WO2016113824A1

WO2016113824A1 - High-pressure pump

Info

Publication number: WO2016113824A1
Application number: PCT/JP2015/006430
Authority: WO
Inventors: 振一郎越本; 宮本　裕
Original assignee: 株式会社デンソー
Priority date: 2015-01-16
Filing date: 2015-12-24
Publication date: 2016-07-21
Also published as: JP2016133010A

Abstract

A high-pressure pump equipped with: an upper housing (15) for forming an intake channel connected to a compression chamber having a cylinder; a valve seat (43) having a seat surface (432) and a connecting channel (431) for connecting the compression-chamber side and the side opposite the compression chamber with one another, and provided in the intake channel of the upper housing; an intake valve member (44) for blocking the flow of fuel between the connecting channel (431) and the compression chamber by contacting the seat surface (432), and allowing the flow of fuel between the connecting channel (431) and the compression chamber by separating from the seat surface (432); a floor-equipped cylindrical member (45) provided on the compression-chamber side of the valve seat (43); a spring (49) capable of biasing the intake-valve member (44) toward the valve-seat (43) side, and provided between the floor-equipped cylindrical member (45) and the intake valve member (44); and the like. The floor-equipped cylindrical member (45) is formed separately from the valve seat (43), has a sliding part (46) capable of sliding along the outer-edge section (443) of the intake-valve member (44), and guides the movement of the intake-valve member (44).

Description

High pressure pump

Cross-reference of related applications

This application is based on Japanese Patent Application No. 2015-6749 filed on January 16, 2015, and the contents thereof are disclosed in this specification.

This disclosure relates to a high pressure pump.

Conventionally, a high-pressure pump that is provided in a fuel supply system that supplies fuel to an internal combustion engine and pressurizes the fuel is known. The low-pressure fuel pumped from the fuel tank and supplied to the high-pressure pump is sucked into the pressurizing chamber when the plunger of the high-pressure pump is lowered, and is metered and pressurized when the plunger is raised. The high-pressure pump returns a part of the fuel sucked into the pressurizing chamber to the fuel supply side when the plunger moves up. As a result, the amount of fuel pressurized and fed from the high pressure pump to the internal combustion engine is adjusted. For example, in Patent Document 1, fuel is supplied to the pressurizing chamber by opening the valve when the plunger descends, and the pressurizing chamber is closed by closing the valve when the plunger starts to rise or during the ascent. A high-pressure pump is described that includes a fuel supply that allows the fuel to be pressurized.

In the high-pressure pump, a multi-seat type valve having a plurality of seat surfaces in the valve seat may be used for the fuel supply unit in order to supply a sufficient amount of fuel to the pressurizing chamber. When the multi-seat type valve shuts off the pressurizing chamber side of the valve seat and the side opposite to the pressurizing chamber of the valve seat, the valve member needs to reliably contact each of a plurality of seat surfaces of the valve seat. . However, since there are many fuel leakage paths, when the fuel pressure becomes high, the discharge efficiency during low-speed operation decreases due to a decrease in sealing performance under high pressure. Therefore, in order to improve the sealing performance under high pressure, the rigidity of the valve seat is increased to make it difficult to deform the valve seat, while the rigidity of the valve member is lowered to easily deform the valve member along a plurality of seat surfaces. It is effective to do so.

In the fuel supply unit provided in the high-pressure pump described in Patent Document 1, a guide unit that guides the reciprocating movement of the valve member is provided integrally with the valve seat on the pressurizing chamber side of the valve seat. Since the guide portion is formed relatively thin due to restrictions on the physique of the high-pressure pump, the guide portion may be deformed when the fuel on the pressure chamber side of the valve seat becomes high pressure. When the guide portion is deformed, the valve seat body having a plurality of seal surfaces is deformed, so that a problem occurs in the contact between the valve member and the valve seat, and the sealing performance is deteriorated. For this reason, the discharge efficiency of the fuel in the high-pressure pump may be reduced.

Patent 5370792 specification (corresponding to US2012 / 0288389A1)

An object of the present disclosure is to provide a high-pressure pump that improves fuel discharge efficiency.

The present disclosure is a high-pressure pump including a plunger that can reciprocate, a cylinder that has a pressurizing chamber that supports the plunger so that the plunger can reciprocate and changes its volume when the plunger moves, and a communication path that communicates with the pressurizing chamber. A passage forming member to be formed, a plurality of fuel passages that are provided in the communication passage and communicate with the pressurizing chamber side and the opposite side of the pressurizing chamber, and fuel flows to the pressurizing chamber; A valve seat having a plurality of valve seat surfaces formed around the opening, and provided so as to be able to abut against the valve seat surface and shut off the flow of fuel between the fuel passage and the pressurizing chamber when abutting against the valve seat surface A valve member that allows fuel flow between the fuel passage and the pressurizing chamber when separated from the valve seat surface, and a sliding portion that is provided on the pressurizing chamber side of the valve seat and that can slide on the outer edge of the valve member And a guide member provided between the guide member and the valve member and capable of biasing the valve member toward the valve seat side. Comprising a member, a fuel discharge portion for discharging the pressurized fuel to the outside pressure chamber, the.

The high-pressure pump of the present disclosure is characterized in that the guide member is formed separately from the valve seat.

In the high pressure pump of the present disclosure, the guide member is formed separately from the valve seat. Thereby, the rigidity of the valve seat can be increased and the deformation can be made difficult by removing from the valve seat a portion that is easily deformed when the fuel becomes high pressure. Therefore, the high-pressure pump of the present disclosure can improve the sealing performance between the valve member and the valve seat when the valve member and the valve seat come into contact with each other, and can improve the fuel discharge efficiency.

FIG. 1 is a cross-sectional view of a high-pressure pump according to a first embodiment of the present disclosure. 2 is a cross-sectional view taken along line II-II in FIG. 3 is a cross-sectional view taken along line III-III in FIG. FIG. 4 is an enlarged cross-sectional view of a portion IV in FIG. FIG. 5A is a plan view of a valve seat included in the suction valve portion of the high-pressure pump according to the first embodiment of the present disclosure, and FIG. 5B is a cross-sectional view taken along the line Vb-Vb in FIG. FIG. 6A is a plan view of the suction valve member included in the suction valve portion of the high-pressure pump according to the first embodiment of the present disclosure, and FIG. 6B is a cross-sectional view taken along line VIb-VIb in FIG. It is sectional drawing. FIG. 7A is a plan view of a bottomed cylindrical member included in the suction valve portion of the high-pressure pump according to the first embodiment of the present disclosure, and the suction valve member accommodated in the bottomed cylindrical member. FIG. 7B is a cross-sectional view taken along the line VIIb-VIIb in FIG. 7A. FIG. 8 is an enlarged cross-sectional view of the suction valve portion of the high-pressure pump according to the second embodiment of the present disclosure. FIG. 9A is a plan view of an intake valve member included in the intake valve portion of the high-pressure pump according to the second embodiment of the present disclosure, and FIG. 9B is a cross-sectional view taken along line IXb-IXb in FIG. FIG. FIG. 10A is a plan view of a bottomed cylindrical member included in the suction valve portion of the high-pressure pump according to the second embodiment of the present disclosure, and the suction valve member accommodated in the bottomed cylindrical member. FIG. 10B shows a positional relationship, and FIG. 10B is a cross-sectional view taken along line Xb-Xb in FIG.

Hereinafter, a plurality of embodiments of the present disclosure will be described with reference to the drawings.

(First embodiment)
A high-pressure pump according to a first embodiment of the present disclosure is shown in FIGS. 1 to 7 (b). 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 part 10, a fuel storage part 30, a plunger part 20, a fuel suction part 38, and a fuel discharge relief part 60 as a “fuel discharge part”. In the following description, the upper part of FIGS. 1 and 2 is described as “upper”, and the lower part of FIGS.

The main body 10 includes a lower housing 11, a cylinder 13, and an upper housing 15 as a “passage forming member”.

The lower housing 11 includes a cylindrical cylinder holding part 111, an annular flange part 112 protruding radially outward from a lower part of the cylinder holding part 111, a cylindrical engine fitting part 113 protruding downward from the flange part 112, and the like.

The cylinder holding part 111 has a press-fitting hole 114. A cylinder 13 described later is press-fitted and fixed in the press-fitting hole 114. The flange portion 112 has a communication hole 115 at a position between the cylinder holding portion 111 and the engine fitting portion 113. The communication hole 115 communicates the space inside the engine fitting portion 113 and the space above the flange portion 112.

The cylinder 13 includes a cylindrical portion 131 that slidably supports the plunger 21, a bottom portion 132 that closes the upper end of the cylindrical portion 131, an annular protrusion 133 that protrudes radially outward below the cylinder holding portion 111, and the like. The protrusion 133 engages with the flange portion 112 and restricts the upward movement of the cylinder 13.

The cylinder 13 has a pressurizing chamber 14 in which an inner wall of the cylindrical portion 131, an inner wall of the bottom portion 132, and an 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 cylinder 13 has a suction hole 141 and a discharge hole 142 at symmetrical positions with respect to the central axis of the plunger 21.

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

The upper housing 15 is connected to a suction passage 152 as a “communication passage” communicating with the suction hole 141 of the cylinder 13, a plurality of communication passages 153 communicating the suction passage 152 and the outside of the upper housing 15, and a discharge hole 142 of the cylinder 13. It has a discharge passage 154 that communicates. The fuel sucked by the pressurizing chamber 14 can flow through the suction passage 152. The fuel discharged from the pressurizing chamber 14 can flow through the discharge passage 154.

The plunger portion 20 includes a plunger 21, an oil seal holder 22, a spring seat 23, and a plunger spring 24. The plunger unit 20 pressurizes the fuel in the pressurizing chamber 14 whose volume changes due to reciprocation.

The plunger 21 has a large diameter part 212 and a small diameter part 213. The large-diameter portion 212 is accommodated in the cylinder 13 so as to be slidable with the inner wall of the cylindrical portion 131. The small-diameter portion 213 extends downward from the large-diameter portion 212, and the lower end can be in contact with a tappet (not shown). The tappet makes the outer surface contact 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 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, a fixing portion 222 that is fixed to the engine fitting portion 113, and the like. The seal holding part 221 holds the seal 223. The seal 223 includes a radially inner Teflon (registered trademark) ring and a radially outer O-ring, and adjusts the thickness of the fuel oil film around the small diameter portion 213. An oil seal 224 is fixed to the lower end of the seal holding part 221. The oil seal 224 adjusts the thickness of the oil oil film around the small diameter portion 213.

The spring seat 23 is fixed to the lower end of the plunger 21.

The plunger spring 24 has one end locked to the spring seat 23 and the other end locked to the fixing portion 222 of the oil seal holder 22. The plunger spring 24 biases the plunger 21 so that the plunger 21 contacts 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 storage unit 30 includes a cover 31, a pulsation damper 33, and a fuel inlet 35. The fuel storage unit 30 temporarily stores the fuel supplied to the fuel suction unit 38.

The cover 31 is a bottomed cylindrical member, and has a cover bottom portion 311 and a cover tube portion 312.

The cover bottom 311 closes the upper opening of the cover tube 312. The lower end portion of the cover cylinder portion 312 is in contact with the upper end surface of the flange portion 112. The cover 31 accommodates the upper housing 15 and the upper part of the cylinder 13.

The cover tube portion 312 has

fitting holes

313, 314, and 315 formed so as to be separated from each other in the circumferential direction. The position of the fitting hole 313 corresponds to the suction passage 152, and the position of the fitting hole 314 corresponds to the discharge passage 154. A fuel suction portion 38 is inserted into the fitting hole 313 from the outside of the cover 31. A fuel discharge relief 60 is inserted into the fitting hole 314 from the outside of the cover 31. A fuel inlet 35 is inserted into the fitting hole 315 from the outside of the cover 31.

The cover 31 and the flange portion 112 are joined by welding. The fuel suction portion 38, the fuel discharge relief portion 60, and the fuel inlet 35 are joined to the cover 31 by welding. By these weldings, the gap between the lower end of the cover 31 and the flange portion 112, the gap between the portion forming the fitting hole 313 and the fuel suction portion 38, the portion forming the fitting hole 314, and the fuel discharge relief The gap between the portion 60 and the gap between the portion forming the fitting hole 315 and the fuel inlet 35 are sealed in a liquid-tight manner.

The cover 31 has a fuel gallery 32 defined by the cover 31 and the flange portion 112. The fuel supplied from the fuel inlet 35 to the fuel gallery 32 is supplied into the fuel suction portion 38 via the communication path 153.

The pulsation damper 33 is provided in the fuel gallery 32. The pulsation damper 33 is composed of two circular dished

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 edges of the

diaphragms

331 and 332 are sandwiched between the two

supports

333 and 334. The pulsation damper 33 is elastically deformed according to the change in the pressure of the fuel in the fuel gallery 32 and reduces the pressure pulsation of the fuel in the fuel gallery 32.

The fuel suction part 38 is a normally open type electromagnetically driven valve, and has a suction valve part 40 and an electromagnetically driven part 50. The fuel suction portion 38 is opened when the plunger 21 descends in the cylinder 13 and supplies fuel to the pressurizing chamber 14. Further, when the plunger 21 starts to rise in the cylinder 13 or in the middle of the rise, the valve 21 is closed so that the fuel in the pressurizing chamber 14 can be pressurized by raising the plunger 21.

The suction valve section 40 includes a first suction valve body 41, a second suction valve body 42, a valve seat 43, a suction valve member 44 as a “valve member”, a bottomed cylindrical member 45 as a “guide member”, And a spring 49 as a biasing member.

The first suction valve body 41 is formed in a cylindrical shape and is fixed to the suction passage 152 of the upper housing 15. The first suction valve body 41 is provided with an electromagnetic drive unit 50 at one end. A second suction valve body 42 that is accommodated inside the upper housing 15 is provided at the other end. The second suction valve body 42 is formed in a cylindrical shape and has a suction chamber 400 that can communicate with the communication path 153 and the pressurizing chamber 14.

In the suction valve section 40, the suction valve member 44 moves in the axial direction by the balance between the pressing force output by the electromagnetic drive section 50 and the biasing force of the spring 49, and the suction valve member 44 is separated from or separated from the valve seat 43. As a result, the suction valve unit 40 opens or closes, and the suction chamber 400 and the pressurization chamber 14 are communicated or blocked. The detailed configuration of the suction valve unit 40 will be described later.

The electromagnetic drive unit 50 includes a movable core 51, a needle 52, a needle guide 53, a fixed core 54, a coil 55, and the like.

The movable core 51 is formed in a cylindrical shape, and is provided so as to be movable in the axial direction within one end portion of the first suction valve body 41. The movable core 51 is fixed to one end of the needle 52.

The needle 52 is supported by the needle guide 53 in the first suction valve body 41 and the second suction valve body 42 so as to be reciprocally movable in the axial direction. The needle 52 can reciprocate integrally with the movable core 51, and the position of the needle 52 is determined when the needle 52 and the valve seat 43 come into contact with each other, and then comes into contact with the suction valve member 44. When the needle 52 is in contact with the valve seat 43, the suction valve member 44 is separated from the valve seat 43.

The needle 52 forms an annular stopper portion 521 that protrudes radially outward on the side opposite to the movable core 51 with respect to the needle guide 53. The needle 52 can move in the direction of the fixed core 54 until the stopper portion 521 contacts the needle guide 53.

The end of the needle guide 53 on the movable core 51 side has a flange 531 that protrudes in the radial direction. The needle 52 forms a flange 522 that protrudes radially outward at a position corresponding to the end of the needle guide 53 opposite to the movable core 51.

A spring 56 is provided between the flange portion 531 and the flange portion 522. The spring 56 urges the needle 52 in the direction of the pressurizing chamber 14 with an urging force stronger than the urging force by which the spring 49 urges the suction valve member 44 in the valve closing direction.

The fixed core 54 is made of a magnetic material, and is provided on the side opposite to the suction valve unit 40 with respect to the movable core 51.

The coil 55 is provided outside the fixed core 54 in the radial direction.

In the electromagnetic drive unit 50, when electric power is supplied to the coil 55, the fixed core 54 attracts the movable core 51 against the urging force of the spring 56. The needle 52 moves in the direction of the fixed core 54 together with the movable core 51 sucked by the fixed core 54. Further, when the supply of power to the coil 55 is stopped, the magnetic attractive force between the fixed core 54 and the movable core 51 is lost. When the magnetic attractive force disappears, the needle 52 moves in the direction opposite to the fixed core 54 by the biasing force of the spring 56.

Thus, the electromagnetic drive unit 50 controls the position of the suction valve member 44 relative to the valve seat 43 by controlling the drive of the needle 52.

The fuel discharge relief portion 60 includes a first discharge valve body 61, a second discharge valve body 62, a discharge valve member 64, and a relief valve member 66.

The first discharge valve body 61 is formed in a cylindrical shape and is fixed to the discharge passage 154 of the upper housing 15.

The second discharge valve body 62 is provided inside the first discharge valve body 61. The second discharge valve body 62 has a bottomed cylindrical shape, and is sandwiched between the first discharge valve body 61 and the upper housing 15 so as to have a bottomed cylindrical space on the pressurizing chamber 14 side.

The second discharge valve body 62 has a discharge passage 621 and a relief passage 622 that is not in communication with the discharge passage 621. The discharge passage 621 opens to the outside in the radial direction of the wall surface on the pressurizing chamber 14 side of the second discharge valve body 62 and opens to the center of the wall surface on the opposite side of the pressurizing chamber 14 of the second discharge valve body 62. ing. The relief passage 622 opens to the center of the wall surface of the second discharge valve body 62 on the pressure chamber 14 side, and opens to the radially outer side of the wall surface of the second discharge valve body 62 opposite to the pressure chamber 14. is doing.

The discharge valve member 64 is located on the side opposite to the pressurizing chamber 14 with respect to the second discharge valve body 62. The discharge valve member 64 can contact or separate from the second discharge valve body 62 and can open and close the discharge passage 621. The discharge valve member 64 is urged in the valve closing direction by a discharge valve spring 65 held by a discharge valve spring holder 641.

The relief valve member 66 is accommodated in a bottomed cylindrical space on the pressure chamber 14 side of the second discharge valve body 62 and can open and close the relief passage 622. The relief valve member 66 is urged in the valve closing direction by a relief valve spring 67 held by a relief valve spring holder 661.

The high-pressure pump 1 according to the first embodiment is characterized by the configuration of the intake valve portion 40 included in the fuel intake portion 38. Here, the detailed configuration of the suction valve unit 40 will be described with reference to FIGS. 4 to 7B. FIG. 4 is a cross-sectional view of the intake valve portion 40 when the valve is closed. Hereinafter, the right side of FIG. 4 will be described as “pressure chamber side”, and the left side of FIG. 4 will be described as “suction chamber side”.

The valve seat 43 is a cylindrical member. The valve seat 43 is provided at the end of the second suction valve body 42 on the pressure chamber 14 side so as not to move relative to the second suction valve body 42 and the upper housing 15. The valve seat 43 partitions the suction passage 152 of the upper housing 15 into a suction chamber 400 and a space on the pressurizing chamber 14 side.

The valve seat 43 has a communication passage 430 at the center. As shown in FIG. 4, the needle 52 is inserted into the communication passage 430 and the fuel flows. Further, the valve seat 43 has a plurality of communication passages 431 as “fuel passages” outside the communication passage 430 in the radial direction. The plurality of communication paths 431 are located at equal intervals in the circumferential direction. The communication passage 431 communicates the suction chamber 400 side and the pressurization chamber 14 side of the valve seat 43. The valve seat 43 has a plurality of seat surfaces 432 as “valve seat surfaces” corresponding to the openings of the plurality of communication passages 431 on the pressurizing chamber 14 side.

The suction valve member 44 is a disk-shaped member, and is provided on the pressure chamber 14 side of the valve seat 43 so as to be reciprocally movable. The suction valve member 44 has a plurality of communication passages 441 as “valve member flow paths” that are positioned at equal intervals in the circumferential direction. The communication passage 441 communicates the suction chamber 400 side and the pressurization chamber 14 side of the suction valve member 44. An end surface 442 of the suction valve member 44 on the suction chamber 400 side is formed so as to be able to contact a plurality of seat surfaces 432, and one end of the needle 52 is in contact therewith. The outer edge portion 443 of the suction valve member 44 on the pressurizing chamber 14 side is formed in a tapered shape so as to allow the fuel flow from the pressurizing chamber 14 to escape radially outward.

The bottomed cylindrical member 45 is provided on the radially outer side of the suction valve member 44 and on the pressurizing chamber 14 side. The bottomed cylindrical member 45 includes a sliding portion 46 positioned on the radially outer side of the suction valve member 44, a connecting portion 47 positioned on the pressurizing chamber 14 side of the sliding portion 46, and the pressurizing chamber 14 side of the connecting portion 47. A bottom portion 48 serving as a “blocking portion”, a contact portion 482, a restriction portion 483, and the like. The sliding part 46, the connecting part 47, the bottom part 48, the contact part 482, and the restricting part 483 are integrally formed.

The sliding portion 46 is a cylindrical portion provided on the radially outer side of the suction valve member 44. The sliding portion 46 is formed to be slidable with the outer edge portion 443 of the suction valve member 44. When the suction valve member 44 is housed inside the sliding portion 46 in the radial direction, the valve seat 43 and the suction valve member 44 are in a positional relationship that allows sealing under high pressure. An outer wall 461 on the radially outer side of the sliding portion 46 is in contact with the inner wall 155 of the upper housing 15.

The sliding part 46 has dents 462 formed at equal intervals in the circumferential direction on the radially inner side. In the first embodiment, as shown in FIG. 7A, four recesses 462 are formed at intervals of 90 degrees. When the suction valve member 44 is accommodated inside the bottomed tubular member 45, the outer wall 444 on the radially outer side of the suction valve member 44 slides on the inner wall 463 where the recess 462 of the bottomed tubular member 45 is not provided. To do. On the other hand, between the inner wall of the recess 462 and the outer wall 444 of the suction valve member 44, the suction chamber 400 side of the bottomed tubular member 45 communicates with the inside of the bottomed tubular member 45 so that fuel can flow. It becomes the “gap” described in the claims.

The connecting portion 47 is an annular portion provided at the end of the sliding portion 46 on the pressurizing chamber 14 side. An end surface 471 of the connecting portion 47 on the pressure chamber 14 side is in contact with the inner wall 156 of the upper housing 15. Thereby, the movement of the bottomed cylindrical member 45 in the direction of the pressurizing chamber 14 is restricted.

The bottom part 48 is a substantially disk-shaped part. The bottom 48 is provided so as to close the opening on the pressure chamber 14 side of the sliding portion 46 and the connecting portion 47. The bottom 48 has a plurality of communication paths 481 as “guide channels”. The communication path 481 communicates the inside of the bottomed tubular member 45 and the pressurized chamber 14 side of the bottomed tubular member 45. The communication path 481 has a virtual circle C441 (see FIG. 7A) connecting the inside (radial inner end) in the radial direction of the communication path 441 of the suction valve member 44 in the direction of the central axis C45 of the bottomed cylindrical member 45. It is formed between a virtual extension surface VP441 formed when translated and an outer wall extension surface VP444 obtained by extending the outer wall 444 of the suction valve member 44 in the direction of the central axis C45 of the bottomed tubular member 45 ( (Refer FIG.7 (b)).

The abutting portion 482 is provided in the approximate center of the bottom portion 48 and on the suction valve member 44 side. One end of the spring 49 comes into contact with the contact portion 482.

The regulating portion 483 is provided on the suction valve member 44 side of the contact portion 482. The restricting portion 483 is formed so as to protrude in the direction of the intake valve member 44 compared to the contact portion 482. The restricting portion 483 restricts the movement of the suction valve member 44 in the direction of the pressurizing chamber 14 while restricting the movement of the spring 49 in the radial direction.

The spring 49 is provided between the suction valve member 44 and the bottom 48. The other end of the spring 49 is in contact with the end surface 445 of the suction valve member 44 on the pressure chamber 14 side. The spring 49 biases the suction valve member 44 toward the suction chamber 400 so that the suction valve member 44 and the valve seat 43 come into contact with each other.

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 621 is blocked by the discharge valve member 64. When the supply of power to the coil 55 is stopped, the needle 52 moves in the direction opposite to the fixed core 54 by the urging force of the spring 56. Thereby, the needle 52 presses the suction valve member 44 and the suction valve member 44 is separated from the valve seat 43. When the valve seat 43 and the suction valve member 44 are separated from each other, the fuel in the suction chamber 400 is sucked into the pressurizing chamber 14 through the

communication passages

431, 430, 441, and 481. Further, the fuel in the suction chamber 400 is sucked into the pressurizing chamber 14 even through the communication passage 431, the radially outer side of the suction valve member 44, and the communication passage 481.

(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 this time, since the supply of electric power to the coil 55 is stopped until a predetermined time, the suction valve unit 40 remains open. For this reason, a part of the fuel sucked into the pressurizing chamber 14 in the suction stroke returns to the fuel storage part 30 via the suction valve part 40.

A magnetic attraction force is generated between the fixed core 54 and the movable core 51 by supplying electric power to the coil 55 at a predetermined time while the plunger 21 is rising. When this magnetic attractive force becomes larger than the resultant force obtained by subtracting the biasing force of the spring 49 from the biasing force of the spring 56, the movable core 51 and the needle 52 move in the direction of the fixed core 54. Thereby, the pressing force to the suction valve member 44 of the needle 52 is released. The suction valve member 44 comes into contact with the valve seat 43 by the dynamic pressure generated by the fuel flow and the spring 49, and the suction valve portion 40 is closed.

(III) Pressurization stroke After the intake valve section 40 is closed, the volume of the pressurizing chamber 14 is reduced by the rise of the plunger 21, and the fuel pressure in the pressurizing chamber 14 is increased. When the force acting on the discharge valve member 64 due to the fuel pressure in the pressurizing chamber 14 becomes larger than the sum of the force acting on the discharge valve member 64 due to the fuel pressure on the fuel discharge port 69 side and the biasing force of the discharge valve spring 65, The member 64 is opened. Thus, the fuel pressurized in the pressurizing chamber 14 is discharged from the fuel discharge port 69 via 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 69.

(A) In the high-pressure pump 1 according to the first embodiment, the sliding portion 46 for guiding the reciprocating movement of the suction valve member 44 in the fuel suction portion 38 is provided as a separate member from the valve seat 43. As a result, the valve seat can have a simple shape so that the rigidity of the valve seat is higher than that in the case where a guide portion having a relatively thin thickness is provided in the valve seat due to restrictions on the physique of the high-pressure pump. Thereby, deformation of the valve seat 43 due to external force such as fuel dynamic pressure can be prevented, and the sealing performance between the intake valve member 44 and the valve seat 43 under high pressure can be improved. Therefore, the high-pressure pump 1 is free from leakage of high-pressure fuel in the fuel suction portion 38, and can improve the fuel discharge efficiency.

(B) Further, a bottom 48 is provided on the pressure chamber 14 side of the suction valve member 44. When the fuel flows backward from the pressurizing chamber 14 to the fuel suction portion 38 in the metering step, the flow of the fuel that flows backward collides with the bottom 48. Thereby, it is possible to prevent the dynamic pressure of the fuel flowing backward from the pressurizing chamber 14 from acting on the suction valve member 44.

(C) Further, the communication path 481 of the bottomed cylindrical member 45 is parallel to the direction of the central axis C45 of the bottomed cylindrical member 45 with a virtual circle C441 connecting the inside in the radial direction of the communication path 441 of the suction valve member 44. It is formed between a virtual extension surface VP441 formed when moved and an outer wall extension surface VP444 obtained by extending the outer wall 444 of the suction valve member 44 in the direction of the central axis C45 of the bottomed tubular member 45. Thus, when fuel is sucked from the suction chamber 400 into the pressurizing chamber 14, the fuel flowing through the communication path 441 toward the pressurizing chamber 14 can smoothly flow without colliding with the bottom 48. Further, when the fuel returns from the pressurizing chamber 14 to the suction chamber 400, the fuel flowing toward the suction chamber 400 through the communication passage 481 does not collide with the valve seat 43, so that the deformation of the valve seat 43 due to the dynamic pressure of the fuel is prevented. can do.

(D) The bottom 48 has an abutting portion 482 with which one end of the spring 49 abuts. This eliminates the need for a member that abuts against the spring 49, and reduces the number of components that constitute the fuel suction portion 38.

(E) Further, the bottom 48 has a restricting portion 483 for restricting the movement of the suction valve member 44 in the direction of the pressurizing chamber 14. This eliminates the need for a member that restricts the movement of the suction valve member 44 in the direction of the pressurizing chamber 14, and reduces the number of components that constitute the fuel suction portion 38.

(F) The bottom 48 has a communication passage 481 through which fuel flowing from the suction chamber 400 to the pressurization chamber 14 or from the pressurization chamber 14 to the suction chamber 400 passes. This eliminates the need to form a fuel passage for the fuel to flow radially outward of the bottomed cylindrical member 45 that slides on the outer wall 444 of the intake valve member 44, thereby simplifying the shape of the intake valve portion 40. be able to.

(G) Since the bottom 48 has a plurality of communication passages 481, the amount of fuel sucked by the pressurizing chamber 14 in the suction stroke and the amount of fuel returned from the pressurizing chamber 14 to the suction chamber 400 in the metering stroke Can be made a sufficient amount. Thereby, the fall of the discharge efficiency of the high-pressure pump 1 by the shortage of fuel flow can be prevented.

(H) Further, the bottomed cylindrical member 45 communicates the suction chamber 400 side and the pressurization chamber 14 side of the suction valve member 44 with the recess 462 while the inner wall 463 slides with the outer wall 444 of the suction valve member 44. To do. Thereby, while guiding the reciprocating movement of the suction valve member 44, the amount of fuel sucked by the pressurizing chamber 14 in the suction stroke and the amount of fuel returned from the pressurizing chamber 14 to the suction chamber 400 in the metering stroke are sufficient. It can be an amount. Thereby, the fall of the discharge efficiency of the high-pressure pump 1 by the shortage of fuel flow can be prevented.

(Second embodiment)
Next, a high-pressure pump according to a second embodiment of the present disclosure will be described based on FIGS. 8 to 10 (b). The second embodiment differs from the first embodiment in the shapes of the suction valve member and the bottomed cylindrical member. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

FIG. 8 shows a cross-sectional view of the suction valve portion 70 of the high-pressure pump according to the second embodiment. FIG. 8 is a cross-sectional view of the intake valve portion 70 when the valve is closed. The suction valve section 70 includes a first suction valve body 41, a second suction valve body 42, a valve seat 43, a suction valve member 74 as a “valve member”, a bottomed cylindrical member 75 as a “guide member”, and a spring 49. Etc. Hereinafter, the right side of FIG. 8 will be described as “pressure chamber side”, and the left side of FIG. 8 will be described as “suction chamber side”.

The suction valve member 74 is a disk-like member and is provided on the pressure chamber 14 side of the valve seat 43 so as to be capable of reciprocating in the axial direction. The suction valve member 74 includes a plurality of communication passages 741 as a plurality of “valve member flow paths” located at equal intervals in the circumferential direction. The communication passage 741 communicates the suction chamber 400 side and the pressurization chamber 14 side of the suction valve member 74. An end surface 742 of the suction valve member 74 on the suction chamber 400 side is formed so as to be able to contact a plurality of seat surfaces 432, and one end of the needle 52 is in contact therewith.

The radially outer end of the suction valve member 74 has a plurality of protrusions 743. In the second embodiment, three protrusions 743 are provided at equal intervals in the circumferential direction. The outer wall 744 of the protrusion 743 slides on the inner wall 762 of the sliding portion 76 included in the bottomed cylindrical member 75. Between the adjacent projections 743, the suction valve member 74 is connected to the suction chamber 400 side and the pressurization chamber 14 side to form a gap 745 through which fuel can flow. The outer edge portion 746 on the pressurizing chamber 14 side of the suction valve member 74 not provided with the protrusion 743 is formed in a tapered shape so as to allow the fuel flow from the pressurizing chamber 14 to escape radially outward. The other end of the spring 49 is in contact with the end surface 747 of the suction valve member 74 on the pressure chamber 14 side.

The bottomed cylindrical member 75 is provided on the radially outer side of the suction valve member 74 and on the pressurizing chamber 14 side. The bottomed cylindrical member 75 includes a sliding portion 76 positioned on the radially outer side of the suction valve member 74, a connecting portion 47 positioned on the pressurizing chamber 14 side of the sliding portion 76, and the pressurizing chamber 14 side of the connecting portion 47. At the bottom 48. The sliding part 76, the connection part 47, and the bottom part 48 are integrally formed.

The sliding portion 76 is a cylindrical portion provided on the radially outer side of the suction valve member 44. The sliding portion 76 is formed to be slidable with the outer edge portion 746 of the suction valve member 74. An outer wall 761 on the radially outer side of the sliding portion 76 is in contact with the inner wall 155 of the upper housing 15. The inner wall 762 of the sliding portion 76 is formed in a circular shape.

The bottom portion 48 of the bottomed cylindrical member 75 is provided so as to close the opening on the pressure chamber 14 side of the sliding portion 76 and the connecting portion 47. The bottom 48 of the bottomed cylindrical member 75 has a plurality of communication passages 781 as “guide channels”. The communication passage 781 is formed when a virtual circle C741 (see FIG. 10A) connecting the radial inner sides of the communication passage 741 of the suction valve member 74 is translated in the direction of the central axis C75 of the bottomed cylindrical member 75. The virtual extension surface VP741 is formed and the outer wall extension surface VP744 obtained by extending the outer wall 744 of the suction valve member 74 in the direction of the central axis C75 of the bottomed cylindrical member 75 (see FIG. 10B). ).

In the high-pressure pump according to the second embodiment, a sliding portion 76 that guides the reciprocating movement of the suction valve member 74 in the suction valve portion 70 is provided as a separate member from the valve seat 43. Thereby, 2nd embodiment has the effect (a) of 1st embodiment.

The bottomed cylindrical member 75 has a contact portion 482 and a restriction portion 483. Thereby, 2nd embodiment has an effect (b) of a 1st embodiment, (d), and (e). The bottom 48 has a communication path 781. Thereby, 2nd embodiment has the effect (c), (f), (g) of 1st embodiment.

Further, a gap 745 between adjacent protrusions 743 included in the suction valve member 74 serves as a fuel passage through which fuel can flow. Thereby, 2nd embodiment has the effect (h) of 1st embodiment.

(Other embodiments)
(1) In the above-described embodiment, the suction valve portion of the high-pressure pump is a multi-seat valve. However, the suction valve portion of the high pressure pump may be a single seat type valve.

(2) In the above-described embodiment, the bottomed cylindrical member has a bottom portion that is provided so as to close the opening on the pressurizing chamber side of the guide portion. However, the bottom may not be present.

(3) In the above-described embodiment, the guide portion and the bottom portion are integrally formed. However, the guide part and the bottom part may not be formed integrally. It may be provided as a separate member.

(4) In the above-described embodiment, the bottomed tubular member has the restricting portion that restricts the movement of the suction valve member in the direction of the pressurizing chamber. However, a protrusion that protrudes radially inward from the inner wall of the end portion of the guide portion on the pressurizing chamber side may be the restricting portion.

(5) In the first embodiment, the bottomed cylindrical member has four recesses. In addition, the depressions are formed at regular intervals at intervals of 90 degrees. However, the number of depressions and the positions where they are formed are not limited to this.

(6) In the second embodiment, the number of protrusions of the suction valve member is three. Further, the protrusions are formed at equal intervals in the circumferential direction. However, the number of protrusions and the positions where they are formed are not limited to this.

(7) In the above-described embodiment, the bottomed tubular member restricts the movement of the communication passage as the “guide passage”, the contact portion with which one end of the spring contacts, and the suction valve member in the direction of the pressurizing chamber. It has a regulation part to do. However, the bottomed cylindrical member may not have these parts. These may be provided as separate members.

(8) In the above-described embodiment, the guide portion is configured such that the outer wall on the radially outer side is in contact with the inner wall of the upper housing as a “passage forming member”. However, the outer wall of the guide portion may not be in contact with the inner wall of the “passage forming member”.

(9) In the above-described embodiment, a gap through which fuel flows is formed between the intake valve member and the guide portion. However, there may be no gap.

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

Claims

A reciprocating plunger (21);
A cylinder (13) having a pressurizing chamber (14) that supports the plunger (21) so as to be reciprocally movable and whose volume changes when the plunger (21) moves;
A passage forming member (15) forming a communication passage (152) communicating with the pressurizing chamber (14);
A plurality of fuels that are provided in the communication passage (152) and communicate with the pressurizing chamber (14) through the pressurizing chamber (14) and the opposite side of the pressurizing chamber (14). A valve seat (43) having a passage (431) and a plurality of valve seat surfaces (432) respectively formed around the opening on the pressurizing chamber (14) side of the plurality of fuel passages (431);
The plurality of valve seat surfaces (432) are provided so as to be in contact with each other, and contact between the plurality of valve seat surfaces (432) is provided between the plurality of fuel passages (431) and the pressurizing chamber (14). A valve member (44, 44) that cuts off the flow of fuel and allows the flow of fuel between the plurality of fuel passages (431) and the pressurizing chamber (14) when separated from the plurality of valve seat surfaces (432). 74)
The valve seat (43) is formed separately from the valve seat (43), is provided on the pressure chamber (14) side, and the outer edge (443, 746) of the valve member (44, 74). A guide member (45, 75) having a slidable sliding portion (46, 76) and capable of guiding the movement of the valve member (44, 74);
A biasing member (49) provided between the guide member (45, 75) and the valve member (44, 74) and capable of biasing the valve member (44, 74) toward the valve seat (43). )When,
A fuel discharge section (60) for discharging the fuel pressurized in the pressurizing chamber (14) to the outside;
High pressure pump with
The guide member (45, 75) is formed so as to be able to contact the pressure chamber (14) side of the valve member (44, 74), and the pressure chamber (14) of the valve member (44, 74). The high pressure pump according to claim 1, further comprising a restricting portion (483) capable of restricting movement toward the) side.
The high-pressure pump according to claim 2, wherein the restricting portion (483) can contact a center of the valve member (44, 74).
The guide members (45, 75) extend the radially outer outer walls (444, 744) of the valve members (44, 74) in the direction of the central axis (C45, C75) of the guide members (45, 75). The high-pressure pump according to any one of claims 1 to 3, further comprising a guide channel (481, 781) formed inside the outer wall extension surface (VP444, VP744).
The guide channel (481, 781) has a center on a central axis (C45, C75) of the guide member (45, 75), and the valve seat (43) side of the valve member (44, 74). A virtual circle (C441, C741) connecting the radially inner sides of the plurality of valve member flow paths (441, 741) communicating with the pressurizing chamber (14) side is a central axis (C45) of the guide member (45, 75). , C75) The high-pressure pump according to claim 4, wherein the high-pressure pump is formed between a virtual extension surface (VP441, VP741) formed when translated in the direction C75) and the outer wall extension surface (VP444, VP744).
The guide member (45, 75) is provided on the pressurizing chamber (14) side of the valve member (44, 74) and has an opening on the pressurizing chamber (14) side of the guide member (45, 75). The high-pressure pump according to any one of claims 1 to 5, further comprising a closing portion (48) for closing.
The said guide member (45, 75) has a contact part (482) with which the one end by the side of the said pressurization chamber (14) of the said urging | biasing member (49) contact | abuts. The high-pressure pump described.
The outer wall (461, 761) on the radially outer side of the guide member (45, 75) and the inner wall (155) of the passage forming member (15) are in contact with each other. High pressure pump.
Between the valve member (44, 74) and the guide member (45, 75), the pressure member (44, 74) side of the valve member (44, 74) and the valve member (44, 74). The high pressure pump according to any one of claims 1 to 8, wherein a gap (462, 745) is formed to communicate with a side opposite to the pressurizing chamber (14).