to the dynamic pressure, the electromagnetic drive unit 81 can be made more compact.

[0073] In the first embodiment, the first passages 743 are formed at equal intervals in the circumferential direction. Therefore, the fuel flowing into the first pressure equalization groove 746, the first pressure equalization groove 784 and the second pressure equalization groove 785 can be made uniform in the circumferential direction.

[0074] In the first embodiment, the first wall 745 and the second wall 783 are flat and parallel. Therefore, the sealing of the intake valve component 74 and the valve seat 78 can be ensured, and the first sealing section 787, the second sealing section 788 and the third sealing section 789 can be manufactured at low cost. [Second embodiment]

[0075] An intake valve section of the unclaimed second embodiment is described with reference to Fig. Figure 9 explains. A first pressure equalization groove 421 and a second pressure equalization groove 422 of an intake valve section 41 are formed on an intake valve component 42. Because the intake valve component 42 is lighter, the attractive force of the electromagnetic actuator can be reduced. This allows for a miniaturization of the electromagnetic actuator. The manufacturing costs of the second intake valve body 43 can be reduced. [Third embodiment]

[0076] An intake valve section of an unclaimed third embodiment is described with reference to Fig. 10 explained. A radially inner wall of a first projection section 451 of an intake valve component 45 of the intake valve section 44 is closer to the first passages 743 in the direction of the valve seat 78. Therefore, the fuel is introduced from the pressure chamber radially inwards along the radially inner wall of the first projection section 451 towards the first projection section 451. Therefore, the fuel can be guided gently and uniformly from the pressure chamber towards the intake valve component 45 at the time of metering to the first passages 743. [Fourth embodiment]

[0077] An intake valve section of an unclaimed fourth embodiment is described with reference to Fig. 11A, Fig. 11B and Fig. 11C explains. An intake valve component 46 has a first disc component 461 and a second disc component 462, which are laminated together. The intake valve component 46 forms a first projecting section 744. The first projecting section 744 functions as a guide section. The first disc component 461 and the second disc component 462 are formed, for example, by pressing and then joined by gluing, welding, or diffusion bonding. Since the second disc component 462 does not affect the sealing sections, it can be formed by molding from resin. Therefore, the cutting process with high process costs can be reduced, and the intake valve component 46 can be manufactured at low cost. [Fifth embodiment]

[0078] An intake valve component of an intake valve section of the unclaimed fifth embodiment is described with reference to Fig. 12A, Fig. 12B and Fig. Figure 12C explains. An intake valve component 47 has a first disc component 471 and a second disc component 472, which are combined. The intake valve component 47 has a first passage 473, which functions as a passage for fuel. The intake valve component 47 forms a first annular projection section 474 radially outside the first passage 473. The first projection section 474 functions as a guide section. The first disc component 471 and the second disc component 472 are formed, for example, by pressing and then joined by press fitting, gluing, welding, or diffusion bonding. The second disc component 472 can be formed by molding from resin because it does not affect the sealing sections. Therefore, as in the fourth embodiment, the cutting process with high process costs can be reduced, and the intake valve component 47 can be manufactured at low cost. [Sixth embodiment]

[0079] An intake valve component of an intake valve section of the unclaimed sixth embodiment is described with reference to Fig. 13A, Fig. 13B and Fig. Figure 13C explains. An intake valve component 48 has a first disc component 481 and a second disc component 482, which are laminated together. The intake valve component 48 has first passages 483, which function as passages for fuel. The intake valve component 48 forms a first projecting section 484 radially outside the first passages 483. The first projecting section 484 functions as a guide section. The first disc component 481 and the second disc component 482 are formed, for example, by pressing and are then joined by gluing, welding, or diffusion bonding. The second disc component 482 can be formed by molding from resin because it does not affect the sealing sections. Therefore, as in the fourth embodiment, the cutting process with high process costs is reduced, and thus the intake valve component 48 can be manufactured at low manufacturing costs. [Seventh embodiment]

[0080] An intake valve component of an intake valve section of an unclaimed seventh embodiment is described with reference to Fig. 14A, Fig. 14B and Fig. 14C explained.

[0081] An intake valve component 49 has a disc component 491, a first annular component 492, and a second annular component 493, which are laminated together. The intake valve component 49 has first passages 494, which serve as fuel passages. The intake valve component 49 forms a first projecting section 495 radially outside the first passages 494. A first projecting section 495 functions as a guide section. The disc component 491, the first annular component 492, and the second annular component 493 are formed, for example, by pressing and are then joined by gluing, welding, or diffusion bonding. The second annular component 492 can be formed by molding from resin because it does not relate to the sealing sections.

[0082] Therefore, as in the fourth embodiment, the cutting process with high process costs can be reduced, and the intake valve component 49 can be manufactured cost-effectively. The second annular component 492 and the third annular component 493 have simpler shapes and are easier to manufacture. [Eighth embodiment]

[0083] An intake valve section of an unclaimed eighth embodiment is described with reference to Fig. Explained in sections 15 to 17. A valve seat 51 of an intake valve section 50 has a first disc component 511 and a second disc component 512, which are laminated together. The first disc component 511 and the second disc component 512 are formed, for example, by pressing and then joined by gluing, welding, or diffusion bonding. Therefore, the cutting process, which involves high process costs, can be reduced, and the valve seat 51 can be manufactured cost-effectively. [Ninth embodiment]

[0084] An intake valve section of an unclaimed ninth embodiment is described with reference to Fig. Figure 18 explains. An intake valve component 53 of an intake valve section 52 forms an annular pin guide section 531, which projects towards a spring guide 54. The spring guide 54 forms an annular pin guide section 541, which projects towards the intake valve component 53. A positioning pin 55, acting as a "guide section," fits into the pin guide sections 531 and 541. The radial movement of the intake valve component 53 is prevented by the positioning pin 55, allowing it to move stably in the axial direction.

[0085] The spring guide 54 forms a second annular projection section 542, which is radially outside the first passages 743 and projects towards the intake valve component 53. An upper end of the second projection section 542 can abut the first projection section 744 of the intake valve component 53 at the time of valve opening. The second projection section 542 functions as a stop section to prevent the intake valve component 53 from moving in the opposite direction to the valve seat 78 and to guide the fuel from the pressure chamber towards the intake valve component 53 at the time of metering to the first passages 743. [Tenth embodiment]

[0086] An intake valve section of an unclaimed tenth embodiment is described with reference to Fig. 19 explained. An intake valve component 57 of an intake valve section 56 has the same structure as the intake valve component 74 of the first embodiment, except that the intake valve component 57 does not form the first projecting section 744 on it. A spring guide 58 forms a second annular projecting section 581, which is radially outside the first passages 743 and projects towards the intake valve component 57. The second projecting section 581 functions as a guide section to prevent the intake valve component 57 from moving in the opposite direction to the valve seat 78 and to guide the fuel from the pressure chamber towards the intake valve component 47 at the time of metering to the first passages 743. [Eleventh embodiment]

[0087] An intake valve section of an unclaimed eleventh embodiment is described with reference to Fig. 20 explained. An upper end of a second projecting section 601, formed by a spring guide 60 of an intake valve section 59, is arranged radially inside the outer passages 782. Therefore, the upper end of the second projecting section 601 is located near the first passages 743. Therefore, during metering, the fuel is guided gently and uniformly from the pressure chamber towards the intake valve component 61 through the second projecting section 601 to the first passages 743. [Twelfth embodiment]

[0088] An intake valve section of an unclaimed twelfth embodiment is described with reference to Fig. 21 explained. An intake valve component 63 of an intake valve section 62 has a locating hole 631 for a first spring 65. A spring guide 64 forms a locating projection 641 to secure the first spring 65. The first spring 65, located between the intake valve component 63 and the spring guide 64, is designed to surround the first passages 743 and the third passages 754. The fuel flowing from the pressure chamber into the spring guide 64 through the third passages 754 at the time of metering is prevented by the first spring 65 from flowing radially outward. For this reason, the first spring 65 acts as a guide to direct the fuel from the pressure chamber toward the intake valve component 63 and the first passages 743. [Modification of the twelfth embodiment]

[0089] An intake valve section of an unclaimed modification of the twelfth embodiment is described with reference to Fig. 22 explained. A third passage 671 of a spring guide 67 of an intake valve section 66 differs from the third passage 754 of the spring guide 64 of the twelfth embodiment. The third passage 671 is provided in the axial center of the spring guide 67. The flow of fuel, which flows into the spring guide 67 through the third passage 671 in the radial direction, is prevented by the first spring 65 as in the twelfth embodiment. [Thirteenth embodiment]

[0090] An intake valve section of an unclaimed thirteenth embodiment of the present invention is described with reference to Fig. 23 and Fig. 24 explained. An intake valve section 68 has a stop 69, which is arranged opposite the valve seat 78 with respect to the intake valve component 74. The stop 69 is disc-shaped and bears against the intake valve component 74 at the time of valve opening to prevent movement of the intake valve component 74 in the valve opening direction. The stop 69 has grooves 691 that extend circumferentially along its radial outer surface. Three grooves 691 are formed at equal intervals in the circumferential direction and function as passages for fuel. The stop 69 has an axial central section 692 that projects opposite the intake valve component 74. A first spring 76 is provided between the intake valve component 74 and the axial central section 692 of the stop 69. The stop 69 has through holes 693 in positions which, from an axial point of view, overlap with the first through holes 743 of the intake valve component 74.Three through holes 693 are formed at equal intervals in the circumferential direction.

[0091] The fuel from the pressure chamber towards the intake valve component 74 at the time of metering flows between the stop 69 and the intake valve component 74 through the through-holes 693. The fuel flowing between the stop 69 and the intake valve component 74 is prevented from flowing radially outwards through the first projecting section 744 and the stop 69 and is guided to the first passages 743. In the thirteenth embodiment, the stop 69 and the first projecting section 744 function as a guide section to direct the fuel to the first passages 743. [Fourteenth embodiment]

[0092] An intake valve section of a fourteenth embodiment according to the present invention is described with reference to Fig. Sections 25 to 27B are explained. An intake valve section 25 has an intake valve component 26 and a stop 27. The intake valve component 26 is located on the side of the pressurization chamber 14 with respect to a valve seat 430 and can come into contact with and move away from the valve seat 430. The intake valve component 26 moves away from the valve seat 430 to connect the intake chamber 711 to the pressurization chamber 14 and comes into contact with the valve seat 430 to shut off the intake chamber 711 from the pressurization chamber 14.

[0093] The intake valve component 26 forms projecting sections 261 that extend radially outwards to narrow a radially outer passage 262, which is located radially outside the intake valve component 26. Three projecting sections 261 are formed at equal intervals in the circumferential direction. The radially outer walls of the projecting sections 261 are slidable on the inner wall of the second intake valve body 73.

[0094] The intake valve component 26 forms a fitting projection 263 at its axial center to secure one end of the first spring 76. The intake valve component 26 has, on its wall opposite the valve seat 430, grooves 264 which are cut radially outwards at circumferential points corresponding to the radially outer passage 262. The grooves 264 are formed at equal intervals in the circumferential direction.

[0095] A first wall 265 of the intake valve component 26, which faces a second wall 783 of the valve seat 78, is arranged in the radial direction between the inner passage 781 and the outer passages 782 and has an annular first pressure equalization groove 266 that surrounds the inner passage 781.

[0096] The intake valve component 26 has a first passage 267 that connects the first pressure equalization groove 266 and the notched grooves 264. The first passage 267 is arranged radially between the inner passage 781 and the outer passages 782. The first passage 267 functions as a fuel passage and an inlet port, introducing fuel to each pressure equalization groove.

[0097] The projecting sections 261 prevent the flow of fuel from the pressurization chamber 14 towards the intake valve component 26 from flowing towards the radially outer passage 262 and act as a guide section to direct the fuel to the first passage 267. The fuel flowing from the pressurization chamber 14 towards the intake valve component 26 can flow more easily to the first passage 267 than to the radially outer passage 262, which is constricted by the projecting sections 261.

[0098] The stop 27 is formed on the side of the pressurization chamber 14 with respect to the second intake valve body 73. The stop 27 forms a collar 271 that projects radially outwards and is secured by clamping the flange 271 between the second intake valve body 73 and the upper housing 15.

[0099] The stop 27 has a receiving hole 272 on its wall facing the intake valve component 26, which receives the first spring 76, and has an annular groove 273 that is ring-shaped to surround the receiving hole 272. An inner contact section 274, which can bear against the radially inner section of the intake valve component 26, is formed between the receiving hole 272 and the annular groove 273 in the radial direction. An outer contact section 275, which can bear against the radially outer section of the intake valve component 26, is arranged radially outside the annular groove 273. The stop 27 prevents the intake valve component 26 from moving in the opposite direction towards the valve seat 430 when the inner contact section 274 and the outer contact section 275 are in contact with the intake valve component 26.

[0100] The stop 27 has second passages 276 that extend radially from the bottom surface of the annular groove 273 towards the intake valve component 26, between the inner mounting section 274 and the outer mounting section 275. Four second passages 276 are formed at equal intervals in the circumferential direction.

[0101] In the fourteenth embodiment, the stop 27 has the inner contact section 274, which can bear against the radially inner section of the intake valve component 26, and the outer contact section 275, which can bear against the radially outer section of the intake valve component 26. Therefore, when the intake valve component 26 bears against the stop 27, the pressure force of the intake valve component 26 is applied via the stop 27 without being concentrated solely on the radially inner section of the stop 27. A counterforce to the aforementioned pressure is applied via the intake valve component 26 without being concentrated solely on the radially outer section of the intake valve component 26.

[0102] Therefore, the required mechanical strengths of the intake valve component 26 and the stop 27 are lowered, allowing the intake valve component 26 and the stop 27 to be made smaller, and the body of the intake valve section 25 to be made smaller. The intake valve component 26 is lightweight, thus improving pump efficiency and suppressing vibration and noise. Axial out-of-roundness of the intake valve component 26 at the time of valve opening is prevented, and pump efficiency is further improved.

[0103] In the fourteenth embodiment, the stop 27 has the second passages 276 between the inner contact section 274 and the outer contact section 275 of the stop 27 in the radial direction. Accordingly, the fuel is guided from the pressurization chamber 14 towards the stop 27 and the first passage 267 of the intake valve component 26 via the second passages 276.

[0104] In the fourteenth embodiment, the first spring 76 is provided radially inside the inner contact section 274 of the stop 27. Therefore, without forming a space to separately accommodate the first spring 76, the space radially inside the inner contact section 274 is effectively utilized so that the first spring 76 can be positioned. [Modification of the fourteenth embodiment]

[0105] An intake valve section of a modification of a fourteenth embodiment according to the invention is described with reference to Fig. 28 and Fig. 29 explained. In comparison to the stop 27 of the fourteenth embodiment, the stop 29 of the intake valve section 28 has second passages 291 instead of the annular groove 273 and the second passage 276. Six second passages 291 extend axially and are formed at equal intervals in the circumferential direction. One inner diameter of the second passage 291 is larger than one inner diameter of the second passage 276 of the fourteenth embodiment. When the intake valve component 26 rests against the stop 29, one or more of the six second passages 291 are connected to each other.

[0106] In the modification of the fourteenth embodiment, when the intake valve component 26 rests against the stop 29, the fuel can be interconnected through one or more of the six secondary passages 291. Compared to the case where the annular groove 273 is formed, as in the fourteenth embodiment, the mechanical strength of the stop 29 is higher and its manufacture is easier due to its simpler shape. [Fifteenth embodiment]

[0107] An intake valve section of an unclaimed fifteenth embodiment is described with reference to Fig. Explained in sections 30 to 32. An intake valve section 16 has a second intake valve body 17 and an intake valve component 18. The second intake valve body 17 has a cylindrical outer rim 171 and a valve seat 172 that fills the end of the outer rim 171. The second intake valve body 17 is clamped by the first intake valve body 72 and the stop 27. The second intake valve body 17 corresponds to a "valve body".

[0108] A valve seat 172 has an inner passage 173 extending axially through its radial center, and outer passages 174 extending axially radially outside the inner passage 173. Ten outer passages 174 are formed at equal intervals in the circumferential direction. The inner passage 173 and the outer passages 174 function as fuel passages. The inner passage 173 also functions as an insertion hole for the needle 86.

[0109] The intake valve component 18 is plate-shaped, is arranged on the side of the pressurization chamber 14 with respect to the valve seat 172, and can come into contact with and move away from the valve seat 172. The intake valve component 18 moves away from the valve seat 172 to connect the intake chamber 711 and the pressurization chamber 14, and comes into contact with the valve seat 172 to shut off the intake chamber 711 from the pressurization chamber 14.

[0110] The intake valve component 18 has first passages 181 that extend axially in the radial direction between the inner passage 173 and the outer passages 174. Eight first passages 181 are formed at equal intervals in the circumferential direction. The first passages 181 function as fuel passages. One end of the first spring 76 engages with a locating hole 182 in the axial central section of the intake valve component 18.

[0111] The intake valve component 18 forms projecting sections 183 that extend radially outward to constrict a radially outer passage 19 located radially outside the intake valve component 18. Four projecting sections 183 are formed at equal intervals in the circumferential direction. Radially outer walls of the projecting sections 183 can slide on the inner wall of the second intake valve body 17. The projecting sections 183 prevent the fuel flowing from the pressurization chamber 14 toward the intake valve component 18 from flowing toward the radially outer passage 19 and act as a guide section to direct the fuel to the first passage 181.

[0112] The intake valve component 18 forms a first sealing section 184, a second sealing section 185, and a third sealing section 186, which bear against the valve seat 172 at the time of valve closure. The first sealing section 184 is arranged radially between the inner passage 173 and the first passages 181. The first sealing section 184 seals between the inner passage 173 and the first passages 181 when the intake valve component 18 bears against the valve seat 172.

[0113] The second sealing section 185 is arranged radially between the first passages 181 and the outer passages 174. The second sealing section 185 seals between the first passages 181 and the outer passages 174 when the intake valve component 18 is in contact with the valve seat 172. The third sealing section 186 is arranged radially between the outer passages 174 and the radially outer passage 19. The third sealing section 186 seals between the outer passages 174 and the radially outer passage 19 when the intake valve component 18 is in contact with the valve seat 172.

[0114] In the fifteenth embodiment, a force is applied to the sealing sections 184, 185, and 186 of the intake valve component 18 in the valve opening direction by the pressure of the fuel flowing between the valve seat 172 and the intake valve component 18. The force in the valve opening direction is applied uniformly to the intake valve component 18 in the circumferential direction and can compensate for the force in the valve closing direction, which is received by the intake valve component 18 due to the flow from the pressurization chamber 14 towards the intake valve component 18.

[0115] Therefore, while each of the sealing sections 184, 185, and 186 functions as a sealing section to seal between each passage at the time of valve closure, it also functions as a self-closing prevention section to prevent the intake valve component 18 from closing on its own. Therefore, even if the preload force of the spring that biases the intake valve component 18 in the valve opening direction is small, self-closing of the intake valve component 18 can be prevented. Therefore, the maximum power of the electromagnetic actuator can be reduced, and the miniaturization is achieved.

[0116] In the fifteenth embodiment, eight first passages 181 are formed at equal intervals in the circumferential direction. Therefore, the stiffness of the intake valve component 18 can be made uniform in the circumferential direction, and the clearance between the intake valve component 18 and the valve seat 172 can be prevented in the circumferential direction at the time of valve closure. Therefore, fluid escape at the time of valve closure can be prevented, and the pump efficiency can be improved. [Modification of the fifteenth embodiment]

[0117] An intake valve section of an unclaimed modification of the fifteenth embodiment is described with reference to Fig. 33 and Fig. 34 explained. An intake valve component 37 of an intake valve section 36 differs in first passages 371 and projection sections 372 from the intake valve component 18 of the fifteenth embodiment.

[0118] Nine first passages 371 are formed at equal intervals in the circumferential direction. Three projecting sections 372 are formed at equal intervals in the circumferential direction. The modification of the fifteenth embodiment has the same advantageous effect as the fifteenth embodiment. [Other embodiment]

[0119] In a further embodiment of the present invention, the number of first passages of the intake valve component can be seven or fewer, or ten or more. The number of outer passages of the valve seat can be nine or fewer, or eleven or more. The first intake valve body and the second intake valve body can be formed integrally from the same component. The valve device can be applied, for example, to other devices of vehicles or industrial robots, machine tools, and the like. The fluid flowing through the passages opened and closed by the valve device need not be limited to fuel; other liquids and gases can also be used.

[0120] The valve assembly can be a normally closed valve. The needle and valve component can be integrated. The actuator can be of an electromagnetic design, or an electromechanical design can be used. The specifications of components other than the intake valve section of the high-pressure pump are not limited to those of the embodiments described above.

[0121] The invention is not limited to the aforementioned embodiments and can be implemented in various forms without deviating from the subject matter as defined in the claims.

Claims

[1] Valve device with: a valve body (43) having a central axis; a valve seat (430) having an inner passage (781) arranged inside in a radial direction with respect to the central axis of the valve body (43) and outer passages (782) arranged outside in the radial direction; a valve member (26) having a first passage (267) adapted to engage and move away from the valve seat (430), the first passage (267) being disposed radially between the inner passage (781) and the outer passages (782); and a drive unit (81) which can prevent movement of the valve component (26) towards the valve seat (430), wherein: the valve component (26) is provided with a first annular sealing portion that seals between the inner passage (781) and the first passage (267) at a time of abutment against the valve seat (430), a second annular sealing portion that seals between the first passage (267) and the outer passages (782), and a third sealing portion that seals between the outer passages (782) and a radially outer passage (262) arranged on the radially outer side of the valve component (26) with respect to the central axis; the valve component (26) is further provided with a guide portion for preventing a flow of fluid flowing from an opposite side to the valve seat (430) with respect to the valve component (26) towards the radially outer passage (262) and for guiding the fluid to the first passage (267) of the valve component (26), and the valve devicecharacterized by is that the guide portion has a plurality of projection portions (261) projecting radially outwardly with respect to the central axis to narrow the radially outer passage (262); the projection portions (261) which are adjacent to each other in a circumferential direction define the radially outer passage (262) therebetween; and Outer walls of the projection portions (261) are designed to slide on an inner wall of the valve body (43). [2] The valve device according to claim 1, wherein a plurality of said first passages (267) are provided in a circumferential direction. [3] Valve device according to claim 1 or 2, further comprising a stop (27, 29) which is arranged opposite the valve seat (430) with respect to the valve component (26), which stop forms an inner abutment portion (274) for abutting against a portion of the valve component (26) which is radially inner with respect to the central axis, and an outer abutment portion (275) for abutting against a portion of the valve component (26) which is radially outer with respect to the central axis, and which prevents movement of the valve component (26) opposite to the valve seat (430). [4] A valve device according to claim 3, wherein the stop (27, 29) has a second passage (276) passing in the radial direction between the inner abutment portion (274) and the outer abutment portion (275) axially with respect to the central axis. [5] Valve device according to claim 3 or 4, further comprising a spring (76) arranged radially inward of the inner abutment portion (274) of the stop (27, 29) with respect to the central axis for biasing the valve member (26) toward the valve seat (430). [6] Valve device according to one of claims 1 to 5, wherein one or both of a first wall (265) of the valve member (26) and a second wall (783) of the valve seat (430) facing each other has / have an annular first pressure equalization groove (266) connected to the first passage (267) and surrounding the inner passage (781), and one or both of the first wall (265) and the second wall (783) has / have an annular second pressure equalization groove connected to the outer passages (782) and surrounding the first pressure equalization groove (266) and the first passage (267). [7] The valve device according to claim 6, wherein the valve member (26) has the first pressure equalizing groove (266) and the second pressure equalizing groove. [8] High pressure pump with: a piston (21); a cylinder (13) having a bottomed cylinder shape which supports the piston (21) reciprocally in an axial direction of the cylinder (13), and which has a pressure chamber whose volumetric capacity changes as the piston (21) moves; and a fuel intake section having the valve device according to any one of claims 1 to 7, which opens the valve member (26) when the piston (21) moves downwards to supply fuel to the pressure chamber, and which closes the valve member (26) when the piston (21) starts an upward movement or is in the upward movement to be able to pressurize fuel in the pressure chamber.

Images