JP2011220197A - Damper unit and high-pressure pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damper unit having improved strength of a damper member and suppressing a direct action of dynamic pressure of a fuel on the damper member, and capable of sufficiently suppressing pulsation.SOLUTION: The damper unit 32 includes a damper member 35 and a support member 36. On a circumference edge of the damper member 35, a separation section 37 in a shape of expanding upward and downward is formed, and further a welded section 38 is formed in such a manner that damper plates are again bent from the separation section 37 into directions to be closer to each other and butt-welded. The support member 36 includes a base section 40, a pinching section 41 pinching the separation section 37, an assembling section 42 engaged with a concave 31b of a sidewall of a fuel gallery 31, a bypass section 43 forming a bypass passage 47, and a passage section 44 forming a fuel passage 48.

Description

  The present invention relates to a high-pressure pump used in an internal combustion engine (hereinafter referred to as “engine”).

  A high-pressure pump used for an engine includes a plunger that reciprocates by rotation of a camshaft. The operation of the high-pressure pump is specifically the intake stroke in which fuel is sucked from the fuel gallery in the pump into the pressurizing chamber when the plunger moves from top dead center to bottom dead center, and the plunger moves from bottom dead center to top dead center. The fuel in the pressurizing chamber is pressurized by the metering process for returning a part of the low-pressure fuel from the pressurizing chamber to the fuel gallery and the plunger toward the top dead center after closing the metering valve. It is roughly divided into the pressurization stroke.

  Here, when the plunger operates, pulsation due to fuel pressure occurs. For example, when the engine rotates at a high speed and the camshaft rotates at a high speed, the plunger reciprocates at a high speed. Here, “high-speed rotation” means “a state in which the number of rotations per unit time is high”. As a result, the change in the fuel pressure inside the fuel gallery becomes extremely large, resulting in large pulsations. Note that the pulsation does not depend only on the engine speed but can occur due to various factors.

  Such pulsation propagates to a fuel inlet or the like that opens in the fuel gallery, causing abnormal noise or piping vibration. Therefore, conventionally, a high-pressure pump has been proposed in which a damper member called a pulsation damper is disposed in the fuel gallery to attenuate pulsation (see, for example, Patent Documents 1 and 2). This type of damper member is formed, for example, by welding a peripheral portion of a metal diaphragm. At this time, “garbage bonding” is generally performed in which peripheral portions protruding in the radial direction are overlapped and welded in the vertical direction.

  In order to suppress the above-described pulsation, a high-pressure pump having a volume chamber that changes in volume with a change in volume of the pressurizing chamber has been proposed (see, for example, Patent Document 3). By providing the volume chamber, part of the volume change in the fuel gallery is covered, and pulsation is suppressed.

JP 2004-138071 A Japanese Patent No. 4036153 JP 2008-286144 A

  By the way, if the peripheral edge is "garbage bonding", when a force is applied in the direction to separate the two diaphragms, there are minute cracks in the bonded part, and stress tends to concentrate, and cracks are likely to occur. There is a problem that it is easy to extend. For this reason, in the conventional technology, the periphery of the damper member is sandwiched from above and below, and the joining portion is protected so that the joining portion does not contact other members.

  However, when the clamping structure as described above is employed, the structure of the lid is limited because the fuel gallery is pressed with a lid, a press-fitting member, an elastic member, or the like in order to clamp with a sufficient load. Further, when the damper member is sandwiched from above and below, if the upper contact position and the lower contact position of the damper member are shifted, the position where the load acts on the damper is shifted, and the damper member is damaged. It can be. In addition, if a structure that protects the joint portion is taken, the physique in the radial direction may increase.

  In addition to these problems, in the structure in which the volume chamber is provided to suppress pulsation, it is necessary to devise a technique that prevents the fuel discharged from the volume chamber from directly colliding with the diaphragm. This is because the dynamic pressure of the fuel may hinder the movement of the diaphragm. In this regard, in Patent Document 3 described above, the dynamic pressure of the fuel is suppressed by the support structure of the damper member, but as a result, there is a problem that the support structure becomes large.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to improve the strength of the damper member and to suppress pulsation by suppressing the dynamic pressure of the fuel from directly acting on the damper member. An object of the present invention is to provide a damper unit capable of sufficiently suppressing the above.

  The damper unit according to claim 1, which has been made to achieve the above-described object, is used by being installed in a housing of a high-pressure pump that pressurizes and discharges fuel of an automobile, for example. At this time, the housing includes a pressurizing chamber in which fuel is pressurized, a pressurizing side passage, a variable volume chamber whose volume changes with a change in volume of the pressurizing chamber, and a volume side passage.

  The pressurizing side passage connects from the pressurizing chamber to the fuel gallery and opens to the fuel gallery. On the other hand, the volume side passage connects from the variable volume chamber to the fuel gallery and opens to the fuel gallery.

  Here, the variable volume chamber changes the volume opposite to that of the pressurizing chamber in synchronization with the volume change of the pressurizing chamber. With this configuration, in the suction stroke, when the volume of the pressurizing chamber increases, the volume of the variable volume chamber decreases, and a part of the fuel sucked into the pressurizing chamber is covered by the variable volume chamber. On the other hand, in the metering process, when the volume of the pressurizing chamber decreases, the volume of the variable volume chamber increases, and a part of the fuel discharged from the pressurizing chamber to the fuel gallery is covered by the variable volume chamber.

  Here, in particular, the damper member has a separation portion and a welding portion on the periphery of the diaphragm. Here, the separation portion is a portion where the diaphragm is separated in the vertical direction. Moreover, a welding part is a part welded in the aspect which is bend | folded in the proximity | contact direction from a separation | spacing part, and abuts. That is, the peripheral edge of the diaphragm is abutted by creating a part where the upper and lower diaphragms are separated and bending it in the proximity direction. This abutted part becomes a joint part. Therefore, the welded part is a peripheral part including the joint part. Such a welded portion becomes a so-called “butt joint” instead of the conventional “garb joint”, and the strength against tensile stress increases. Therefore, even if a load in a direction away from the diaphragm is applied, the joint portion is not easily damaged. As a result, the strength of the damper member can be improved.

The support member supports such a damper member inside the fuel gallery. The support member has a base part, a clamping part, an assembly part, and a bypass part.
Here, the clamping unit clamps the separation unit. The assembly part is assembled to the inner wall of the fuel gallery. The bypass portion provided in the base portion forms a bypass passage having one end opened around the opening of the pressure side passage and the other end opened around the opening of the volume side passage.

  Conventionally, in order to sandwich the peripheral portion that is “garbage bonding”, for example, a cylindrical support member is sandwiched from above and below, and the peripheral portion is pressed by attaching a lid or the like. It was.

  On the other hand, in the present invention, the peripheral edge of the damper member is “butt joint”, so that the support member is composed of a clamping portion that clamps the separation portion and an assembly portion for the fuel gallery. In addition, a bypass passage is formed by a bypass portion provided in the base portion.

  In this way, in the suction stroke, part of the fuel sucked into the pressurizing chamber is guided from the volume side passage to the pressure side passage through the bypass passage. Therefore, it is possible to suppress the dynamic pressure of the fuel discharged from the volume side passage from acting on the damper member. On the other hand, in the metering process, part of the fuel discharged from the pressurizing chamber to the fuel gallery is guided from the pressurizing side passage to the volume side passage through the bypass passage. Therefore, it is possible to suppress the fuel discharged from the pressure side passage from flowing directly into the fuel inlet. As a result, pulsation can be sufficiently suppressed.

  By the way, as shown in claim 2, the holding part is exemplified to have a resin support part that is integrally formed with the base part and supports the separation part, and a clip part that holds the separation part on the support part. Here, a support part is good also as what supports the perimeter of a damper member, and good also as what supports multiple places (for example, 3 places). If it does in this way, the structure of a clamping part will become easy. Note that the clip portion is not necessarily integrated with the base portion.

  At this time, as shown in claim 3, it is exemplified that the clip portion and the assembly portion are formed by bending a single metal member. This is advantageous in that the number of parts is reduced.

  The assembly part is not necessarily integrated with the base part, like the clip part. However, as shown in claim 4, if at least one of the clip portion and the assembly portion is embedded in the base portion so as to protrude from the base portion, the time required for the assembly operation can be shortened. For example, when the clip portion and the assembly portion are integrated as in the above-described configuration, the damper unit is sub-assembled, and this effect is conspicuous.

  In addition, as shown in claim 5, a part of the bypass portion is inserted into the opening of the volume chamber side passage, and directly connects the bypass passage and the volume side passage, and positions the base portion with respect to the fuel gallery. It is conceivable to have a configuration to perform. In this way, it is possible to reliably prevent the dynamic pressure of the fuel discharged from the bypass passage from acting on the damper member. Also, the positioning of the base with respect to the fuel gallery is simplified.

  According to a sixth aspect of the present invention, on the assumption that the housing has a supply side passage that connects the fuel inlet and the fuel gallery and opens to the fuel gallery, one end of the support member opens around the opening of the supply side passage. It is good also as having the channel | path part which forms the fuel channel | path which an other end opens below a damper member.

  One cause of the pulsation is that, in the metering stroke, the fuel discharged from the pressure side passage to the fuel gallery flows into the supply side passage leading to the fuel inlet. By providing the fuel passage that opens around the opening of the supply side passage, it is possible to suppress the fuel from flowing into the supply side passage.

  In addition, as in the above-described bypass portion, such a passage portion is partially inserted into the opening of the supply side passage, and directly connects the fuel passage and the supply side passage. It can be considered that the base is positioned with respect to the fuel gallery. If it does in this way, it can fully control that the fuel discharged from a pressurization side passage flows into a supply side passage. Also, the positioning of the base with respect to the fuel gallery is simplified. Furthermore, according to the eighth aspect, since the other end of the fuel passage is opened in a direction not facing the opening of the pressurization side passage, the fuel discharged from the pressurization side passage is reliably suppressed from flowing into the supply side passage. it can.

  Although the above has been described as an invention of a damper unit, the present invention can also be realized as an invention of a high-pressure pump including a damper unit as shown in claim 9. Even in such a high-pressure pump, the same effect as the above-described damper unit is exhibited.

It is sectional drawing which shows the structure of the high pressure pump of one Embodiment. It is sectional drawing which expands and shows a damper unit. It is a fragmentary sectional view which shows the structure of a damper member. It is a fragmentary sectional view of the damper unit of another embodiment. It is a fragmentary sectional view which shows the structure of the damper member of another embodiment.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings. The high-pressure pump of this embodiment is used by being mounted on a vehicle, pressurizes the fuel pumped up from the fuel tank by the low-pressure pump and supplied from the fuel inlet, and supplies it to the fuel rail to which the injector is connected. A pipe from the low pressure pump is connected to the upstream side of the fuel inlet.

  As shown in FIG. 1, the high-pressure pump 1 includes a main body unit 10, a fuel supply unit 30, a metering valve unit 50, a plunger unit 70, and a discharge valve unit 90.

The main body 10 has a housing 11 that forms an outer shell. A fuel supply unit 30 is formed in a part of the housing 11 (upper part in FIG. 1).
Moreover, the plunger part 70 is provided in the exact opposite side (lower part in FIG. 1) of the fuel supply part 30. FIG. A pressurizing chamber 12 capable of pressurizing fuel is formed near the middle between the plunger unit 70 and the fuel supply unit 30.
Furthermore, a metering valve unit 50 (left part in FIG. 1) and a discharge valve part 90 (right part in FIG. 1) are provided in a direction orthogonal to the arrangement direction of the fuel supply unit 30 and the plunger unit 70. Yes.

  Next, the configuration of the fuel supply unit 30, the metering valve unit 50, the plunger unit 70, and the discharge valve unit 90 will be described in detail.

  The fuel supply unit 30 includes a fuel gallery 31. The fuel gallery 31 is a space surrounded by the concave portion 13 and the lid portion 14 of the housing 11. A damper unit 32 is disposed in the fuel gallery 31. The damper unit 32 includes a circular damper member 35 formed by joining two metal diaphragms 33 and 34, and a support member 36.

Next, the plunger part 70 will be described.
As shown in FIG. 1, the plunger unit 70 includes a plunger 71, an oil seal holder 72, a spring seat 73, a plunger spring 74, and the like.

  The plunger 71 has a large-diameter portion 711 supported by a cylinder 16 formed inside the housing 11 and a small-diameter portion 712 having a smaller outer diameter than the large-diameter portion 711. The small diameter portion 712 is surrounded by the oil seal holder 72. The large diameter portion 711 and the small diameter portion 712 are integrated and reciprocate in the axial direction.

  The oil seal holder 72 is disposed at the end of the cylinder 16 and has a base 721 located on the outer periphery of the small diameter portion 712 of the plunger 71 and a press-fit portion 722 that is press-fitted into the housing 11.

  The base 721 has a ring-shaped seal 723 inside. The seal 723 includes an inner peripheral Teflon ring (“Teflon” is a registered trademark) and an outer peripheral O-ring. By this seal 723, the thickness of the fuel oil film around the small diameter portion 712 of the plunger 71 is adjusted, and fuel leakage to the engine is suppressed.

  In addition, the base 721 has an oil seal 725 at the tip. The oil seal 725 regulates the thickness of the oil film around the small diameter portion 712 of the plunger 71, thereby suppressing oil leakage.

  The press-fitting portion 722 is a portion that protrudes in a cylindrical shape around the base portion 721, and the cylindrical portion has a U-shaped longitudinal section. On the other hand, a recess 17 corresponding to the press-fit portion 722 is formed in the housing 11. As a result, the oil seal holder 72 is press-fitted in such a manner that the press-fitting portion 722 is pressed against the radially inner wall of the recess 17.

  The spring seat 73 is disposed at the end of the plunger 71. The end of the plunger 71 abuts on a tappet (not shown). The tappet makes its 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. As a result, the plunger 71 reciprocates in the axial direction.

  One end of the plunger spring 74 is locked to the spring seat 73, and the other end is locked to the deep portion of the press-fit portion 722 of the oil seal holder 72. Thereby, the plunger spring 74 functions as a return spring of the plunger 71 and urges the plunger 71 to contact the tappet.

  With this configuration, the reciprocating movement of the plunger 71 according to the rotation of the camshaft is realized. At this time, a volume change of the pressurizing chamber 12 is created by the large diameter portion 711 of the plunger 71.

  In this embodiment, in particular, a variable volume chamber 75 is formed around the small diameter portion 712 of the plunger 71. Here, a region surrounded by the cylinder 16 of the housing 11 and the base end surface (step surface with the small diameter portion 712) of the large diameter portion 711 of the plunger 71, the outer peripheral wall of the small diameter portion 712, and the seal 723 of the oil seal holder 72. Is the variable volume chamber 75. Although the seal 723 suppresses fuel leakage as described above, the seal 723 seals the variable volume chamber 75 in a liquid-tight manner and prevents fuel leak from the variable volume chamber 75 to the engine.

  The variable volume chamber 75 includes a cylindrical cylindrical passage 727 formed between the press-fit portion 722 and the concave portion 17 in the radially inward direction, an annular annular passage 728 formed deep in the concave portion 17, and the housing 11. It is connected to the bottom 31 a of the fuel gallery 31 via the formed volume side passage 18 (passage indicated by a broken line in the figure).

  With this configuration, the variable volume chamber 75 changes the volume opposite to that of the pressurizing chamber 12 in synchronization with the volume change of the pressurizing chamber 12. Therefore, in the suction stroke, when the volume of the pressurizing chamber 12 increases, the volume of the variable volume chamber 75 decreases, and a part of the fuel sucked into the pressurizing chamber 12 is covered by the variable volume chamber 75. On the other hand, in the metering process, when the volume of the pressurizing chamber 12 decreases, the volume of the variable volume chamber 75 increases, and a part of the fuel discharged from the pressurizing chamber 12 to the fuel gallery 31 is covered by the variable volume chamber 75. Is called.

Next, the metering valve unit 50 will be described.
As shown in FIG. 1, the metering valve unit 50 includes a cylinder part 51 formed by the housing 11, a valve part cover 52 that covers the opening of the cylinder part 51, a connector 53, and the like.
The cylindrical portion 51 is formed in a substantially cylindrical shape, and the inside is a fuel passage 55. A substantially cylindrical seat body 56 is disposed in the fuel passage 55. The seat body 56 has a valve 57 slidably supported therein. The valve 57 is lifted toward the pressurizing chamber 12, and the stopper 61 controls the lift amount of the valve 57. Further, the fuel passage 55 communicates with the fuel gallery 31 via the pressure side passage 58.

  A needle 59 is in contact with the valve 57. The needle 59 passes through the valve cover 52 described above and extends to the inside of the connector 53. The connector 53 includes a coil 531 and a terminal 532 for energizing the coil 531. Inside the coil 531, a fixed core 533, a movable core 534, and a spring 535 interposed between the fixed core 533 and the movable core 534 are disposed. Here, the needle 59 described above is fixed to the movable core 534. That is, the movable core 534 and the needle 59 are integrated.

  With this configuration, when energization is performed via the terminal 532 of the connector 53, a magnetic attractive force is generated between the fixed core 533 and the movable core 534 by the magnetic flux generated in the coil 531. As a result, the movable core 534 moves to the fixed core 533 side, and accordingly, the needle 59 moves in a direction away from the pressurizing chamber 12. At this time, the movement of the valve 57 is not restricted by the needle 59. Therefore, the valve 57 can be seated on the seat body 56, and the fuel passage 55 and the pressurizing chamber 12 are blocked by the seating of the valve 57.

  On the other hand, if energization through the terminal 532 of the connector 53 is not performed, no magnetic attractive force is generated, so that the movable core 534 is moved toward the pressurizing chamber 12 by the spring 535. As a result, the needle 59 moves in a direction approaching the pressurizing chamber 12. As a result, the movement of the valve 57 is regulated by the needle 59, and the valve 57 is held on the pressurizing chamber 12 side. At this time, the valve 57 is separated from the seat body 56, and the fuel passage 55 and the pressurizing chamber 12 communicate with each other.

Next, the discharge valve unit 90 will be described.
As shown in FIG. 1, the discharge valve portion 90 has a cylindrical accommodating portion 91 formed by the housing 11. A discharge valve 92, a spring 93, and a locking portion 94 are accommodated in a storage chamber 911 formed by the storage portion 91. Further, the opening portion of the storage chamber 911 is a discharge port 95. A valve seat is formed in the deep portion of the storage chamber 911 opposite to the discharge port 95.

  The discharge valve 92 contacts the valve seat by the biasing force of the spring 93 and the pressure from the fuel rail (not shown). As a result, the discharge valve 92 stops discharging fuel while the fuel pressure in the pressurizing chamber 12 is low. On the other hand, when the pressure of the fuel in the pressurizing chamber 12 increases and overcomes the biasing force of the spring 93 and the pressure from the fuel rail side, the discharge valve 92 moves toward the discharge port 95. As a result, the fuel that has flowed into the storage chamber 911 is discharged from the discharge port 95.

  The above is the configuration of the high-pressure pump 1, but this embodiment is characterized by the configuration of the above-described damper unit 32. Next, the configuration of the damper unit 32 will be described in detail. As described above, the damper unit 32 includes the damper member 35 and the support member 36.

  As shown in FIG. 2, the damper member 35 has a separating portion 37 having a shape that swells in the vertical direction at the periphery of the diaphragms 33 and 34 that are once approached and separated as they approach the periphery. Moreover, it has the welding part 38 welded in the aspect which bend | folds again in the proximity | contact direction from the spacing part 37, and is faced | matched. The welded portion 38 is a peripheral portion including a joint portion 39 where the diaphragms 33 and 34 are joined to each other.

Here, the structure of the diaphragms 33 and 34 will be described in detail with reference to FIG.
The diaphragms 33 and 34 have operating portions 33a and 34a, concave groove portions 33b and 34b, convex edge portions 33c and 34c, and welded portions 33d and 34d. The diaphragms 33 and 34 are formed by pressing a metal plate having a high elastic modulus that is not affected by corrosive substances.

  The operation portions 33a and 34a serving as the operation regions have a substantially disc-shaped disc portion at the center portion and a curved portion formed around the disc portion, and are formed in a substantially dome shape.

The recessed groove portions 33b and 34b are formed in an arc shape whose longitudinal section is recessed toward the sealed space 300, and are provided annularly on the outer peripheral side of the operating portions 33a and 34a.
The convex edge portions 33c and 34c are formed in an arc shape whose vertical cross section protrudes to the outside of the sealed space 300, and are provided annularly on the outer peripheral side of the concave groove portions 33b and 34b.

  The welded portions 33d and 34d extend so as to be close to each other from the outer peripheral side of the convex edge portions 33c and 34c, and are welded in such a manner that the end portions are butted. Thereby, the joining part 39 is formed.

  At this time, the convex edge parts 33c and 34c form the said separation part 37, and the welding parts 33d and 34d form the said welding part 38 (refer FIG. 2). At this time, the sealed space 300 formed by welding is sealed with a gas having a filling pressure, for example, 300 kPa, which can cope with a pressure that suppresses the generation of vapor generated in the fuel at a minimum fuel pressure necessary for engine operation.

  Note that R1> R2> R3, where R1 is the radius of curvature of the curved surface portions of the operating portions 33a and 34a, R2 is the radius of curvature of the concave groove portions 33b and 34b, and R3 is the radius of curvature of the convex edge portions 33c and 34c. .

  Moreover, if the height of the operation parts 33a and 34a after welding is H1, the height of the recessed groove parts 33b and 34b is H2, and the height of the convex edge parts 33c and 34c is H3, H1> H3> H2. ing. Here, H2> 0 is formed. Thereby, the recessed groove parts 33b and 34b can be elastically deformed in the axial direction.

  Returning to FIG. 2, the support member 36 includes an annular resin base 40 corresponding to the damper member 35, a clamping part 41 that clamps the separation part 37, and a metal assembly part that is assembled to the inner wall of the fuel gallery 31. 42, and a resin bypass portion 43 and a passage portion 44 that are integrally formed with the base portion.

  Here, the annular base 40 is fitted into the bottom 31 a of the fuel gallery 31 and is positioned in the radial direction. The base portion 40 is formed with a plurality of (three in this embodiment) support portions 45 at equal intervals in the circumferential direction. The upper surface of the support portion 45 is a concave surface corresponding to the separation portion 37. Therefore, the support part 45 supports the separation part 37 from below.

  The clip portion 46 sandwiches the separation portion 37 together with the support portion 45. The clip part 46 protrudes upward from the support part 45 (base part 40) so as to correspond to the support part 45. Further, the clip portion 46 is bent substantially vertically inward in the radial direction to form a substantially horizontal portion, and is in contact with the separation portion 37 from above. The tip 46a of the horizontal portion is bent downward and abuts from the radially inner side of the separating portion 37. Further, a part of the base end portion 46 b of the horizontal portion is bent downward and abuts from the radially outer side of the separating portion 37. With this configuration, the support portion 45 and the clip portion 46 restrict the vertical movement of the separation portion 37. Further, the clip portion 46 restricts the radial movement of the separation portion 37.

  The metal assembly portion 42 is formed so as to be bent radially outward from the protruding portion of the clip portion 46. That is, the assembly part 42 is formed integrally with the clip part 46 by bending a single metal member. The assembly portion 42 is engaged with a recess 31 b formed on the side wall of the fuel gallery 31.

  The bypass part 43 forms a bypass passage 47. One end of the bypass passage 47 is connected to the volume side passage 18 by inserting a part of the bypass portion 43 into the volume side passage 18. Thereby, the damper unit 32 is positioned so as not to rotate in the circumferential direction. The other end is opened around the opening of the pressure side passage 58.

  On the other hand, the passage portion 44 forms a fuel passage 48. The fuel passage 48 is connected to the supply side passage 19 having one end connected to the fuel inlet. The other end is opened below the damper member 35. In particular, the other end opens in a direction that does not face the opening of the pressure side passage 58.

As described above in detail, in this embodiment, the damper unit 32 includes the damper member 35 and the support member 36.
Here, on the periphery of the damper member 35, a spaced-apart portion 37 swelled in the vertical direction is formed, and a welded portion 38 that is welded in a manner in which it is bent again from the spaced-apart portion 37 in the proximity direction and is abutted is formed. ing. As a result, the welded portion 38 becomes a so-called “butt joint” instead of the conventional “garb joint”, and the strength against tensile stress increases. Therefore, even if a load in a direction away from the diaphragms 33 and 34 is applied, the joint portion 39 is not easily damaged. As a result, the strength of the damper member 35 can be improved.

  In particular, as shown in FIG. 3, in the damper member 35 of this embodiment, the operating parts 33a and 34a are elastically deformed with the pulsation of the fuel inside the fuel gallery 31, and at this time, as described above, the operating part The curvature radius R1 of the curved surface portions 33a and 34a is the largest. For this reason, when the operation parts 33a and 34a are elastically deformed, vibration is absorbed most in the curved surface portions of the operation parts 33a and 34a having low rigidity. Thereby, the effect | action of the stress to the welding parts 33d and 34d is suppressed.

  Further, by making the radius of curvature R3 of the convex edge portions 33c, 34c the smallest, the rigidity of the convex edge portions 33c, 34c becomes the highest, and the radial deformation of the welded portions 33d, 34d is suppressed. Therefore, it is possible to suppress an excessive stress from acting on the joint portion 39.

  Furthermore, when the height of each part of the damper member 35 satisfies the relationship of H1> H3> H2, when the pressure of the fuel gallery 31 increases, the recessed groove parts 33b and 34b come into close contact with each other. As a result, the curved surface portions of the operating portions 33a and 34a are greatly elastically deformed, and the elastic deformation of the convex edge portions 33c and 34c is suppressed. As a result, the welded portions 33d and 34d can be prevented from being deformed in the radial direction, and the stress can be prevented from acting on the joint portion 39.

  Further, due to the relationship of H1> H3, the pressure receiving areas of the welded portions 33d and 34d from the sealed space 300 are smaller than the pressure receiving areas of the operating portions 33a and 34a. Thereby, the load which acts on the welding part 33d and 34d in the radial direction can be made small. As a result, it is possible to suppress the occurrence of minute cracks in the joint portion 39.

  In addition, by adopting such a damper member 35, in this embodiment, the support member 36 is engaged with the base portion 40, the clamping portion 41 that sandwiches the separation portion 37, and the recessed portion 31 b on the side wall of the fuel gallery 31. 42, a bypass portion 43 that forms a bypass passage 47, and a passage portion 44 that forms a fuel passage 48.

  Thereby, the damper unit 32 is realized with a simple configuration. In the suction stroke, part of the fuel sucked into the pressurizing chamber 12 is guided from the volume side passage 18 to the pressure side passage 58 through the bypass passage 47. Therefore, it is possible to suppress the dynamic pressure of the fuel discharged from the volume side passage 18 from acting on the damper member 35. On the other hand, in the metering stroke, a part of the fuel discharged from the pressurizing chamber 12 to the fuel gallery 31 is guided to the volume side passage 18 from the pressure side passage 58 through the bypass passage 47. Therefore, the fuel discharged from the pressurization side passage 58 can be prevented from flowing directly into the supply side passage 19 to the fuel inlet. As a result, pulsation can be reliably suppressed.

  In particular, by inserting a part of the bypass portion 43 into the volume side passage 18, one end of the bypass passage 47 is connected to the volume side passage 18. Thereby, it is possible to reliably suppress the dynamic pressure of the fuel discharged from the volume side passage 18 from acting on the damper member 35. In addition, since a part of the bypass portion 43 is inserted into the volume side passage 18, the positioning of the damper member 35 in the circumferential direction can be easily realized.

  One cause of the pulsation is that, in the metering stroke, the fuel discharged from the pressure side passage 58 to the fuel gallery 31 flows into the supply side passage 19 leading to the fuel inlet. In this regard, in the present embodiment, one end of the fuel passage 48 is connected to the supply side passage 19. Thereby, it is possible to suppress the fuel discharged from the pressurizing side passage 58 from flowing into the supply side passage 19 directly.

  The other end of the fuel passage 48 opens below the damper member 35, and in particular, opens in a direction that does not face the opening of the pressure side passage 58. Thereby, it is possible to reliably suppress the fuel discharged from the pressurizing side passage 58 from flowing into the supply side passage 19.

  Furthermore, the sandwiching portion 41 of this embodiment has a resin-made support portion 45 that is integrally formed with the base portion 40 and supports the separation portion 37, and a clip portion 46 that holds the separation portion 37 on the support portion 45. . Thereby, the structure of the clamping part 41 is simplified.

  In this embodiment, a part of the clip part 46 is bent outward in the radial direction to form the assembly part 42. That is, the clip portion 46 and the assembly portion 42 are formed from a single metal member. This is advantageous in that the number of parts is reduced.

  Furthermore, in this embodiment, in addition to the clip portion 46 and the assembly portion 42 being integrated, the clip portion 46 is embedded in the support portion 45 so as to protrude from the support portion 45 (base portion 40). Yes. Thereby, since the damper unit 32 is sub-assembled, the time required for the assembly work can be shortened.

  Specifically, first, the damper member 32 is configured by attaching the support member 36 to the damper member 35. Next, when the damper unit 32 is pushed into the recess 13 of the housing 11, the damper unit 32 is elastically deformed around the assembly portion 42, and the assembly portion 42 engages with the recess 31b. Thereby, compared with the structure which presses a supporting member with the cover part 14, an assembly | attachment operation | work becomes easy. Further, there is no restriction on the shape of the lid 14. For example, in the present embodiment, the central portion of the lid portion 14 is expanded outward to increase the rigidity and suppress the radiated sound.

  The high-pressure pump 1 of this embodiment constitutes a “high-pressure pump” in the claims, the damper unit 32 constitutes a “damper unit”, the damper member 35 constitutes a “damper member”, and the support member 36 It constitutes a “support member”. Further, the separation part 37 constitutes a “separation part”, and the welding part 38 constitutes a “weld part”. Furthermore, the base 40 constitutes a “base part”, the clamping part 41 constitutes a “clamping part”, the assembly part 42 constitutes an “assembly part”, and the support part 45 constitutes a “support part”. The clip portion 46 constitutes a “clip portion”, the bypass portion 43 constitutes a “bypass portion”, the bypass passage 47 constitutes a “bypass passage”, the passage portion 44 constitutes a “passage portion”, The fuel passage 48 constitutes a “fuel passage”. The pressurizing chamber 12 constitutes a “pressurizing chamber”, the pressurizing side passage 58 constitutes a “pressurizing side passage”, the variable volume chamber 75 constitutes a “variable volume chamber”, and the volume side passage 18 “ "Volume side passage" is configured.

  As mentioned above, this invention is not limited to the form mentioned above at all, In the range which does not deviate from the meaning, it can be implemented with a various form.

  (A) For example, a damper unit 320 as shown in FIG. 4 may be adopted. The configuration of the support member 360 is different from the above form. The support member 360 includes a base part 400, a clamping part 410, an assembly part 420, a bypass part 430, and a passage part 440.

  The clamping unit 410 includes a support unit 450 and a clip unit 460. In this case, the support part 450 and the clip part 460 are separate bodies. The support part 450 has the same shape as the support part 45 of the above-described form. The clip portion 460 has a substantially horizontal portion that comes into contact with the separation portion 37 from above, and a distal end portion on the radially inner side is bent downward and is in contact with the separation portion 37 from the inside in the radial direction. On the other hand, the base end portion is bent substantially vertically downward and is in contact with the separation portion 37 from the outside in the radial direction.

  The assembly portion 420 is bent radially outward from the proximal end of the clip portion 460 and is engaged with the recess 31 b of the fuel gallery 31. By the engagement of the assembling part 420, the clip part 460 holds the separating part 37 on the support part 450.

  Moreover, the bypass part 430 and the channel | path part 440 are the structures substantially the same as the said form. The difference from the above configuration is that the fuel passage 480 is connected to the supply side passage 19 by inserting one end of the passage portion 440 into the supply side passage 19. On the other hand, although the bypass passage 470 is connected to the volume side passage 18, a part of the bypass portion 430 is not inserted into the volume side passage 18.

  Also in this embodiment, the same effects as in the above embodiment can be obtained. However, in the present embodiment, the base portion 400 is positioned in the circumferential direction by inserting one end of the passage portion 440 into the supply-side passage 19. In addition, since the clip unit 460 is separate from the support unit 450, the sub-assembly of the damper unit 320 is not achieved, but the clip unit 460 and the assembly unit 420 are integrated. The configuration is simple.

  Here, the damper unit 320 constitutes a “damper unit”, the support member 360 constitutes a “support member”, the base 400 constitutes a “base”, and the clamping part 410 constitutes a “clamping part”. The assembly part 420 constitutes an “assembly part”, the support part 450 constitutes a “support part”, the clip part 460 constitutes a “clip part”, and the bypass part 430 constitutes a “bypass part”. The bypass passage 470 constitutes a “bypass passage”, the passage portion 440 constitutes a “passage portion”, and the fuel passage 480 constitutes a “fuel passage”.

(B) In the above embodiment, the passage portions 44 and 440 are provided. However, the passage portions 44 and 440 may not be provided. Moreover, you may comprise the clip parts 46 and 460 and the assembly | attachment parts 42 and 420 as a different body.
(C) In the above embodiment, the clip portion 46 is embedded in the support portion 45. However, in addition to or in place of the clip portion 46, the assembly portion 42 may be embedded in the support portion 45.

  (D) In the above embodiment, when the height of the operating portions 33a, 34a is H1, the height of the recessed groove portions 33b, 34b is H2, and the height of the convex edge portions 33c, 34c is H3, H1> H3> H2. It was. On the other hand, as shown in FIG. 5, you may employ | adopt the structure from which the height of the convex edge parts 33c and 34c becomes larger than the height of the action | operation parts 33a and 34a. That is, it is good also as H3> H1> H2. Even in this case, it was experimentally confirmed that the same performance as described above was exhibited.

  1: high pressure pump, 10: body, 11: housing, 12: pressurizing chamber, 13: recess, 14: lid, 16: cylinder, 17: recess, 18: volume side passage, 19: supply side passage, 30 : Fuel supply part, 31: Fuel gallery, 31a: Bottom part, 31b: Concave part, 32: Damper unit, 33, 34: Diaphragm, 33a, 34a: Actuating part, 33b, 34b: Concave groove part, 33c, 34c: Convex edge part 33d, 34d: welded part, 35: damper member, 36: support member, 37: spaced part, 38: welded part, 39: joined part, 40: base part, 41: clamping part, 42: assembly part, 43: Bypass section, 44: passage section, 45: support section, 46: clip section, 46a: distal end section, 46b: base end section, 47: bypass path, 48: fuel path, 300: sealed space, 320: damper unit, 360 : Support section , 400: base, 410: clamping unit, 420: assembling unit, 430: Bypass section 440: passage, 450: supporting portion, 460: clip portion, 470: Bypass passage, 480: fuel passage

Claims (9)

A pressurizing chamber in which fuel is pressurized, a pressurizing side passage connecting from the pressurizing chamber to the fuel gallery and opening to the fuel gallery, a variable volume chamber whose volume changes with a change in volume of the pressurizing chamber, and A damper unit installed in the fuel gallery of a housing having a volume side passage that connects the variable volume chamber to the fuel gallery and opens to the fuel gallery;
A damper member having a separation part spaced apart in the vertical direction on the periphery of the diaphragm, and a weld part welded in a manner of being bent and butted from the separation part in a proximity direction;
A base housed inside the fuel gallery, a clamping part for clamping the spacing part, an assembly part assembled to the inner wall of the fuel gallery, and one end provided in the base part around the opening of the pressure side passage And a support member having a bypass portion forming a bypass passage whose other end opens around the opening of the volume side passage;
A damper unit characterized by comprising: The damper unit according to claim 1,
The damper unit includes a resin support part that is integrally formed with the base part and supports the separation part, and a clip part that holds the separation part on the support part. The damper unit according to claim 2,
The damper unit, wherein the clip part and the assembly part are formed by bending a single metal member. The damper unit according to any one of claims 2 and 3,
At least one of the clip part and the assembly part is embedded in the base part so as to protrude from the base part. In the damper unit according to any one of claims 1 to 4,
A part of the bypass portion is inserted into an opening of the volume chamber side passage, and directly connects the bypass passage and the volume side passage, and positions the base portion with respect to the fuel gallery. A damper unit. In the damper unit according to any one of claims 1 to 5,
The housing has a supply-side passage that connects a fuel inlet and the fuel gallery and opens to the fuel gallery,
The damper unit is characterized in that the support member has a passage portion that forms a fuel passage having one end opened around the opening of the supply side passage and the other end opened below the damper member. The damper unit according to claim 6,
A part of the passage portion is inserted into an opening of the supply side passage, and directly connects the fuel passage and the supply side passage, and positions the base portion with respect to the fuel gallery. Damper unit to be used. The damper unit according to claim 6 or 7,
The damper unit is characterized in that the other end of the fuel passage is opened in a direction not facing the opening of the pressurizing side passage.   A high pressure pump comprising the damper unit according to any one of claims 1 to 8.

Images