JP5408010B2 - High pressure pump - Google Patents

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.

  In such a high-pressure pump, since the plunger moves at a high speed, seizure between the plunger and the cylinder becomes a problem. Therefore, a high-pressure pump in which the cylinder is formed of a member different from the housing has been proposed (see, for example, Patent Documents 1 and 2).

German Patent Application No. 10322595 JP 2008-286144 A

  However, when the cylinder is formed of a separate member from the housing, there is a problem that the number of parts increases and the manufacturing cost increases.

  Further, the high-pressure pump is usually assembled to the engine head. For example, in the pressurization stroke, a pressure-feed reaction force of fuel in a direction away from the engine head acts on the high-pressure pump. For this reason, the high-pressure pump is fastened with a bolt or the like via a flange extending in the radial direction.

  However, fastening with a bolt or the like via such a flange distorts the housing. If this distortion propagates to the cylinder, it causes seizure between the cylinder and the plunger.

  In this regard, in Patent Documents 1 and 2, although the cylinder and the housing are configured as separate members, there is a possibility that the distortion of the housing may still propagate to the cylinder. Further, in Patent Document 1, since it is considered that the flange is joined to the lower end portion of the housing by welding or the like, there is a possibility that stress is applied to the joint portion when the flange is tightened with a bolt. On the other hand, in Patent Document 2, since the flange is sandwiched between the cylinder holder and the housing that are in close contact with the engine head and the flange cannot move relative to the cylinder holder and the housing, the flange is excessively pulled when tightened with a bolt. There is a risk of being stretched. As a result, in the techniques of Patent Documents 1 and 2, there is a concern that the fastening of the housing via the flange becomes insufficient.

  The present invention has been made in order to solve the above-described problems. The object of the present invention is to suppress the propagation of distortion due to fastening to a cylinder in fastening a high-pressure pump and to provide high reliability through a flange. It is to realize the fastening of the housing.

  The high-pressure pump according to claim 1, which has been made to achieve the above-described object, is attached to the engine head and pressurizes and discharges the fuel supplied from the fuel inlet. The high pressure pump includes a housing and a flange.

  The housing has a cylinder, a cylindrical part, a flange part, and a cylindrical space. The cylinder slidably supports a plunger capable of pressurizing the fuel. Further, the cylindrical portion forms an outline so as to surround the periphery of the cylinder. Furthermore, the collar portion is formed on the cylindrical surface of the cylindrical portion and protrudes radially outward. A cylindrical space is formed between the flange and the cylinder.

  As will be described later, the housing is fastened to the engine head by pressing the collar, but at this time, there is a possibility that distortion occurs in the vicinity of the collar. In this regard, in the present invention, since the cylindrical space is formed between the flange portion and the cylinder, it is possible to suppress the distortion due to fastening from propagating to the cylinder.

  The flange has an engaging portion and a fastening portion. An engaging part is a part which presses down a collar part. On the other hand, the fastening portion is formed continuously with the engaging portion, and a bolt insertion hole is formed in the fastening portion. At this time, the flange is movable relative to the housing in a state where the flange is placed on the engine head before fastening with the bolt, and a gap is formed between the engine head and the lower surface of the fastening portion. Yes. And after fastening with a bolt, it elastically deforms centering on an engaging part so that a clearance gap may be lost, and a collar part is pressed down to the engine head side by the reaction force of the elastic deformation concerned.

  Also in the prior art, there is a structure in which a gap is provided between the lower surface of the flange and the engine head, the connecting portion of the flange and the housing or the flange is deformed by the tightening axial force of the bolt, and the housing is pressed by the deformation reaction force.

  However, in the configuration of Patent Document 1, the deformation concentrates on the joint between the flange and the housing, and stress may concentrate on the joint by fastening. On the other hand, in patent document 2, it is the structure which bears all deformation | transformation by the expansion of a flange, and there exists a possibility that a great stress may act on a flange similarly by the deformation | transformation by fastening.

  This is because in both Patent Documents 1 and 2, the flange is fixed so that it cannot move relative to the housing. As a result, the amount of deformation due to fastening is small, and it is considered that the deformation cannot be performed so that the lower surface of the flange is in close contact. In this case, the lower surface of the flange remains floating, which may cause loosening of the bolt.

  On the other hand, in the present invention, the flange is movable relative to the housing before fastening with the bolt. Therefore, by fastening with the bolt, the flange moves the engaging portion while slightly shifting the relative position with the housing. It is elastically deformed in the center, and the flange is pressed against the engine head by the reaction force of the elastic deformation. Thereby, the fastening of a highly reliable housing via a flange is realizable.

  By the way, the flange portion protrudes radially outward. For example, as shown in claim 2, by forming a groove-like recess extending in the circumferential direction on the cylindrical surface, the flange portion is provided below the groove-like recess. It is conceivable to form.

  For example, when the groove-shaped concave portion is formed over the entire circumference of the cylindrical surface, the arm portion inserted into the groove-shaped concave portion may be configured to have the engaging portion. For example, as shown in claim 3, the engaging portion may include a pressing portion that presses the collar portion and an arm portion that extends bifurcated from the pressing portion.

In the present invention, since the flange is not fixed to the housing, it is conceivable that the flange falls off the housing before fastening with the bolt. Therefore, as shown in claim 1 , a pin may be provided so as to protrude from the upper surface of the flange, and a pin hole in which the pin is loosely fitted may be provided in the engaging portion. In this way, the flange is not dropped from the housing, and the assembly work is facilitated. Further, the rotation of the housing relative to the flange can be restricted.

In addition, as shown in Claim 4 , it is possible to provide a flange on both sides of a housing so that an engaging part may oppose. Fastening the housing with two flanges on both sides of the housing is advantageous in that the number of parts is reduced.

In this case, for example, as shown in claim 5 , it is conceivable to provide pin holes at positions that are symmetrical with each other in plan view in each of the opposed flanges. In this way, the amount of rotation of the housing can be reduced.

  For example, as shown in FIG. 7A, the pin holes 116 are formed in the opposing arm portions 114 of the two flanges 101 so as to be symmetrical with respect to the plane view.

  In this case, when the housing 11 is rotated in the clockwise direction, as shown in FIG. 7B, the rotation is restricted by the arm portion 114 far from the pin hole 116 of the right flange 101 coming into contact with the housing 11. Is done.

  On the other hand, when the housing 11 is rotated in the counterclockwise direction, as shown in FIG. 7C, the arm portion 114 far from the pin hole 116 of the left flange 101 abuts on the housing 11 to restrict the rotation. Is done.

  Thus, by forming the pin hole 116 in a line-symmetrical position, even when the housing 11 is rotated clockwise, the housing 11 is rotated counterclockwise. However, the rotation is restricted by the arm portion 114 far from the pin hole 116 of the left or right flange 101. Thereby, the rotation amount of the housing 11 can be made small.

  By the way, from the viewpoint of cost reduction, it is preferable to integrally mold the cylinder and the housing. This is because the number of parts can be reduced. Even if such a configuration is adopted, since the cylindrical space is formed inside the housing, it is possible to suppress the distortion due to fastening from propagating to the cylinder.

It is sectional drawing which shows the structure of the high pressure pump of one Embodiment. (A) is a perspective view which shows the upper surface of a flange, (b) is a perspective view which shows the lower surface of a flange. (A) is a top view of a flange, (b) is the BB sectional drawing of (a). It is explanatory drawing which shows a mode that the flange was loosely fitted by the housing with the pin. (A) is explanatory drawing which shows the flange before the fastening with a volt | bolt, (b) is explanatory drawing which shows the flange after the fastening with a volt | bolt. It is explanatory drawing which shows rotation of the housing by the position of a pin. It is explanatory drawing which shows rotation of the housing by the position of a pin. It is a perspective view which shows the flange of another embodiment. It is a perspective view which shows the high-pressure pump with which the flange was integrated.

  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. The damper unit 32 is pressed by the lid portion 14 via the wave spring 37.

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 housing 11 forms a cylinder 16 therein. The periphery of the cylinder 16 is a substantially cylindrical portion 11a. 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 oil film around the small diameter portion 712 of the plunger 71 and suppresses the inflow of oil from the engine.

  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.

  In this embodiment, in particular, a cylindrical cylindrical space 727 is formed between the press-fit portion 722 and the concave portion 17 in the radially inward direction.

  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.

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.

  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. Next, the fastening configuration to the engine head 200 will be described.

  As shown in FIG. 1, the high-pressure pump 1 is attached to the engine head 200 in such a manner that the lower portion of the plunger portion 70 is inserted into the attachment hole 201 of the engine head 200.

  As described above, the periphery of the cylinder 16 is the substantially cylindrical cylindrical portion 11a. However, a groove-shaped recess 18 is formed on the entire cylindrical surface of the cylindrical portion 11a. As a result, a flange 19 projecting in the radial direction is formed below the groove-shaped recess 18. The housing 11 is fastened to the engine head 200 so that the flange portion 19 is pressed from both sides by the two flanges 101. The flange 101 is fastened to the engine head 200 by a bolt 210.

Here, the structure of the flange 101 will be described.
As shown in FIGS. 2 and 3, the flange 101 has an engaging portion 111 and a fastening portion 112. The lower surface of the flange 101 has a step as can be seen from FIG. Here, the engaging part 111 is a thin part, and the fastening part 112 is a part thicker than the engaging part 111. Further, the engaging portion 111 is thinner than the width of the groove-like recess 18 of the housing 11.

  The engaging portion 111 includes a pressing portion 113 that is continuous with the fastening portion 112 and an arm portion 114 that is divided into two branches from the pressing portion 113 and extends symmetrically. The inner side surface of the arm portion 114 has a substantially arc shape so as to correspond to the groove-shaped recess portion 18 of the housing 11. With this configuration, the arm portion 114 is disposed so as to surround the housing 11 when inserted into the groove-like recess 18.

  Although the flange 101 is symmetric with respect to the line BB shown in FIG. 3A, the fastening portion 112 has a bolt hole 115 on the line BB. Further, the arm portion 114 has a pin hole 116 at a position deviated from the BB line.

  As shown in FIG. 4, a pin 19 a corresponding to the pin hole 116 of the arm portion 114 is provided on the collar portion 19 in a manner protruding at a predetermined location. It is conceivable that the pin 19a is press-fitted from a contact surface with the engine head 200 of the housing 11, for example. Therefore, the arm portion 114 of the flange 101 is inserted into the groove-shaped recess 18 of the housing 11, and then the pin 19 a is press-fitted into the housing 11, whereby the pin 19 a is inserted into the pin hole 116. At this time, the outer diameter of the pin 19 a is smaller than the inner diameter of the pin hole 116, and the pin 19 a is loosely fitted in the pin hole 116.

  In addition, the pin hole 116 formed in the arm part 114 is formed in the arm part 114 which the two flanges 101 oppose, as shown to Fig.7 (a). Specifically, it is formed on one side of the axis line J that connects the centers of the bolt holes 115 of the fastening portion 112 and at a position that is line symmetric with respect to the axis line K perpendicular to the axis line J.

Next, fastening by the bolt 210 will be described.
As shown in FIG. 5A, when the high-pressure pump 1 is placed on the engine head 200 with the arm 114 inserted in the groove-shaped recess 18 of the housing 11, the lower surface of the fastening portion 112 of the flange 101 is A gap C is formed between the head 200 and the head 200. At this stage, the flange 101 is movable relative to the housing 11.

  When the fastening portion 112 of the flange 101 is fastened to the engine head 200 with the bolt 210, the flange 101 is elastically deformed while slightly shifting the relative position with respect to the housing 11, and as shown in FIG. C is eliminated, and the fastening portion 112 is fixed to the upper surface of the engine head 200. At this time, the engaging portion 111 is elastically deformed around the connection portion with the fastening portion 112. By the reaction force due to this elastic deformation, the pressing portion 113 presses the flange portion 19 of the housing 11 against the engine head 200 side. That is, a downward load acts on the portion indicated by the symbol F.

  Here, the flange 101 may be deformed within the elastic region as follows. That is, the distance from the portion indicated by symbol F of the flange portion 19 to the step portion of the flange 101 is designed to have an appropriate dimension. In this way, the flange 101 can be provided with such rigidity that the gap C is filled in the elastic region and a necessary load can be secured in the portion indicated by the symbol F.

Next, the effect which the high pressure pump 1 of this form exhibits is demonstrated.
The high-pressure pump 1 of this embodiment is fastened to the engine head 200 by pressing the flange portion 19 of the housing 11 against the engine head 200 side with the flange 101 as shown in FIG. Therefore, there is a possibility that distortion occurs in the vicinity of the collar portion 19.

  In this regard, in this embodiment, as shown in FIG. 1, a cylindrical space 727 is formed inside the housing 11, that is, between the flange portion 19 and the cylinder 16. Thereby, even if distortion occurs in the flange portion 19 due to the fastening of the flange 101, the distortion can be prevented from propagating to the cylinder 16.

  Further, in this embodiment, as shown in FIG. 5B, the engaging portion 111 is slightly elastically deformed around the connecting portion with the fastening portion 112, so that the pressing portion 113 is the flange portion 19 of the housing 11. Is pressed against the engine head 200 side. As a result, the housing 11 can be sufficiently fastened to the engine head 200 via the flange 101. At this time, since the housing 11 is fastened by the two flanges 101, the number of parts is reduced as compared with the case of using three or more flanges.

  Furthermore, in this embodiment, as shown in FIG. 4, the arm portion 114 of the flange 101 is inserted into the groove-shaped recess portion 18 of the housing 11, and then the pin 19 a is press-fitted into the housing 11. The hole 116 is loosely fitted. As a result, the flange 101 does not fall off the housing 11, and the assembly work is facilitated.

  At this time, the pin hole 116 formed in the arm part 114 is formed in the arm part 114 which the two flanges 101 oppose as shown in FIG. Thereby, rotation of the housing 11 is regulated. This will be described with reference to FIGS.

  The inner diameter of the bolt hole 115 is larger than the outer diameter of the bolt 210. Moreover, as described above, the inner diameter of the pin hole 116 is larger than the outer diameter of the pin 19a. Therefore, the housing 11 rotates within a predetermined range, and the mounting angle of the high-pressure pump 1 varies. At this time, the pin holes 116 are arranged as shown in FIG. In the following description, for the sake of convenience, the left flange 101 is described as “left flange 101” and the right flange 101 is described as “right flange 101” in the drawing.

  Here, a comparative example will be described. In FIG. 6A, the pin hole 116 of the arm portion 114 is formed at a position that is point-symmetric with respect to the two flanges 101.

  In this case, when the housing 11 is rotated in the clockwise direction, as shown in FIG. 6 (b), both the left and right flanges 101 are rotated by the arm portion 114 far from the pin hole 116 contacting the housing 11. Movement is regulated. The contact position of the arm portion 114 is indicated by symbols A1 and A2.

  On the other hand, when the housing 11 is rotated counterclockwise, as shown in FIG. 6C, both the left and right flanges 101 are rotated by the arm portion 114 on the side close to the pin hole 116 contacting the housing 11. Movement is regulated. The contact position of the arm portion 114 is indicated by symbols A3 and A4.

  Here, when the restriction is performed by the arm portion 114 on the side far from the pin hole 116, the rotation is suppressed to be smaller than the case where the restriction is performed by the arm portion 114 near the pin hole 116. Therefore, in this case, the amount of rotation in the counterclockwise direction shown in FIG.

  On the other hand, in this embodiment, the pin holes 116 are formed in the opposing arm portions 114 of the two flanges 101 as shown in FIG. That is, the pin hole 116 is formed at a position that is line-symmetric with respect to the two flanges 101.

  In this case, when the housing 11 is rotated in the clockwise direction, as shown in FIG. 7B, the rotation is restricted by the arm portion 114 far from the pin hole 116 of the right flange 101 coming into contact with the housing 11. Is done. The contact position of the arm 114 is indicated by symbol A5.

  On the other hand, when the housing 11 is rotated in the counterclockwise direction, as shown in FIG. 7C, the arm portion 114 far from the pin hole 116 of the left flange 101 abuts on the housing 11 to restrict the rotation. Is done. The contact position of the arm portion 114 is indicated by symbol A6.

  Thus, in this embodiment, the pin hole 116 is formed at a line-symmetrical position, so that the housing 11 can be rotated counterclockwise even when the housing 11 is rotated clockwise. Even in this case, the rotation is restricted by the arm portion 114 on the side far from the pin hole 116 of the left or right flange 101. Thereby, the rotation amount of the housing 11 can be made small.

  Further, in this embodiment, since the cylinder and the housing are integrally formed, the number of parts can be reduced also in this respect.

  The high-pressure pump 1 of this embodiment corresponds to the “high-pressure pump” in the claims, the cylinder 16 corresponds to the “cylinder”, the cylindrical portion 11 a corresponds to the “cylindrical portion”, and the flange portion 19 corresponds to “鍔”. The cylindrical space 727 corresponds to the “cylindrical space”, and the housing 11 corresponds to the “housing”. Further, the engaging portion 111 corresponds to an “engaging portion”, the fastening portion 112 corresponds to a “fastening portion”, and the flange 101 corresponds to a “flange”. Furthermore, the groove-shaped recess 18 corresponds to a “groove-shaped recess”, the pressing portion 113 corresponds to a “pressing portion”, the arm portion 114 corresponds to an “arm portion”, and the pin 19a corresponds to a “pin”. The pin hole 116 corresponds to a “pin hole”.

  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 flange 301 as shown in FIG. 8 may be adopted. The flange 301 has an engaging portion 311 and a fastening portion 312. Here, the engaging portion 311 includes only the pressing portion 313 and does not include the arm portion 114 as described above. In this case, a bolt hole 315 is formed in the fastening portion 312, and a pin hole 316 is formed at the end of the pressing portion 313. This is advantageous in that the material cost can be reduced, although the effect of restricting the amount of rotation by the arm portion 114 is reduced unlike the above-described embodiment.

  At this time, the flange 301 corresponds to the “flange”, the engaging portion 311 corresponds to the “engaging portion”, the fastening portion 312 corresponds to the “fastening portion”, and the pressing portion 313 corresponds to the “pressing portion”. To do.

  (B) Further, for example, a high-pressure pump 2 as shown in FIG. 9 may be adopted. FIG. 9 is a perspective view showing the appearance of the high-pressure pump. The high-pressure pump 2 is formed by integrally molding the cylindrical portion 401 and the flange 410 of the housing 400. The flange 410 has a bolt hole 411 for fastening.

  In this way, although the effect of pressing the housing 400 against the engine head by the flange 410 is not exhibited, sufficiently firm fastening can be realized. Of course, if a cylindrical space is formed around the cylinder formed inside, it is possible to suppress the distortion generated in the projecting portion of the flange 410 from propagating to the cylinder.

  In this sense, “a high-pressure pump attached to the engine head and pressurizing and discharging the fuel supplied from the fuel inlet, and a cylinder that slidably supports a plunger capable of pressurizing the fuel; A cylindrical portion that forms an outer shell so as to surround the periphery, a flange that is integrally formed so as to protrude radially outward from the cylindrical portion, and a bolt insertion hole is formed between the protruding portion of the flange and the cylinder It is good also as a high pressure pump characterized by including a housing having a formed cylindrical space.

  1, 2: High pressure pump, 11, 400: Housing, 11a, 401: Cylindrical part, 16: Cylinder, 18: Groove-shaped concave part, 19: Gutter part, 19a: Pin, 101, 301, 410: Flange, 111, 311 : Engaging part, 112, 312: fastening part, 113, 313: pressing part, 114: arm part, 115, 315, 411: bolt hole, 116, 316: pin hole, 200: engine head, 201: mounting hole, 210: Bolt, 727: Cylindrical space

Claims (6)

A high-pressure pump attached to the engine head and pressurizing and discharging fuel supplied from a fuel inlet;
A cylinder that slidably supports a plunger capable of pressurizing fuel, a cylindrical portion that forms an outer shell so as to surround the cylinder, a flange portion that is formed on a cylindrical surface of the cylindrical portion and protrudes radially outward, and A housing having a cylindrical space formed between the flange and the cylinder;
It has an engaging part for pressing down the flange part, and a fastening part formed continuously with the engaging part and formed with a bolt insertion hole, and placed on the engine head before fastening with the bolt. In this state, the housing is movable relative to the housing, and a gap is formed between the engine head and the lower surface of the fastening portion. After fastening with bolts, the engagement portion is elastically centered so that the gap disappears. A flange that deforms and presses the flange against the engine head side by a reaction force of the elastic deformation ,
The flange has a pin provided in a manner protruding on the upper surface thereof,
The high-pressure pump , wherein the engaging portion has a pin hole into which the pin is loosely fitted . The high-pressure pump according to claim 1,
The said collar part is formed in the lower part of the said groove-shaped recessed part by forming the groove-shaped recessed part over the circumferential direction in the said cylindrical surface, The high pressure pump characterized by the above-mentioned. The high-pressure pump according to claim 1 or 2,
The high-pressure pump, wherein the engaging portion includes a pressing portion that presses the collar portion, and an arm portion that extends from the pressing portion. In the high pressure pump according to any one of claims 1 to 3 ,
The high-pressure pump, wherein the flange is provided on both sides of the housing so that the engaging portions face each other. The high-pressure pump according to claim 4 ,
The high-pressure pump according to claim 1, wherein the pin holes are provided at positions that are symmetrical with each other in the plan view in each of the opposed flanges. In the high pressure pump according to any one of claims 1 to 5 ,
The high-pressure pump, wherein the cylinder is integrally formed with the housing.

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