JP2013060945A - High pressure pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a high pressure pump allowing the mounting of a pulsation damper to a fuel chamber with a simple structure.SOLUTION: The pulsation damper 70 comprises an upper diaphragm 72, a lower diaphragm 73, an upper support member 80 and a lower support member 90. A peripheral edge part of the upper diaphragm 72, a peripheral edge part of the lower diaphragm 73, an upper ring-shaped part 81 of the upper support member 80 and a lower ring-shaped part 91 of the lower support member 90 are joined together. A protrusion 937 of a lower support body 932 extended from the lower ring-shaped part 91 is locked to the hole 194 of a pump body 20. Thereby, the pulsation damper 70 is mounted in the fuel chamber.

Description

  The present invention relates to a high pressure pump.

Conventionally, a high pressure pump that pressurizes fuel pumped from a fuel tank by a low pressure pump and supplies the pressurized fuel to an internal combustion engine is known. The high-pressure pump includes a pulsation damper that reduces pressure pulsation in a fuel chamber that communicates with a pressurizing chamber in which fuel is pressurized. In the pulsation damper, the peripheral portions of two diaphragms are welded, and a gas at atmospheric pressure or higher is sealed inside. The displacement of the two diaphragms according to the pressure change in the fuel chamber changes the volume of the fuel chamber and attenuates the pressure pulsation.
The pulsation damper of Patent Document 1 is attached to a fuel chamber with the peripheral edge of a diaphragm constituting the pulsation damper sandwiched between an upper support member and a lower support member. Thereby, the pulsation damper is restrained from being displaced in the direction in which the peripheral portions of the two diaphragms are separated from each other by the pressure pulsation of the fuel chamber.

Japanese Patent No. 423567

However, in Patent Document 1, the following problems (1), (2), and (3) may occur.
(1) The upper support member and the lower support member are formed so that the end face contacting the peripheral edge of the diaphragm is parallel to the peripheral edge so that the stress due to the displacement of the diaphragm does not act on the welding for joining the peripheral edge. Must. Therefore, the processing cost of the upper support member and the lower support member increases.
(2) The upper support member and the lower support member must hold the entire periphery of the peripheral edge of the diaphragm with the same load so that stress due to the displacement of the diaphragm does not act on the welding of the peripheral edge. For this reason, the upper support member and the lower support member increase the area of the conical portion that connects the end surface that contacts the inner wall of the fuel chamber and the end surface that contacts the peripheral edge of the diaphragm. Therefore, the fuel flow in the fuel chamber is prevented by the upper support member and the lower support member.
(3) In order to prevent the twisting stress from acting on the diaphragm, the center of the upper support member and the center of the lower support member must be assembled together. Therefore, the processing accuracy and assembly accuracy of the upper support member and the lower support member must be increased, and the manufacturing cost increases. Further, when the upper support member and the lower support member are formed by pressing, it is difficult to reduce the manufacturing tolerance so that the center of the upper support member and the center of the lower support member coincide with each other.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a high-pressure pump in which a pulsation damper can be attached to a fuel chamber with a simple configuration.

According to the present invention, in the high-pressure pump provided with the pulsation damper main body, the support extending from at least one of the annular upper annular part and the lower annular part joined to the peripheral part of the pulsation damper main body is the pump body or It is locked to the lid member.
Thereby, the upper annular portion and the lower annular portion prevent stress due to the displacement of the diaphragm from acting on the peripheral portion of the weld. Therefore, the pulsation damper can be attached to the fuel chamber by locking the support extending from at least one of the upper annular portion and the lower annular portion to the pump body or the lid member. Therefore, the size of the support body can be reduced, the fuel flow in the fuel chamber can be improved, and the pulsation damper can be attached to the fuel chamber with a simple configuration.

1 is a cross-sectional view of a high pressure pump according to a first embodiment of the present invention. Sectional drawing of the II-II line | wire of FIG. The principal part expanded sectional view of the high pressure pump by a 1st embodiment of the present invention. (A) is a top view of the state before the pulsation damper with which the high pressure pump by 1st Embodiment of this invention is equipped is attached to a fuel chamber. (B) is sectional drawing of the IVB-IVB line | wire of (A). The expanded sectional view of the pulsation damper with which the high-pressure pump by a 1st embodiment of the present invention is provided. The graph which shows the displacement of the diaphragm of the high pressure pump by 1st Embodiment of this invention. (B) is a graph which shows the stress which arises in a diaphragm. The principal part expanded sectional view of the high-pressure pump by a 2nd embodiment of the present invention. (A) is a top view of the pulsation damper with which the high-pressure pump by a 3rd embodiment of the present invention is provided. (B) is sectional drawing of the VIIIB-VIIIB line | wire of (A). (C) is the arrow VIIIC direction view of (B), and is a bottom view of a pulsation damper. Sectional drawing of the high pressure pump by 4th Embodiment of this invention. The principal part expanded sectional view of the high-pressure pump by a 4th embodiment of the present invention. The principal part expanded sectional view of the high pressure pump by a 5th embodiment of the present invention. The principal part expanded sectional view of the high pressure pump by a 6th embodiment of the present invention. The principal part expanded sectional view of the high-pressure pump by a 7th embodiment of the present invention. The principal part expanded sectional view of the high pressure pump by 8th Embodiment of this invention. The top view before the bending process of the lower support member by 8th Embodiment of this invention. Explanatory drawing of the assembly | attachment process of the pump body and lower support member by 8th Embodiment of this invention. The principal part expanded sectional view of the high-pressure pump by 9th Embodiment of this invention. The arrow view of the XVIII direction of FIG. The principal part expanded sectional view of the high pressure pump by 10th Embodiment of this invention. The top view before the bending process of the lower support member by 10th Embodiment of this invention. The top view before the bending process of the lower support member by 11th Embodiment of this invention. The principal part expanded sectional view of the high-pressure pump by a 12th embodiment of the present invention. FIG. 23 is an arrow view in the XXIII direction of FIG. 22. The perspective view of FIG. The top view before the bending process of the lower support member by 12th Embodiment of this invention. The principal part expanded sectional view of the high pressure pump by 13th Embodiment of this invention. The top view before the bending process of the lower support member by 13th Embodiment of this invention. The principal part expanded sectional view of the high-pressure pump by 14th Embodiment of this invention. The top view before the bending process of the lower support member by 14th Embodiment of this invention. The principal part expanded sectional view of the high pressure pump by 15th Embodiment of this invention. The top view of the lower support member by 15th Embodiment of this invention. Explanatory drawing of the assembly | attachment process of the pump body and lower support member by 15th Embodiment of this invention. Explanatory drawing of the assembly | attachment process of the pump body and lower support member by 15th Embodiment of this invention. Explanatory drawing of the assembly | attachment process of the pump body and lower support member by 15th Embodiment of this invention. The principal part expanded sectional view of the high-pressure pump by a 16th embodiment of the present invention. The principal part expanded sectional view of the high-pressure pump by a 17th embodiment of the present invention. The top view of the pump body by 17th Embodiment of this invention. The principal part expanded sectional view of the high-pressure pump by 18th Embodiment of this invention. Sectional drawing of the XXXIX-XXXIX line | wire of FIG. The principal part expanded sectional view of the high-pressure pump by a 19th embodiment of the present invention. The principal part expanded sectional view of the high-pressure pump by a 20th embodiment of the present invention. The principal part expanded sectional view of the high pressure pump by 21st Embodiment of this invention. The principal part expanded sectional view of the high pressure pump by 22nd Embodiment of this invention. The principal part expanded sectional view of the high-pressure pump by a 23rd embodiment of the present invention. The principal part expanded sectional view of the high-pressure pump by 24th Embodiment of this invention.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
A high-pressure pump 1 according to a first embodiment of the present invention is shown in FIGS. The high-pressure pump 1 pressurizes fuel pumped from a fuel tank (not shown) by a low-pressure pump and pumps the fuel to a fuel rail. An injector that injects fuel into a cylinder of the internal combustion engine is connected to the fuel rail.
In the following description, the upper side of FIG. 1 is referred to as “upper” and the lower side of FIG. However, the direction in which the high-pressure pump is installed is not limited.

As shown in FIGS. 1 and 2, the high-pressure pump 1 includes a plunger 10, a cylinder portion 11, an upper pump body 20 and a lower pump body 21 as a pump body, a lid member 60, a pulsation damper 70, and the like. In addition, the cylinder part 11 and the pump body may be comprised integrally.
The plunger 10 is formed in a solid cylindrical shape, and is provided inside the cylinder portion 11 so as to be capable of reciprocating in the axial direction. In the plunger 10, a large diameter portion 12 and a small diameter portion 13 having an outer diameter smaller than that of the large diameter portion 12 are integrally formed. The large diameter portion 12 slides on the inner wall of the cylinder portion 11. The small diameter portion 13 is formed below the large diameter portion 12.

  The cylinder part 11 is formed in a bottomed cylindrical shape. A pressurizing chamber 110 is formed by the inner wall on the bottom side of the cylinder portion 11 and the outer wall of the large-diameter portion 12 of the plunger 10. The cylinder part 11 has a suction hole 111 that passes through the pressurizing chamber 110 and the supply part 30, and a discharge hole 112 that passes through the pressurization chamber 110 and the discharge part 50.

The lower pump body 21 is provided outside the cylinder portion 11 in the radial direction, and includes a cylinder holding portion 211, an engine mounting portion 212, and a fitting portion 213.
The cylinder holding portion 211 is formed in a cylindrical shape, and abuts against the outer wall of the cylinder portion 11 in the radially outward direction. The engine mounting portion 212 extends annularly from the lower portion of the cylinder holding portion 211 in the radially outward direction. The engine mounting portion 212 is provided with a mounting hole 214 in which the high-pressure pump 1 can be mounted on the engine head. The fitting portion 213 extends downward from the engine mounting portion 212 in a cylindrical shape. The fitting part 213 can be fitted into a high-pressure pump mounting hole of an engine head (not shown).

An oil seal holder 14 is provided inside the fitting portion 213. The oil seal holder 14 is formed in a substantially cylindrical shape, and has a press-fit portion 141 that is press-fitted into the inner wall of the fitting portion 213, and a base portion 142 that is positioned on the outer periphery of the small-diameter portion 13.
A ring-shaped seal 15 is provided between the oil seal holder 14 and the small diameter portion 13. The seal 15 includes a Teflon ring 151 (Teflon is a registered trademark) on the inner diameter side and an O-ring 152 on the outer diameter side. The thickness of the fuel oil film around the small-diameter portion of the plunger 10 is adjusted by the seal 15, and fuel leakage to the engine is suppressed.
The oil seal holder 14 has an oil seal 153 at the tip. The oil seal 153 regulates the thickness of the oil oil film around the small-diameter portion of the plunger 10, and oil leakage from the engine into the high-pressure pump is suppressed.

The plunger stopper 16 is formed in a disc shape and is provided between the end of the cylinder portion 11 and the seal 15. The plunger stopper 16 has the small-diameter portion 13 of the plunger 10 inserted through a central hole. The plunger stopper 16 has a plurality of grooves 161 extending radially outward from the central hole. A variable volume chamber is formed by the stepped surface between the large diameter portion 12 and the small diameter portion 13 of the plunger 10, the inner wall of the small diameter portion 13, the inner wall of the cylinder portion 11, and the plunger stopper 16.
One end of the plunger spring 17 is locked to a spring seat 18 provided at the end of the plunger 10, and the other end is locked to a press-fit portion 141 of the oil seal holder 14. The plunger spring 17 urges the end of the plunger 10 to a cam shaft (not shown) via a tappet (not shown). Thereby, the plunger 10 reciprocates in the axial direction according to the profile of the camshaft. The volume of the pressure chamber 110 and the volume of the variable volume chamber are changed by the reciprocating movement of the plunger 10.

The upper pump body 20 is formed in a substantially rectangular parallelepiped shape and is provided on the upper side of the lower pump body 21. The upper pump body 20 includes a cylinder insertion hole 22, a supply unit 30 and a discharge unit 50. In the upper pump body 20, the inner wall of the cylinder insertion hole 22 is press-fitted into the outer wall of the cylinder portion 11 in the radially outward direction.
The supply unit 30 includes a suction valve body 31, a seat body 32, a suction valve member 33, a first spring holder 34, a first spring 35, an electromagnetic drive unit 40, and the like.
The suction valve body 31 is formed in a substantially cylindrical shape and is press-fitted into a suction passage 23 formed in the upper pump body 20. A cylindrical seat body 32 is provided on the pressure chamber side of the suction valve body 31. The seat body 32 has a suction chamber 311 inside. The suction chamber 311 communicates with the fuel chamber 63 outside the upper pump body 20 through a communication passage 24 formed in the upper pump body 20. The seat body 32 has a suction valve valve seat 36 on the pressurizing chamber side.
The suction valve member 33 is provided on the pressurizing chamber side of the suction valve valve seat 36 and can be seated and separated from the suction valve valve seat 36.
One end of the first spring 35 contacts the first spring holder 34 provided on the pressure chamber side of the suction valve member 33, the other end contacts the suction valve member 33, and the suction valve member 33 is closed in the valve closing direction ( (Left direction in FIG. 1).

The electromagnetic drive unit 40 includes a fixed core 41, a coil 42, a movable core 43, and the like.
A fixed core 41 is provided on the opposite side of the suction valve body 31 from the pressurizing chamber 110. A cylindrical member 44 made of a nonmagnetic material is provided between the fixed core 41 and the suction valve body 31. The cylindrical member 44 suppresses a short circuit of magnetic flux between the fixed core 41 and the suction valve body 31.
A coil 42 is wound around a bobbin 45 provided on the radially outer side of the fixed core 41. A cylindrical case 46 and a flange 47 cover the outside of the coil 42. A connector 48 extends outward in the diameter direction of the case 46. When the coil 42 is energized through the terminal 481 of the connector 48, the coil 42 generates a magnetic field.
On the pressure chamber side of the fixed core 41, a substantially cylindrical movable core 43 is provided inside the suction valve body 31 so as to be reciprocally movable. A needle 49 is fixed to the movable core 43. The needle 49 is supported by a second spring holder 37 provided inside the suction valve body 31 so as to be reciprocally movable. The end of the pressure chamber side of the needle 49 can come into contact with the suction valve member 33. The second spring 38 provided inside the second spring holder 37 has a force stronger than the force by which the first spring 35 biases the suction valve member 33 in the valve closing direction, and opens the needle 49 in the valve opening direction (FIG. 1). To the right).

When the coil 42 is not energized, the movable core 43 and the fixed core 41 are separated from each other by the urging force of the second spring 38. As a result, the needle 49 integral with the movable core 43 moves to the pressurizing chamber side, and the suction valve member 33 is opened by the end surface of the needle 49 pressing the suction valve member 33.
When the coil 42 is energized, a magnetic flux flows through a magnetic circuit formed by the fixed core 41, the movable core 43, the flange 47, and the case 46, and the movable core 43 resists the urging force of the second spring 38. Magnetically attracted to the side. As a result, the needle 49 releases the pressing force against the suction valve member 33.

The discharge unit 50 includes a fuel discharge housing 51, a discharge valve body 52, a discharge valve member 53, a relief valve member 54, and the like.
The fuel discharge housing 51 is formed in a substantially cylindrical shape and is press-fitted into a discharge passage 25 formed in the upper pump body 20. A discharge valve body 52 is provided inside the fuel discharge housing 51. The discharge valve body 52 has a discharge valve seat 56 on the fuel outlet 55 side.
The discharge valve member 53 is provided on the fuel outlet 55 side of the discharge valve body 52, and can be seated and separated from the valve seat 56 for the discharge valve. The discharge valve spring 57 urges the discharge valve member 53 to the discharge valve valve seat 56.
The discharge valve body 52 has a relief valve valve seat 58 on the pressurizing chamber side. The relief valve member 54 is provided on the pressure chamber side of the relief valve valve seat 58 and can be seated and separated from the relief valve valve seat 58. The relief valve spring 59 biases the relief valve member 54 toward the relief valve seat 58. A relief passage 521 formed inside the relief valve seat 58 communicates with the fuel outlet 55.

The lid member 60 is formed in a bottomed cylindrical shape, and includes a bottom portion 61 and a cylindrical portion 62 that extends from the outer edge of the bottom portion 61 to one side. The cylinder part 62 is joined to the engine mounting part 212 of the lower pump body 21 in a liquid-tight manner by welding or the like. The lid member 60 covers the upper pump body 20 and the lower pump body 21 and forms a fuel chamber 63 inside. The fuel chamber 63 communicates with the pressurizing chamber 110 through the communication passage 24 and the suction chamber 311 of the upper pump body 20.
As shown in FIG. 2, the lid member 60 has a cylindrical section 62 with a substantially octagonal cross section, a first insertion hole 64 through which the supply section 30 is inserted, a second insertion hole 65 through which the discharge section 50 is inserted, In addition, a third insertion hole 67 through which the fuel inlet 66 is inserted is provided. The fuel inlet 66 supplies fuel pumped up from a low-pressure pump (not shown) to the fuel chamber 63.
The first insertion hole 64 and the supply unit 30 of the lid member 60, the second insertion hole 65 and the discharge unit 50, and the third insertion hole 67 and the fuel inlet 66 are liquid-tight by welding or the like. It is joined.
By reciprocating movement of the plunger 10, fuel is sucked from the fuel chamber 63 to the pressurizing chamber side via the communication passage 24 and the suction chamber 311, or fuel from the pressurization chamber 110 via the suction chamber 311 and the communication passage 24. When the fuel is discharged into the chamber 63, fuel pressure pulsation occurs in the fuel chamber 63.

As shown in FIGS. 3 and 4, the pulsation damper 70 is provided between the upper pump body 20 and the lid member 60. The pulsation damper 70 includes a pulsation damper main body 71, an upper support member 80, and a lower support member 90, and is configured as a subassembly.
The pulsation damper main body 71 includes two diaphragms 72 and 73. The diaphragms 72 and 73 are formed in a dish shape by pressing a metal plate having a high yield strength and fatigue limit such as stainless steel. In the pulsation damper main body 71, peripheral portions 74 and 75 of two diaphragms 72 and 73 are joined, and a gas having a predetermined pressure is sealed in an inner sealed space 76. The pulsation damper main body 71 reduces the fuel pressure pulsation of the fuel chamber 63 by elastically deforming the two diaphragms 72 and 73 according to the change of the fuel pressure in the fuel chamber 63. The spring of the pulsation damper main body 71 is set by appropriately setting the plate thickness, material, outer diameter, and air pressure sealed in the sealed space 76 according to durability or other required performance. A constant is set. And the pulsation frequency and pulsation damping performance which the pulsation damper main body 71 reduces are determined by this spring constant. When the diaphragm is thin, the pulsation damping effect of the pulsation damper main body 71 is improved. Further, when the outer diameters of the movable portions 78 and 79 of the pulsation damper main body 71 are large, the pulsation damping effect of the pulsation damper main body 71 is improved. The movable portions 78 and 79 are substantially disk-shaped portions that can be displaced when the pulsation damper main body 71 reduces the fuel pressure pulsation in the fuel chamber 63.

  The upper support member 80 includes an upper annular portion 81, an upper cover portion 82, and an upper support 83, and is integrally formed by pressing a metal plate material having a predetermined rigidity such as stainless steel. A plate material forming the upper support member 80 is referred to as a first plate material. The upper annular portion 81 is formed in an annular shape parallel to the peripheral edge portion 74 of the upper diaphragm 72. The upper annular part 81 of the upper support member 80, the peripheral part 74 of the upper diaphragm 72, the peripheral part 75 of the lower diaphragm 73, and the lower annular part 91 of the lower support member 90 are continuously welded in the circumferential direction by laser welding. Are joined. FIG. 5 shows the weld seam 77. The weld seam 77 is formed on the entire circumference of the pulsation damper 70.

The upper cover portion 82 extends from the upper annular portion 81 along the upper diaphragm 72. The upper cover portion 82 is formed in a planar shape substantially parallel to the movable portion 78 of the upper diaphragm 72. Here, a plane including the contact surfaces of the peripheral portions 74 and 75 of the two diaphragms 72 and 73 is defined as a virtual plane S. The distance between the virtual plane S and the center of the outer end surface of the movable portion 78 when the air pressure in the sealed space 76 of the pulsation damper main body 71 and the air pressure outside the pulsation damper main body 71 are the same is defined as a distance d1. Further, the distance between the upper diaphragm side end surface of the upper cover 82 and the virtual plane S is d2 (not shown). In this case, the relationship is d2> d1. The upper cover portion 82 restricts the upper diaphragm 72 from expanding toward the bottom side of the lid member 60.
The upper cover portion 82 has a circular fuel passage 84 in the center and four fuel passages 85 in the circumferential direction. These fuel passages 84 and 85 are formed by pressing the first plate material described above.

The four upper supports 83 are formed by bending the fuel passages 84 and 85 at the same time as or subsequent to the pressing. That is, the hole formed by cutting the upper support 83 from the first plate material becomes the fuel passage 85. The upper support 83 is connected to the upper cover portion 82 on the lid member side of the movable portion 78 of the upper diaphragm 72, and extends radially outward from a position where it is connected to the upper cover portion 82. Specifically, the upper support 83 has one end on the inner peripheral side of the upper cover portion 82 (specifically, a position inside the half of the radius of the upper diaphragm 72 and a position outside the central fuel passage 84). The other end extends to the outer peripheral side of the upper cover portion 82. The upper support 83 is bent vertically before the lid member 60 from the end of the vertical portion 86 on the lid member side, and extends in the radially outward direction from the upper cover portion 82 to the bottom side of the lid member 60 substantially vertically. The upper abutting portion 87 and a curved portion 88 that curves from the end of the upper abutting portion 87 in the radially outward direction to the upper diaphragm side. In the upper support 83, the upper contact portion 87 contacts the inner wall of the lid member 60. The upper contact portion 87 is in contact with the lid member 60 on the radially outer side, and has a slight gap between the radially inner side and the lid member 60.
The angle formed by the vertical portion 86 and the upper contact portion 87 before the installation in the fuel chamber 63 is set to 90 ° or more. In this state, the distance between the upper contact portion 87 of the upper support 83 and the upper cover portion 82 is h1. On the other hand, the distance between the upper contact portion 87 and the upper cover portion 82 of the upper support 83 in the state where it is installed in the fuel chamber 63 is h2. In this case, h1> h2. The load of the upper support 83 is set according to the material of the upper support 83, the plate thickness, the angle formed by the vertical portion 86 and the upper contact portion 87, the distance h1-h2. That is, the upper support 83 has a spring force that presses the lid member 60 toward the anti-pump body.

The lower support member 90 has substantially the same configuration as the upper support member 80. The lower support member 90 includes a lower annular portion 91, a lower cover portion 92, and a lower support body 93, and is integrally formed by pressing a metal plate material having a predetermined rigidity such as stainless steel. A plate material forming the lower support member 90 is referred to as a second plate material. The lower annular portion 91 is formed in an annular shape parallel to the peripheral edge portion 75 of the lower diaphragm 73.
The lower cover portion 92 extends from the lower annular portion 91 along the lower diaphragm 73. The lower cover portion 92 is formed in a planar shape substantially parallel to the movable portion 79 of the lower diaphragm 73. The distance between the virtual plane S and the center of the outer end face of the movable portion 79 when the air pressure in the sealed space 76 of the pulsation damper main body 71 is the same as the air pressure outside the pulsation damper main body 71 is a distance d3. Further, the distance between the end surface of the lower cover 92 on the lower diaphragm 73 side and the virtual plane S is d4 (not shown). In this case, the relationship is d4> d3. The lower cover portion 92 restricts the lower diaphragm 73 from expanding toward the upper pump body.
The lower cover portion 92 has a circular fuel passage 94 in the center and four fuel passages 95 in the circumferential direction. These fuel passages 94 and 95 are formed by pressing the second plate material described above.

  The four lower supports 93 are formed by bending the fuel passages 94 and 95 at the same time as or after the pressing. That is, the hole formed by cutting the lower support 93 from the second plate material becomes the fuel passage 95. The lower support 93 is connected to the lower cover portion 92 on the pump body side of the movable portion 79 of the lower diaphragm 73 and extends radially outward from a position where the lower support 93 is connected to the lower cover portion 92. Specifically, one end of the lower support 93 is located on the inner peripheral side of the lower cover portion 92 (specifically, a position inside the half of the radius of the lower diaphragm 73 and a position outside the central fuel passage 94). The other end extends to the outer peripheral side of the lower cover portion 92. The lower support body 93 is bent in front of the upper pump body 20 from a cylinder abutting portion 96 extending substantially vertically from the lower cover portion 92 toward the upper pump body side, and an end of the cylinder abutting portion 96 on the upper pump body side. A lower abutting portion 97 extending in the radially outward direction and a curved portion 98 that curves toward the lower diaphragm 73 from the radially outer end of the lower abutting portion 97 are provided.

  The cylinder contact portion 96 extends in the axial direction of the cylinder portion 11 along the outer wall of the convex portion 19 of the cylinder portion 11 protruding from the upper pump body 20 toward the fuel chamber. The convex part 19 of the cylinder part 11 is inserted between the four cylinder contact parts 96. Let the outer diameter of the convex part 19 of the cylinder part 11 be an outer diameter D1. The outer diameter D <b> 1 of the convex portion 19 of the cylinder portion 11 is formed to be smaller than the outer diameter of the cylinder body portion that is press-fitted into the upper pump body 20. A distance D2 is a distance between an end surface in the inward radial direction of the cylinder contact portion 96 and an end surface in the inward radial direction of another cylinder contact portion 96 facing each other across the axis of the cylinder portion 11. The relationship is D1 ≦ D2. Thereby, the cylinder contact part 96 is latched by the outer wall of the convex part 19 of the cylinder part 11 in the radially outward direction. Therefore, the pulsation damper 70 is restricted from moving in the radial direction.

The lower abutting portion 97 is fitted in a concave groove 26 provided in the upper pump body 20. The lower contact portion 97 is in contact with the concave groove 26 of the upper pump body 20 on the outer side in the radial direction, and has a slight gap between the inner side in the radial direction and the concave groove 26.
The angle formed by the cylinder contact portion 96 and the lower contact portion 97 before the installation in the fuel chamber 63 is set to 90 ° or more. In this state, the distance between the lower contact portion 97 and the lower cover portion 92 is h3. The distance between the lower contact portion 97 and the lower cover portion 92 in the state where it is installed in the fuel chamber 63 is h4. In this case, h3> h4. The load of the lower support 93 is set depending on the material of the lower support 93, the plate thickness, the angle formed between the cylinder contact portion 96 and the lower contact portion 97, the distance h3-h4, and the like. That is, the lower support body 93 has a spring force that presses the upper pump body 20 toward the anti-lid member side.
A space 100 is continuously formed in the circumferential direction between the cylindrical portion 62 of the lid member 60 and the pulsation damper main body 71. The fuel reaches the upper diaphragm 72 and the lower diaphragm 73 via the space 100. Therefore, the fluid resistance of the fuel chamber 63 is reduced, and the pulsation damper 70 can exhibit a high pulsation damping effect.

Next, the operation of the high-pressure pump 1 will be described.
(I) Suction stroke When the plunger 10 is lowered from the top dead center toward the bottom dead center by the rotation of the camshaft, the volume of the pressurizing chamber 110 increases and the fuel is depressurized. The discharge valve member 53 of the discharge unit 50 is seated on the discharge valve valve seat 56 and closes the fuel outlet 55. At this time, since energization to the coil 42 is stopped, the movable core 43 and the needle 49 are moved to the pressurizing chamber side by the urging force of the second spring 38. As a result, the needle 49 presses the suction valve member 33, and the valve open state is maintained in a state where the suction valve member 33 is in contact with the first spring holder 34. As a result, fuel is sucked from the fuel chamber 63 into the pressurizing chamber 110 via the communication passage 24, the suction chamber 311 and the suction hole 111.
In the intake stroke, the volume of the variable volume chamber decreases as the plunger 10 descends. Therefore, the fuel in the variable volume chamber is sent to the fuel chamber 63.

(II) Metering stroke When the plunger 10 rises from the bottom dead center toward the top dead center due to the rotation of the camshaft, the volume of the pressurizing chamber 110 decreases. At this time, energization to the coil 42 is stopped until a predetermined time, and the intake valve member 33 is in an open state. For this reason, the low-pressure fuel once sucked into the pressurizing chamber 110 is returned to the fuel chamber 63 via the communication path 24 and the like.
In the metering stroke, the volume of the variable volume chamber increases as the plunger 10 moves up. Therefore, the fuel in the fuel chamber 63 is sucked into the variable volume chamber.

  Magnetic energizing force is generated between the fixed core 41 and the movable core 43 by starting energization of the coil 42 at a predetermined time while the plunger 10 is rising. When this magnetic attractive force becomes larger than the force obtained by subtracting the urging force of the first spring 35 from the urging force of the second spring 38, the movable core 43 and the needle 49 move to the fixed core 41 side, and the needle 49 against the suction valve member 33. The pressing force of is released. As a result, the suction valve member 33 is seated on the suction valve valve seat 36 by the biasing force of the first spring 35 and is opened.

(III) Pressurization stroke After the suction valve member 33 is closed, the fuel pressure in the pressurizing chamber 110 increases as the plunger 10 rises. When the force that the pressure of the fuel on the pressurizing chamber side acts on the discharge valve member 53 becomes larger than the resultant force of the force that the pressure of the fuel on the fuel outlet 55 side acts on the discharge valve member 53 and the urging force of the discharge valve spring 57. The discharge valve member 53 is opened. Thereby, the fuel pressurized in the pressurizing chamber 110 is discharged from the fuel outlet 55.
Note that energization of the coil 42 is stopped during the pressurization stroke. Since the force that the fuel pressure of the pressurizing chamber 110 acts on the suction valve member 33 is larger than the urging force of the second spring 38, the suction valve member 33 maintains the closed state.
As described above, the high-pressure pump 1 repeats the intake stroke, the metering stroke, and the pressurization stroke, and pressurizes and discharges an amount of fuel necessary for the internal combustion engine.

Next, displacement and stress generated in the pulsation damper main body 71 will be described.
FIG. 6A shows the displacement of the lower diaphragm 73 of the pulsation damper main body 71, and FIG. 6B shows the stress generated in the lower diaphragm 73 at that time.
The solid line on the left side of time t0 in FIG. 6A shows a state where the vehicle engine is stopped and the high-pressure pump 1 is not operating (hereinafter referred to as “non-operating state”). Since the swelling of the lower diaphragm 73 is restricted by the lower cover portion 92, the distance between the center of the outer end face of the lower diaphragm 73 and the virtual plane S is d3 in the non-operating state.
A broken line C on the left side of time t0 in FIG. 6A indicates the distance between the center of the outer end face of the lower diaphragm of the conventional pulsation damper main body not provided with the cover portion and the virtual plane S.
From time t0 to time t1, the high-pressure pump 1 shifts from the non-operating state to the operating start state. At this time, as the fuel pressure in the fuel chamber 63 increases, the lower diaphragm 73 and the upper diaphragm 72 are displaced toward each other, and the distance between the center and the virtual plane S is reduced to d4. At this time, the displacement width of the lower diaphragm 73 is A (d3-d4).
After the time t1, the high-pressure pump 1 is in an operating state. At this time, the lower diaphragm 73 and the upper diaphragm 72 repeat the operation of approaching and moving away from each other due to the fuel pressure pulsation of the fuel chamber 63. For this reason, the distance between the center of the lower diaphragm 73 and the virtual plane S varies within a certain range. At this time, the displacement width of the lower diaphragm 73 is B.

In FIG. 6B, the stress generated in the lower diaphragm 73 when the distance between the center and the virtual plane S is larger than d4 is shown on the positive side (+) of the vertical axis, and the distance between the center and the virtual plane S is d4. The stress generated in the lower diaphragm 73 when it is smaller than that is shown on the negative side (−) of the vertical axis.
Since the swelling of the lower diaphragm 73 is restricted to d3 by the lower cover portion 92, the stress generated in the lower diaphragm 73 in the non-operating state is σ1. When the operation state is shifted from the non-operation state to the operation start state, the stress generated in the lower diaphragm 73 becomes zero. At this time, the stress change of the lower diaphragm 73 is A (σ1-0).
When the operating state is reached after time t1, the stress generated in the lower diaphragm 73 varies in a certain range E.
The broken line F on the left side of time t0 in FIG. 6B indicates the stress generated in the lower diaphragm of the conventional pulsation damper main body not provided with the cover portion.
The displacement and stress of the upper diaphragm 72 are generated similarly to the displacement and stress of the lower diaphragm 73.
The lower diaphragm 73 and the upper diaphragm 72 are subjected to stress changes when the cover portions 82 and 92 of the upper and lower support members 80 and 90 are shifted from the non-operating state to the operation starting state and when the operating state is shifted to the non-operating state. Has been reduced.

In the present embodiment, the following effects are obtained.
(1) In the present embodiment, the annular portions 81 and 91 of the upper and lower support members 80 and 90 are formed in an annular shape in parallel with the peripheral portions 74 and 75 of the upper and lower diaphragms 72 and 73, and the peripheral edges of the upper and lower diaphragms 72 and 73. Together with the portions 74 and 75, the entire circumference is joined by laser welding. The annular portions 81 and 91 increase the rigidity of the peripheral portions 74 and 75, and the peripheral portion 74 of the upper diaphragm 72 and the peripheral portion 75 of the lower diaphragm 73 are suppressed from being displaced away from each other. Therefore, it is possible to reliably suppress the stress from being repeatedly applied to the joint portions 77 of the peripheral portions 74 and 75 of the upper and lower diaphragms 72 and 73 due to the stress amplitude of the pulsation damper main body 70.
(2) In the present embodiment, the pulsation damper main body 71, the upper support member 80, and the lower support member 90 are configured as subassemblies, thereby reducing the number of steps for assembling the pulsation damper 70 into the fuel chamber 63. Can do.
(3) In this embodiment, the lower support member 93 of the lower support member 90 is locked to the outer wall of the convex portion 19 of the cylinder portion 11. Thereby, the movement of the pulsation damper 70 in the radial direction is reliably suppressed. Therefore, the pulsation damper main body 71 can be easily and reliably positioned in the fuel chamber.
(4) In the present embodiment, a hole obtained by cutting the upper support 83 from the first plate member that is the basis of the upper support member 80 becomes the fuel passage 85. Further, a hole formed by cutting the lower support 93 from the second plate material that is the base of the lower support member 90 becomes the fuel passage 95. Thus, the fuel passages 85 and 95 are formed simultaneously with the provision of the upper support 83 and the lower support 93 on the upper support member 80 or the lower support member 90 without processing the pump body 20 or the lid member 60. Can do. Therefore, the manufacturing process of the upper support member 80 and the lower support member 90 is simplified, and the manufacturing cost can be reduced.
(5) In the present embodiment, the upper and lower cover portions 82 and 92 of the upper and lower support members 80 and 90 that support the pulsation damper main body 71 are restricted from expanding the upper and lower diaphragms 72 and 73 away from each other. For this reason, the stress amplitude of the pulsation damper 70 is reduced, and the repeated application of stress to the joint portions 77 of the peripheral portions 74 and 75 of the upper and lower diaphragms 72 and 73 is suppressed. Therefore, the service life of the pulsation damper 70 can be extended.
(6) In this embodiment, since the upper support 83 that contacts the lid member 60 is connected to the upper cover portion 82, the displacement of the upper cover portion 82 is suppressed. Therefore, the upper cover portion 82 can reliably prevent the movable portion 78 of the upper diaphragm 72 from being displaced toward the lid member. Further, since the lower support body 93 that contacts the upper pump body 20 is connected to the lower cover portion 92, the displacement of the lower cover portion 92 is suppressed. Therefore, the lower cover portion 92 can reliably prevent the movable portion 79 of the lower diaphragm 73 from being displaced toward the pump body.
(7) In the present embodiment, the upper annular portion 81, the upper cover portion 82, and the upper support body 83 are integrally formed, and the lower annular portion 91, the lower cover portion 92, and the lower support body 93 are integrally formed. Thus, the pulsation damper 70 can be attached to the fuel chamber 63 with a simple configuration, and the service life of the pulsation damper 70 can be extended. Moreover, the manufacturing cost of the pulsation damper 70 can be reduced without increasing the number of parts.

(Second Embodiment)
A high-pressure pump according to a second embodiment of the present invention is shown in FIG.
In the second embodiment, the four upper supports 831 included in the upper support member 801 are connected to the upper cover portion 82 on the lid member side of the movable portion 78 of the upper diaphragm 72 and from the position where the upper support member 831 is connected to the upper cover portion 82. It extends in the radial direction. Specifically, the upper support 831 has one end on the outer peripheral side of the upper cover portion 82 (specifically, a position outside the half of the radius of the upper diaphragm 72 and an inside of the bent portion of the upper cover portion 82). And the other end extends to the inner peripheral side of the upper cover portion 82. The upper support 831 includes an inclined portion 89 that is inclined from the upper cover portion 82 and extends toward the bottom side of the lid member 60, and a curved portion 88 that is curved from the end in the radial direction of the inclined portion 89 toward the upper diaphragm side. Have. The inclined portion 89 is in contact with the inner wall of the lid member 60.
The four lower support members 931 included in the lower support member 901 are connected to the lower cover portion 92 on the pump body side of the movable portion 79 of the lower diaphragm 73, and extend radially inward from the position where the lower support member 901 is connected to the lower cover portion 92. Yes. Specifically, the lower support 931 has one end on the outer peripheral side of the lower cover portion 92 (specifically, a position outside the half of the radius of the lower diaphragm 73 and a position inside the bent portion of the lower cover portion 92). And the other end extends to the inner peripheral side of the lower cover portion 92. The lower support 931 includes an inclined portion 99 that is inclined from the lower cover portion 92 and extends toward the bottom side of the lid member 60, and a curved portion 98 that is curved from the radially inner end of the inclined portion 99 toward the lower diaphragm. doing. The inclined portion 99 is in contact with the upper pump body 20, and the curved portion 98 is in contact with the convex portion 19 of the cylinder portion 11.

The four upper supports 831 are formed by bending the fuel passages 84 and 85 of the upper cover portion 82 at the same time as or subsequent to the pressing. A hole formed by cutting out the upper support 831 from the first plate material becomes the fuel passage 85.
The four lower supports 931 are formed by bending the fuel passages 94 and 95 of the lower cover portion 92 at the same time as or subsequent to the pressing. A hole formed by cutting the lower support 931 from the second plate material becomes the fuel passage 95.
The load of the upper support 831 is set according to the material of the upper support 831, the plate thickness, the angle formed by the upper cover portion 82 and the inclined portion 89, and the like. The load of the lower support 931 is set according to the material of the lower support 931, the plate thickness, the angle between the lower cover portion 92 and the inclined portion 99, and the like.
The convex part 19 of the cylinder part 11 is inserted between the four lower supports 931. The lower support 931 is locked to the outer wall in the radial direction of the convex portion 19 of the cylinder portion 11. Thereby, the movement of the pulsation damper 70 in the radial direction is restricted.
Also in the second embodiment, the same operational effects as those of the first embodiment described above can be achieved.

(Third embodiment)
The principal part of the high pressure pump by 3rd Embodiment of this invention is shown in FIG.
In the third embodiment, the upper support member 80 and the lower support member 90 are joined in a state rotated by 45 ° in the circumferential direction. FIG. 8C shows the position of the upper pump body 20 by a one-dot chain line. The four lower supports 93 are in contact with the upper pump body 20 with certainty.
In the third embodiment, for example, when the mounting direction of the upper support member 80 is limited due to conditions such as the inner wall of the lid member 60 being uneven, the pulsation damper 70 is not increased without increasing the width of the upper pump body 20. Can be installed in the fuel chamber.

(Fourth embodiment)
FIG. 9 shows a high-pressure pump according to the fourth embodiment of the present invention, and FIG.
In the fourth embodiment, the cylinder portion 11 does not protrude from the upper pump body 20 to the fuel chamber 63. Instead, the upper pump body 20 is provided with a convex portion 191.
The upper support member 803 includes an upper annular portion 81, an upper cover portion 82, and an upper support body 833. The upper support 833 is in contact with the lid member 60. The upper support 833 presses the lid member 60 to the side opposite to the upper pump body 20 with a predetermined spring force.
The lower support member 90 includes a lower annular portion 91, a lower cover portion 92, and a lower support body 93. The lower support body 93 is in contact with the upper pump body 20 and the convex portion 191 thereof. As a result, the pulsation damper 70 is restricted from moving in the radial direction and is positioned in the fuel chamber 63. The lower support body 93 presses the upper pump body 20 to the side opposite to the lid member 60 with a predetermined spring force.
Also in the present embodiment, a hole obtained by cutting the upper support 833 from the first plate that is the base of the upper support member 803 becomes the fuel passage 85. Further, a hole obtained by cutting the lower support 93 from the second plate material that is the base of the lower support member 90 becomes the fuel passage 95.
In the fourth embodiment, the same operational effects as those of the first to third embodiments described above can be obtained.

(Fifth embodiment)
The principal part of the high pressure pump by 5th Embodiment of this invention is shown in FIG.
In the fifth embodiment, the upper pump body 20 is provided with a recess 192.
The lower support body 93 of the lower support member 90 is in contact with the recess 192 of the upper pump body 20. As a result, the pulsation damper 70 is restricted from moving in the radial direction and is positioned in the fuel chamber 63.
Also in the fifth embodiment, the same operational effects as those of the first to fourth embodiments described above can be achieved.

(Sixth embodiment)
The principal part of the high-pressure pump according to the sixth embodiment of the present invention is shown in FIG.
In the sixth embodiment, a hole 193 is provided in the upper pump body 20.
The lower support 93 of the lower support member 90 has a protrusion 933 at a position corresponding to the hole 193 of the upper pump body 20. When the protrusion 933 of the lower support 93 enters the hole 193 in the upper pump body 20, the pulsation damper 70 is restricted from moving in the radial direction and is positioned in the fuel chamber 63.
In the sixth embodiment, the pulsation damper 70 is positioned at a position (rightward in FIG. 12) that is shifted away from the communication path 24 of the upper pump body 20. Therefore, the space near the communication passage 24 of the fuel chamber 63 is widened. Therefore, the flow coefficient of the fuel flowing from the fuel chamber 63 to the communication passage 24 is increased, and the fuel can easily flow. In addition, the flow coefficient of the fuel flowing from the communication path 24 to the fuel chamber 63 is increased, and the fuel easily flows. Therefore, it is possible to reduce the pressure pulsation of the fuel and improve the suction efficiency from the fuel chamber 63 to the pressurizing chamber 110.

(Seventh embodiment)
The principal part of the high-pressure pump according to the seventh embodiment of the present invention is shown in FIG.
In the seventh embodiment, a communication passage 240 is provided in the pump body 200. The communication path 240 is opened in the inner wall of the fuel chamber 63 located in the radially outward direction of the pulsation damper 70. Even in this case, the pulsation damper 70 is positioned at a position shifted in a direction away from the communication passage 240 of the pump body 200, so that the space in the vicinity of the communication passage 240 of the fuel chamber 63 is widened. Therefore, the flow coefficient of the fuel flowing from the fuel chamber 63 to the communication path 240 is increased, and the fuel can easily flow. In addition, the flow coefficient of the fuel flowing from the communication path 240 to the fuel chamber 63 is increased, and the fuel easily flows. Therefore, it is possible to reduce the pressure pulsation of the fuel and improve the suction efficiency from the fuel chamber 63 to the pressurizing chamber 110.

(Eighth embodiment)
The principal part of the high-pressure pump according to the eighth embodiment of the present invention is shown in FIGS.
In the eighth embodiment, the lower support member 932 of the lower support member 902 includes a foot portion 934, a body contact portion 935, a body locking portion 936, and a protrusion 937.
The foot portion 934 extends from the lower cover portion 92 to the pump body 20 side. The body contact portion 935 extends substantially in parallel with the upper surface of the pump body 20 from the end of the foot portion 934 on the pump body side. The body locking portion 936 extends along the end surface of the pump body 20 in the width direction.
The protrusion 937 is provided in the body locking portion 936 and enters a hole 194 provided in the pump body 20.
Accordingly, the lower support member 902 is locked to the pump body 20 by the lower support body 932, so that the pulsation damper 70 can be attached to the fuel chamber 63.

As shown in FIG. 15, the lower support 932 is formed by a bending process that is performed simultaneously with or subsequent to the pressing process of the second plate material that is the basis of the lower support member 902. In FIG. 15, positions where the legs 934, the body contact portions 935, and the body locking portions 936 of the lower support 932 are bent are indicated by broken lines. A hole formed by cutting the lower support 932 from the second plate material becomes the fuel passage 95.
As shown in FIG. 16, before the lower support 932 is attached to the pump body 20, the body contact portion 935 and the upper surface of the pump body 20 are nonparallel. Therefore, when the lower support 932 is attached to the pump body 20, a spring force that lifts the protrusion 937 is applied, and the protrusion 937 and the hole 194 are securely fixed. Therefore, rattling of the pulsation damper 70 due to manufacturing tolerances of the protrusion 937 and the hole 194 can be prevented.

  In the eighth embodiment, the pulsation damper 70 can be attached to the fuel chamber 63 by locking only the lower support 932 of the lower support member 902 to the pump body 20. Therefore, the pulsation damper 70 can be attached to the fuel chamber with a simple configuration. In addition, the size of the lower support 932 can be reduced, and the fuel flow in the fuel chamber 63 can be improved.

(Ninth embodiment)
The principal part of the high-pressure pump according to the ninth embodiment of the present invention is shown in FIGS.
In the ninth embodiment, the body locking portion 936 of the lower support 932 is divided into three. The three central portions 938 bend greatly into the hole 194 of the pump body 20 and are locked in the hole 194. Both side portions 939 of the body locking portion 936 divided into three prevent the lower support 932 from tilting.

(10th Embodiment)
The principal part of the high-pressure pump according to the tenth embodiment of the present invention is shown in FIGS.
In the tenth embodiment, a lower support body 940 of the lower support member 903 is provided on the lower cover portion 92. The lower support 940 extends parallel to the end surface of the pump body 20 in the width direction. A protrusion 937 provided on the lower support 940 enters the hole 194 of the pump body 20. Thereby, the pulsation damper 70 is attached to the fuel chamber 63.
In FIG. 15, the position at which the lower support 940 is bent is indicated by a broken line. A hole obtained by cutting the lower support 940 from the second plate material becomes the fuel passage 95. Further, the lower support 940 is provided with a fuel passage 951. The fuel in the fuel chamber 63 can flow through the fuel passage 951.

(Eleventh embodiment)
The principal part of the high pressure pump by 11th Embodiment of this invention is shown in FIG.
In the eleventh embodiment, three lower support members 941 of the lower support member 904 are provided on each end surface of the pump body 20. A protrusion 937 provided on the lower support 941 enters the hole 194 of the pump body 20. Thereby, the pulsation damper 70 is attached to the fuel chamber 63.
In FIG. 19, the position at which the lower support 941 is bent is indicated by a broken line. A hole formed by cutting out the lower support 941 from the second plate material becomes the fuel passage 95. A fuel passage is also formed between each lower support 941 and the lower support 941. The fuel in the fuel chamber 63 can flow through this fuel passage.

(Twelfth embodiment)
The principal part of the high-pressure pump according to the twelfth embodiment of the present invention is shown in FIGS.
In the twelfth embodiment, the corners of the pump body 20 where the lower support member 942 of the lower support member 905 is locked are cut out obliquely. By fitting the lower support body 942 into the notch 201, the pulsation damper 70 is prevented from being displaced in the longitudinal direction of the pump body 20.
Of the plurality of lower supports 942, at least one lower support 942 corresponding to the notch 201 of the pump body 20 may be provided on one end surface in the width direction of the pump body 20.
Further, before the lower support 942 is attached to the pump body 20, the notch 201 of the pump body 20 and the lower support 942 are non-parallel. Therefore, when the lower support 942 is attached to the pump body 20, a spring force that lifts the protrusion 937 is applied, and the protrusion 937 of the lower support 942 and the hole 194 of the pump body 20 are securely fixed. Therefore, rattling of the pulsation damper 70 can be prevented.

(13th Embodiment)
The principal part of the high-pressure pump according to the thirteenth embodiment of the present invention is shown in FIGS.
In the thirteenth embodiment, the lower support member 906 includes an elastic portion 950 having a spring force that presses the pump body 20. As shown in FIG. 27, the elastic portion 950 is cut out from the second plate material together with the other lower support body 941.
The elastic part 950 lifts the pulsation damper 70 toward the lid member, so that the protrusion 937 of the lower support 941 and the hole 194 of the pump body 20 are securely fixed. Therefore, rattling of the pulsation damper 70 can be prevented.

(14th Embodiment)
The principal part of the high-pressure pump according to the fourteenth embodiment of the present invention is shown in FIGS.
In the fourteenth embodiment, the fuel passage 951 is formed in the lower support 940 of the tenth embodiment, and at the same time, the plate material at the location where the fuel passage 951 is provided is used as the elastic portion 952. The elastic portion 952 abuts on the upper surface of the pump body 20 and has a spring force that presses the pump body 20. The elastic portion 952 lifts the pulsation damper 70 toward the lid member, so that the protrusion 937 of the lower support 940 and the hole 194 of the pump body 20 are securely fixed. Therefore, rattling of the pulsation damper 70 can be prevented.

(Fifteenth embodiment)
The principal part of the high-pressure pump according to the fifteenth embodiment of the present invention is shown in FIGS.
In the fifteenth embodiment, an annular groove 195 is provided in the pump body 200. The inner circumferential wall 196 in the radial direction of the groove 195 is tapered in a radial inner direction from the bottom side toward the lid member side.
A plurality of lower supports 943 provided radially on the lower support member 908 extend from the inner diameter side to the outer diameter side, and fit into the inner peripheral wall 196 of the groove 195.
When the lower support 943 is fitted into the groove 195 of the pump body 200, as shown in FIGS. 32 and 33, the plurality of lower supports 943 are radially inward by the end surface of the inner peripheral wall 196 of the groove 195 on the lid member side. Pressed. Thereafter, when the lower support body 943 further moves to the bottom side of the groove 195, as shown in FIG. 34, the plurality of lower support bodies 943 are opened radially outward by their own elastic force at the bottom part of the groove 195, 195 is locked to the inner peripheral wall 196.
Thus, the pulsation damper 70 is attached to the pump body 200 by the lower support member 943 of the lower support member 908.

(Sixteenth embodiment)
The principal part of the high-pressure pump according to the sixteenth embodiment of the present invention is shown in FIG.
In the sixteenth embodiment, the upper support member 804 includes only the upper annular portion 81. Rigidity is increased by the upper annular portion 81 of the upper support member 804 and the lower annular portion 91 of the lower support member 902, and stress due to the displacement of the diaphragms 72, 73 is prevented from acting on the welds 77 of the peripheral portions 74, 75. . Therefore, it is not necessary to press the peripheral portions 74 and 75 of the diaphragms 72 and 73 from above and below. Therefore, the pulsation damper 70 can be attached to the fuel chamber 63 by locking only the lower support 932 extending from the lower annular portion 91 of the lower support member 902 to the pump body 20.

(17th Embodiment)
The principal part of the high-pressure pump according to the seventeenth embodiment of the present invention is shown in FIGS.
FIG. 37 shows the pump body 20 as viewed from above before the pulsation damper 70 is attached.
The pump body 20 has an extruded shape or a drawn shape whose cross section perpendicular to the longitudinal direction is substantially constant. The pump body 20 includes a pump body main body 220, a first flange portion 221 and a second flange portion 222. The first flange portion 221 protrudes from the pump body main body 220 in the width direction. The second flange portion 222 protrudes from the first flange portion 221 in the width direction. The second flange portion 222 has a notch 223 at a position corresponding to the lower support 944 of the lower support member 909.
The lower support body 944 of the lower support member 909 is locked to the first flange portion 221 via the notch portion 223 of the second flange portion 222. The lower support 944 is restricted from moving in the longitudinal direction of the pump body 20 by the notch 223.
Further, the lower support member 909 has an elastic portion 952. The elastic portion 952 has a spring force that presses the pump body 20. The elastic portion 952 lifts the pulsation damper 70 toward the lid member, so that the lower support 944 and the first flange portion 221 of the pump body 20 are securely fixed. Therefore, rattling of the pulsation damper 70 can be prevented.

(Eighteenth embodiment)
The main part of the high-pressure pump according to the eighteenth embodiment of the present invention is shown in FIGS.
In the eighteenth embodiment, the lower support member 910 includes a lower cylinder part 945 and an arm part 946 extending from the lower cylinder part 945 in the circumferential direction and the radially outward direction. The arm portion 946 is cut out from the lower tube portion 945 and bent outward in the radial direction. The arm portion 946 extends obliquely toward the lid member side.
The arm portion 946 of the lower support member 910 is engaged with a groove portion 250 provided on the inner wall of the pump body 200 located in the radially outward direction of the pulsation damper 70.
The arm portion 946 of the lower support member 910 has a spring force that presses the groove portion 250 of the pump body 200 toward the lid member. Therefore, the lower cylinder portion 945 of the lower support member 910 is pressed against the pump body 200 that is the bottom of the fuel chamber 63. Therefore, rattling of the pulsation damper 70 due to manufacturing tolerances of the arm portion 946 and the groove portion 250 can be prevented.

(Nineteenth embodiment)
The main part of the high-pressure pump according to the nineteenth embodiment of the present invention is shown in FIG.
In the nineteenth embodiment, the curvature radius of the arm portion 947 is larger than the curvature radius of the lower tube portion 945. The curvature radius of the arm portion 947 is substantially the same as the curvature radius of the groove portion 250 of the pump body 200. Even this configuration has the same effects as the eighteenth embodiment.

(20th embodiment)
The principal part of the high-pressure pump according to the twentieth embodiment of the present invention is shown in FIG.
In the twentieth embodiment, the curvature radius of the arm portion 948 is smaller than the curvature radius of the groove portion 250 of the pump body 20 and smaller than the curvature radius of the lower tube portion 945. Even this configuration has the same effects as the eighteenth embodiment.

(21st Embodiment)
The principal part of the high-pressure pump according to the twenty-first embodiment of the present invention is shown in FIG.
In the twenty-first embodiment, the arm portion 949 of the lower support member 911 extends perpendicular to the central axis of the lower tube portion 945.
Further, the lower support member 911 has an elastic portion 953 on the pump body side. The elastic portion 953 abuts on the pump body 20 and has a spring force that presses the pump body 20. As a result, the arm portion 949 of the lower support member 911 is pressed against the end surface of the groove portion 250 of the pump body 200 on the lid member side. Therefore, rattling of the pulsation damper 70 can be prevented.

(Twenty-second embodiment)
The principal part of the high-pressure pump according to the twenty-second embodiment of the present invention is shown in FIG.
In the twenty-second embodiment, a groove portion 251 is provided on the inner wall of the lid member 60 located in the radially outward direction of the pulsation damper 70. The arm portion 946 of the lower support member 910 is locked to the groove portion 251 of the lid member 60. The arm portion 946 of the lower support member 910 has a spring force that presses the groove portion 251 of the lid member 60 toward the anti-pump body side. Therefore, the lower cylinder portion 945 of the lower support member 910 is pressed against the pump body 20 that is the bottom of the fuel chamber 63. Therefore, rattling of the pulsation damper 70 can be prevented.

(23rd Embodiment)
The principal part of the high-pressure pump according to the twenty-third embodiment of the present invention is shown in FIG.
In the twenty-third embodiment, the arm portion 949 of the lower support member 911 is locked to the groove portion 251 of the lid member 60.
The lower support member 911 has an elastic portion 953 on the pump body side. By the elastic portion 953, the arm portion 949 is pressed against the end surface of the groove portion 251 of the lid member 60. Therefore, rattling of the pulsation damper 70 can be prevented.

(24th Embodiment)
The principal part of the high-pressure pump according to the twenty-fourth embodiment of the present invention is shown in FIG.
In the twenty-fourth embodiment, a ring 300 is provided on the pump body side of the arm portion 949 of the lower support member 911. The ring 300 is press-fitted and fixed in the groove 251 of the lid member 60. Thereby, the arm portion 949 of the lower support member 911 is fixed to the groove portion 251. A gap is provided between the lower cylinder portion 945 of the lower support member 911 and the pump body 20, and fuel can flow through the gap.

(Other embodiments)
In the above-described eighth to twenty-fourth embodiments, the lower support extending from the lower annular portion of the lower support member of the pulsation damper is configured to be locked in the groove or hole of the pump body or the groove of the lid member. . On the other hand, in another embodiment, the upper support extending from the upper annular portion of the upper support member of the pulsation damper is configured to be locked in a groove or a hole provided in the lid member or a groove of the pump body. May be.
The present invention is not limited to the above-described embodiment. In addition to combining the above-described plurality of embodiments, the present invention can be implemented in various forms without departing from the spirit of the invention.

71 ... Pulsation damper main body 72 ... Upper diaphragm 73 ... Lower diaphragm 74, 75 ... Peripheral parts 80, 801, 803, 804 ... Upper support member 81 ... Upper annular part 83, 831, 833 ... Upper support (support)
90, 901-911 ... lower support member 91 ... lower annular portion 93, 931, 932, 940-944 ... lower support (support)

Claims (11)

A plunger (10) reciprocally movable in the axial direction;
A supply part (30) for supplying fuel to a pressurizing chamber (110) formed in a cylinder part (11) for accommodating the plunger so as to be able to reciprocate, and a fuel pressurized in the pressurizing chamber are discharged. A pump body (20) having a discharge part (50);
A lid member (60) covering the pump body and forming a fuel chamber (63) communicating with the supply section;
The peripheral portion (74) of the upper diaphragm (72) and the peripheral portion (75) of the lower diaphragm (73) are joined together, and a gas having a predetermined pressure is sealed between the upper diaphragm and the lower diaphragm. A pulsation damper main body (71) for reducing pressure pulsation in the fuel chamber,
An upper support member (80, 801, 803, 804) having an annular upper annular portion (81) joined to the peripheral portion of the upper diaphragm;
A lower support member (90, 901-911) having an annular lower annular portion (91) joined to the peripheral portion of the lower diaphragm;
A support body (83, 831, 833, 93, 931, 932, 940-944) extending from at least one of the upper annular portion and the lower annular portion and locked to the pump body or the lid member; A high-pressure pump (1) comprising:   The upper annular part, the peripheral part of the upper diaphragm, the peripheral part of the lower diaphragm, and the lower annular part are formed in parallel and are continuously joined in the circumferential direction. High pressure pump.   The said lower support member or said upper support member is formed from the same board | plate material as the said support body, and the location which cut out the said support body from the board | plate material becomes a fuel channel | path (85, 95, 951), The high pressure pump according to 1 or 2. The support has protrusions (933, 937),
The high pressure according to any one of claims 1 to 3, wherein the pump body or the lid member has holes (193, 194) into which the protrusions of the support body can be fitted. pump.   5. The high-pressure pump according to claim 4, wherein the pump body has an extrusion shape or a drawing shape in which a cross section perpendicular to a longitudinal direction is substantially constant, and the hole is provided in an end surface in a width direction.   The high pressure pump according to claim 5, wherein the lower support member has an elastic portion (950, 952) having a spring force that presses the pump body toward the side of the cover member. The pump body has an annular groove (195) that decreases in a taper shape radially inward from the bottom side toward the lid member side,
The high-pressure pump according to any one of claims 1 to 3, wherein the support body is fitted into the annular groove of the pump body. The pump body has an extruded shape or a drawn shape whose cross section perpendicular to the longitudinal direction is substantially constant, a pump body main body (220), a first flange portion (221) protruding in the width direction from the pump body main body, and the A second flange portion (222) protruding in the width direction from the first flange portion;
The second flange portion has a notch (223) at a position corresponding to the support extending from the lower annular portion,
The said support body extended from the said lower annular part is latched by the said 1st flange part via the said notch part of the said 2nd flange part, The Claim 1 characterized by the above-mentioned. The high-pressure pump described. The lower support member has a lower cylinder part (945) and arm parts (946, 947, 948, 949) extending radially outward from the lower cylinder part,
The said arm part is latched by the groove part (250,251) provided in the said cover member or the said pump body located in the radial direction of the said pulsation damper, The any one of Claims 1-3 characterized by the above-mentioned. The high pressure pump according to claim 1.   The high-pressure pump according to claim 9, wherein the arm portion has a spring force that urges the pulsation damper main body toward the anti-lid member.   The high-pressure pump according to claim 9, further comprising a ring (300) that is press-fitted into the groove portion of the lid member or the pump body and fixes the arm portion of the lower support member.

Images