JP2005114024A - Seal structure using gasket - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a seal structure using a gasket capable of precisely maintaining sealing performance of a fastening part even if external force is applied to a tube body fastened to a housing. <P>SOLUTION: A check valve T having a tapered surface in a tip part 35 thereof and provided with a screw part 39 in rear thereof and provided with a flange part 33 enlarged in diameter from the screw part 39 is fastened to a housing 32 of a high-pressure fuel pump, which is provided with a through hole 38 in a side wall thereof and a circular hole 39a and a screw hole 31 enlarged in diameter from the through hole 38, by screwing the screw part 39 to the screw hole 31. A gasket G is interposed between the housing 32 and the check valve T to seal a fastening part of the housing 32 and the check valve T to each other. The gasket G formed into a ring shape is interposed between the tapered surface of the tip part 35 of the check valve T and the enlarged-diameter circular hole 39a provided in the side wall of the housing 32. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a seal structure in which two opposing surfaces of two elements to be fastened are sealed with a gasket.

  As such a seal structure, for example, a high-pressure fuel pump that supplies fuel to an engine (internal combustion engine) at a high pressure, and high-pressure fuel that is assembled to the pump and discharged from the pump is irreversibly supplied to a delivery pipe (pressure accumulation pipe). There is a seal structure in which a gap between two faces facing a check valve to be sent out is sealed with a gasket. Hereinafter, the outline of a seal structure conventionally employed as a seal structure between the high-pressure fuel pump and the check valve will be described with reference to the drawings.

FIG. 4 shows a schematic configuration of a fuel supply system of an engine in which the high-pressure fuel pump is incorporated.
As shown in FIG. 4, the fuel supply system of this type of engine is roughly divided into a feed pump 58 that sends out fuel from the inside of the fuel tank 56, and a fuel that is sent out by the feed pump 58 to pressurize the delivery pipe ( And a high-pressure fuel pump 54 that feeds pressure toward the pressure accumulation pipe 50.

  Here, the high-pressure fuel pump 54 includes a plunger 54e that reciprocates within the cylinder portion 54d based on the rotation of the cam 2a attached to the camshaft 2 of the engine. The high-pressure fuel pump 54 includes a pressurizing chamber 54f that is partitioned by a cylinder portion 54d and a plunger 54e and whose volume changes based on the reciprocating movement of the plunger 54e. The pressurizing chamber 54f is connected to the feed pump 58 via a low-pressure fuel passage 54c, and a pressure regulator 58a for making the pressure in the passage 54c constant is provided in the middle of the low-pressure fuel passage 54c. ing.

  The pressurizing chamber 54f communicates with the delivery pipe 50 via the check valve T and the high-pressure fuel passage 54a, and the fuel injection valves 22 corresponding to the cylinders of the engine are connected to the delivery pipe 50, respectively. Yes. The check valve T allows the fuel to flow from the pressurizing chamber 54f toward the delivery pipe 50, but prevents the backflow from the delivery pipe 50 to the pressurizing chamber 54f. As a result, when the electromagnetic spill valve 55 is closed when the plunger 54e enters the pressurizing chamber 54f and the fuel in the pressurizing chamber 54f becomes high pressure, the high pressure fuel passage 54a and the check from the pressurizing chamber 54f are checked. The high-pressure fuel is pumped and supplied to the delivery pipe 50 via the valve T. When the plunger 54e is retracted from the pressurizing chamber 54f, fuel is supplied into the pressurizing chamber 54f from the low pressure fuel passage 54c and the discharge passage 54h via the gallery 54b.

  On the other hand, the delivery pipe 50 is provided with a fuel pressure sensor 50 a for detecting the fuel pressure (fuel pressure) in the pipe 50. The delivery pipe 50 communicates with the discharge path 54h through a relief valve 54g. That is, when the fuel pressure in the delivery pipe 50 becomes excessively high, the relief valve 54g opens and the fuel in the pipe 50 flows out to the discharge path 54h.

  The high-pressure fuel pump 54 is provided with an electromagnetic spill valve 55 that communicates and blocks between the low-pressure fuel passage 54c and the pressurizing chamber 54f. The electromagnetic spill valve 55 includes an electromagnetic solenoid 55a, and opens and closes by controlling the voltage applied to the solenoid 55a. That is, when the energization of the electromagnetic solenoid 55a is stopped, the electromagnetic spill valve 55 is opened against the urging force of the coil spring 55b, and the low pressure fuel passage 54c and the pressurizing chamber 54f communicate with each other. Become.

  The closing timing of the electromagnetic spill valve 55 is calculated and executed by the electronic control unit (ECU) 60 according to the fuel pressure sensor 50a provided in the delivery pipe 50 and the fuel injection amount from the fuel injection valve 22. . Thus, the pumping amount of the high-pressure fuel pumped from the high-pressure fuel pump 54 to the delivery pipe 50 side is adjusted so as to maintain an appropriate fuel injection pressure.

Next, the operation of such a high-pressure fuel pump will be described with reference to FIG. 5A to 5C respectively correspond to steps (a) to (c) listed below.
(A) When the plunger 54e moves in the direction in which the volume of the pressurizing chamber 54f increases, the so-called high-pressure fuel pump 54 is inhaled, and the fuel sent from the feed pump passes through the low-pressure fuel passage 54c into the pressurizing chamber 54f. Inhaled.
(B) Thereafter, the plunger 54e gradually rises with the rotation of the cam 2a. However, at this time, the electromagnetic spill valve 55 is in an open state, and the fuel sucked into the pressurizing chamber 54f in the suction stroke is returned to the fuel tank without being pressurized (missed).
(C) Thereafter, when energization to the electromagnetic solenoid 55a is started at a predetermined timing, the electromagnetic spill valve 55 is closed against the urging force of the coil spring 55b, and the low pressure fuel passage 54c and the pressurizing chamber are closed. 54 f is cut off. As a result, the high pressure fuel pump 54 is in a so-called pressure increasing stroke, and as the plunger 54 e rises, the fuel in the pressurizing chamber 54 f passes through the check valve T and is pumped to the delivery pipe 50 (FIG. 4) via the high pressure fuel passage 54 a. The

Thus, the fuel is pressurized and pumped by the high-pressure fuel pump 54.
Next, an example of an attachment structure (fastening structure) of the check valve T to the high-pressure fuel pump 54 and an example of a seal structure thereof will be described with reference to FIG.

  As described above, the check valve T is disposed between the pressurizing chamber 54f of the high-pressure fuel pump 54 and the high-pressure fuel passage 54a (FIG. 4). Specifically, the check valve T is configured to include a tip portion 35 that comes into contact with the gasket g1, a thread portion 31, a flange portion 33, and a coupling portion 34 to which the high-pressure fuel passage 54a is coupled. The part 31 is fastened to the high-pressure fuel pump 54 by being screwed into a screw hole 39 provided in the housing 32 of the high-pressure fuel pump 54. Here, the gasket g1 seals between the two surfaces of the top surface of the tip portion 35 of the check valve T and the bottom surface 37 of the screw hole 39. The gasket g1 is a metal gasket made of, for example, a soft metal material, and has an annular shape having a hollow portion at the center thereof. A through hole 38 is provided between the cylinder portion 54d of the high pressure fuel pump 54 and the bottom surface 37 of the screw hole 39, and the pressure is applied through the through hole 38 and the hollow portion of the gasket g1. Fuel pumped from the chamber 54f is supplied into the check valve T. As is well known, the check valve T pushes open a valve body (not shown) when a predetermined fuel pressure is applied from the pressurizing chamber 54f side, and this pressure is applied to the high pressure fuel passage 54a side coupled to the coupling portion 34. A valve that supplies pressurized fuel. At this time, the gasket g1 is interposed between the front end portion 35 of the check valve T and the bottom surface 37 of the screw hole 39 to seal (seal) the two surfaces, so that the pressure is applied. It is also possible to prevent the leaked fuel from leaking outside.

  In addition, as a seal structure conventionally employed in the fastening portion between the check valve T and the high-pressure fuel pump 54, a structure exemplified in FIG. 7 is also known. That is, in the seal structure illustrated in FIG. 7, the gasket g <b> 2 is provided in such a manner as to seal between the two surfaces of the side surface of the housing 32 of the high-pressure fuel pump 54 and the side surface of the flange portion 33. Even in this case, fuel leakage or the like when pressurized fuel is pumped to the high-pressure fuel passage 54a via the check valve T is prevented by the gasket g2.

  Incidentally, in the case of the seal structure illustrated in FIG. 6 or the seal structure illustrated in FIG. 7, when no external force or the like is applied to the connecting portion 34 of the check valve T with, for example, the high-pressure fuel passage 54 a, the gasket is used. The above-described sealing performance by g1 or g2 is also maintained. However, in these seal structures, if the high-pressure fuel passage 54a itself has high rigidity and an external force due to vibration or the like may be applied to the check valve T, the sealing performance may be deteriorated.

  For example, in the seal structure illustrated in FIG. 6, when an external force F is applied upward to the coupling portion 34 in the manner shown in FIG. 6, the distance from the action point A to the fulcrum S is L4, and the force point P to the force point P. If the distance up to L5 is L5, the check valve T itself has sufficient rigidity, and a moment of “F × (L4 + L5)” is applied to the gasket g1 corresponding to the action point A. And this moment may cause deterioration of sealing performance.

  Also in the seal structure illustrated in FIG. 7, when the external force F is applied upward to the coupling portion 34 in the manner shown in FIG. 7, the following moment is applied to the gasket g2. That is, if the distance from the force point P to the fulcrum S is L6, the distance from the fulcrum S to the action point A is L7, and the distance from the action point A to the force point P is L8, the gasket g2 corresponding to the action point A has “F × (L6−L7) ”, that is, a moment of“ F × L8 ”is applied. In this case, the sealing performance may be deteriorated.

  Not only the seal structure between the check valve T and the high-pressure fuel pump 54, but also a moment caused by the application of external force to the tube acts directly on the gasket, and the tube is caused by this moment. In the seal structure in which the axial force is generated in the same direction as the axial direction, the actual situation is also common.

  The present invention has been made in view of such circumstances, and is a gasket seal that can accurately maintain the sealing performance of these fastening portions even when an external force is applied to a tubular body fastened to an appropriate housing. The purpose is to provide a structure.

In the following, means for achieving the above object and its effects are described.
The invention according to claim 1 has a tapered surface at the tip and a rear side of the housing in which a side wall is provided with a through hole and a circular hole and a screw hole that are expanded from the through hole. When fastening a tubular body having a threaded portion and a flange portion expanded in diameter from the threaded portion through screwing between the threaded hole and the threaded portion, a gasket is interposed between the housing and the tubular body. A sealing structure using a gasket for sealing a fastening portion between the housing and the tubular body, wherein the gasket has a belt-like shape between a tapered surface of the distal end portion of the tubular body and a circular hole having an enlarged diameter on the side wall of the housing. The gist is that it is intervened.

  According to such a sealing structure, when the housing and the tube are fastened, the gasket is in contact with the tapered surface of the tip of the tube, so that the axial force is substantially orthogonal to the axial direction of the tube. To occur in the direction. For this reason, this axial force also increases the surface pressure of the gasket interposed in the band shape, and the sealing performance is also accurately maintained.

  The invention according to claim 2 is the sealing structure by the gasket according to claim 1, wherein the gasket is configured such that one of the inner peripheral edges thereof is in contact with the tapered surface of the distal end portion of the tubular body. The gist is to have an annular shape provided.

  According to such a seal structure, the mounting property of the gasket itself is improved, and the seal is formed by the cooperation with the axial force in the direction substantially perpendicular to the axial direction of the tubular body accompanying the fastening of the housing and the tubular body. Performance will also be maintained higher.

  According to a third aspect of the present invention, in the sealing structure using the gasket according to the first or second aspect, the tubular body is configured such that the flange portion of the tubular body is in contact with the outer peripheral surface of the side wall of the housing. The gist of this is to be fastened to the housing.

  According to such a seal structure, even if an external force is applied to the pipe body, the influence is exerted on the seal part by the gasket by contacting the flange part of the pipe body and the outer peripheral surface of the side wall of the housing. The influence can be suitably suppressed. In addition, since the contact portion between the flange portion of the tube body and the outer peripheral surface of the side wall of the housing is not sealed by the gasket, the tube body may be fastened with a torque that does not loosen. The fastening force can be reduced as compared. Moreover, the gasket can be crushed by a certain amount by bringing the flange portion of the tubular body into contact with the outer peripheral surface of the side wall of the housing. That is, even if there are some dimensional tolerances in the tube body and the housing, they are not easily affected by this, and the sealing performance can be suitably maintained.

  Further, the invention according to claim 4 is the seal structure by the gasket according to any one of claims 1 to 3, wherein the housing is formed of a cylindrical body, and the through hole and the circular hole are formed on a side wall thereof. The gist is that the screw hole is provided.

  When the housing is made of the above-described cylinder, particularly when the cylinder constitutes a cylinder, the occurrence of distortion due to the fastening axial force with the pipe cannot be ignored in terms of its function. In this respect, in such a seal structure, since no load is generated in the axial direction of the tube body, even when the housing is formed of such a cylindrical body, the occurrence of distortion on the wall surface is suppressed, and the seal performance is favorable. Can be maintained.

  According to a fifth aspect of the present invention, in the seal structure using the gasket according to the fourth aspect, the cylindrical body is a cylinder portion of a high-pressure fuel pump, and the tubular body corresponds to a pressurizing chamber of the cylinder portion. The gist is that the check valve is provided.

  As is apparent from the function and effect of the invention described in claim 4, such a seal structure is particularly effective when employed in the fastening portion between the high-pressure fuel pump and the check valve. And, by adopting such a seal configuration for the fastening part, it is possible to keep the sealing performance at the fastening part high while suppressing application of unnecessary load to the cylinder part subjected to high-precision processing. become able to.

  1 and 2 show an embodiment of a sealing structure using a gasket according to the present invention. In this embodiment, an example in which the seal structure is applied to a fastening portion between the high-pressure fuel pump and a check valve assembled to the high-pressure fuel pump is shown.

Hereinafter, with reference to FIG. 1, the sealing structure by the gasket concerning this embodiment is demonstrated in detail.
As shown in FIG. 1, the check valve T, which is a tubular body, is a valve provided corresponding to the pressurizing chamber 54f of the cylinder portion 54d of the high-pressure fuel pump, as illustrated in FIG. In the engine fuel supply system, the high pressure fuel pump 54 is disposed between the pressurizing chamber 54f and the high pressure fuel passage 54a.

  As shown in FIG. 1, the check valve T itself includes a tip portion 35 having a tapered surface, a screw portion 31 provided at the rear thereof, and a flange portion provided at the rear thereof. 33 and a coupling portion 34 to which the high-pressure fuel passage 54a (FIG. 4) is coupled.

  On the other hand, the high-pressure fuel pump has a through hole 38 in a side wall of a housing 32 formed of a cylindrical body, and a circular hole 39 a and a screw hole 39 are provided in a form of expanding the diameter from the through hole 38. The check valve T is fastened to the housing 32 by screwing the screw portion 31 into a screw hole 39 provided in the housing 32 of the high-pressure fuel pump. However, in this embodiment, in particular, the gasket 32 is interposed between the circular hole 39a of the housing 32 and the tapered surface of the tip portion 35 of the check valve T, whereby the housing 32 and the check valve T are fastened. The structure is sealed. Incidentally, the gasket G is an annular metal gasket made of, for example, a soft metal material, and is provided in such a manner that one of the inner peripheral edges thereof is in contact with the tapered surface of the tip portion 35 of the check valve T. Yes.

  In this embodiment, the flange portion 33 of the check valve T is also brought into direct contact with the outer peripheral surface of the side wall of the housing 32 during the fastening. When the check valve T is fastened to the housing 32 of the high-pressure fuel pump in this way, the fuel pressurized in the pressurizing chamber 54f of the pump is transferred from the through hole 38 to the tip of the check valve T through the circular hole 39a. 35, the valve body (not shown) inside the check valve T is pushed open to be supplied to the high-pressure fuel passage 54a (FIG. 4) coupled to the coupling portion 34. At this time, the pressurized fuel leaks to the outside due to the gasket G being interposed between the tapered surface of the tip portion 35 of the check valve T and the circular hole 39a of the housing 32. Is also prevented.

  In FIG. 1, the length L <b> 1 indicates the length from the bottom surface 37 of the circular hole 39 a provided in the housing 32 to the outer peripheral surface of the side wall of the housing 32 with which the flange portion 33 of the check valve T abuts. Yes. The length L2 indicates the length from the top surface 35b of the tip portion 35 having the tapered surface of the check valve to the contact surface of the flange portion 33 with the housing 32 (exactly the outer peripheral surface of the side wall). ing. The length L3 indicates the difference between these lengths L1 and L2, that is, the separation distance from the bottom surface 37 of the circular hole 39a to the top surface 35b of the check valve T.

  FIG. 2 shows a region Z surrounded by a broken line in FIG. 1, that is, the tip 35 of the check valve T, the circular hole 39a formed in the housing 32 with an enlarged diameter, and the gap between them. The relationship with the intervening gasket G is shown by enlarging its dynamic structure. Next, the operation of the seal structure of the embodiment will be further described in detail with reference to FIG.

  As described above or as shown in FIG. 2, the tip portion 35 of the check valve T is provided with a tapered surface tapered in a conical shape. On the other hand, a circular hole 39a is enlarged in the housing 32 (FIG. 1) of the high-pressure fuel pump, and a gasket G is mounted with a crushing margin B between the tapered surface and the circular hole 39a. For this reason, the axial force when the check valve T is fastened to the housing 32 is in a direction substantially perpendicular to the axial direction of the check valve T via the gasket G, as shown by the arrow X1 in FIG. It comes to occur. Accordingly, the surface pressure of the gasket G against the inner peripheral wall of the circular hole 39a is naturally increased, and an accurate sealing performance is ensured.

  In addition, in this embodiment, as shown in FIG. 1, when the check valve T is fastened to the housing 32, the flange portion 33 of the check valve T is brought into direct contact with the outer peripheral surface of the side wall of the housing 32. Even when the above-described external force F is applied, the influence of the gasket G on the seal portion is also suppressed. Further, since the gasket as illustrated in FIG. 7 is not interposed at the contact portion between the flange portion 33 and the side wall outer peripheral surface of the housing 32, the check valve T itself is attached when the check valve T is mounted. The fastening force may be tightened with a torque that does not loosen, and the fastening force can be reduced as compared with the case where the gasket is interposed at the corresponding contact portion.

  FIG. 3 shows an example in which there is a dimensional tolerance in the direction in which the length L3 is relatively contracted with the length L1 and the length L2. Even when the housing 32 or the check valve T has such a dimensional tolerance, the axial force when the check valve T is fastened to the housing 32 is shown as an arrow X1 in FIG. Through the gasket G, it occurs in a direction substantially perpendicular to the axial direction of the check valve T. In particular, when there is a dimensional tolerance in the direction in which the length L3 contracts, the crushing margin B of the gasket G increases, and the surface pressure of the gasket G against the inner peripheral wall of the circular hole 39a. Can be further enhanced. That is, the sealing performance by the gasket G is also ensured more accurately.

As described above in detail, according to the seal structure using the gasket according to this embodiment, the following excellent effects can be obtained.
(1) When the housing 32 and the check valve T are fastened, the axial force of the gasket G is substantially orthogonal to the axial direction of the check valve T because the gasket G is in contact with the tapered surface of the check valve tip 35. To come in the direction. For this reason, the surface pressure of the gasket G is also increased by this axial force, and the sealing performance is also accurately maintained.

  (2) Since the gasket G has an annular shape provided such that one of the inner peripheral edges thereof is in contact with the tapered surface of the check valve tip portion 35, the mounting property of the gasket G itself is improved. .

  (3) Since the flange 33 of the check valve T and the outer peripheral surface of the side wall of the housing 32 are in contact with each other, even if an external force is applied to the check valve T, the influence, that is, the seal portion by the gasket G The influence exerted can also be suitably suppressed. Further, since the contact portion between the flange portion 33 of the check valve T and the outer peripheral surface of the side wall of the housing 32 is not sealed by the gasket G, the check valve T may be fastened with a torque that does not loosen. The fastening force can be reduced compared to the case where the gasket G is provided. In addition, the gasket G can be crushed by a certain amount by bringing the flange portion 33 of the check valve T and the side wall outer peripheral surface of the housing 32 into contact with each other. That is, even if there are some dimensional tolerances in the check valve T and the housing 32, they are not easily affected by the check valve T and the housing 32, and the sealing performance can be suitably maintained.

  (4) Such a seal structure using the gasket G is particularly effective when employed in a fastening portion between the cylinder and the tube, for example, a fastening portion between the high-pressure fuel pump 54 and the check valve T. And, by adopting such a seal configuration for the fastening portion, it is possible to maintain high sealing performance at the fastening portion while suppressing application of an unnecessary load to the cylinder portion 54d subjected to high-precision processing. Will be able to.

  In addition, the sealing structure by the gasket concerning this invention is not limited to the said embodiment, For example, it can also implement as the following forms which changed the embodiment suitably.

  3 shows an example in which the length L3 is reduced due to the dimensional tolerance of the housing 32 or the check valve T, and the crushing margin B of the gasket G is increased. However, the contact of the inner peripheral edge of the gasket G with the tapered surface is ensured. If it is within the range, even if a dimensional tolerance in the direction in which the length L3 becomes longer is produced, it is possible to obtain the effect according to the embodiment.

  In the above embodiment, the gasket G is a metal gasket made of a soft metal material, but the gasket G is not limited to this. Such a gasket G may be a soft one, and for example, a resin gasket, a rubber gasket, or the like can be appropriately employed.

  In the above-described embodiment, the cylinder is the housing 32 of the high-pressure fuel pump 54 and the cylinder portion 54d of the high-pressure fuel pump 54, and the pipe is the check valve T. It is not limited to such a thing. The physical structure of the cylindrical body and the tubular body is arbitrary, and even if it is such a structure, the effect according to the above embodiment can be obtained by applying the seal structure according to the present invention.

  In the above embodiment, the gasket G has an annular shape that is provided in such a manner that one of the inner peripheral edges thereof is in contact with the tapered surface of the check valve (pipe body) tip 35. However, if the gasket is interposed between the tapered surface at the distal end of the tubular body and the circular hole having an enlarged diameter on the side wall of the housing, the shaft in the direction substantially orthogonal to the axial direction of the tubular body described above when fastening them Can produce power. That is, the gasket is not limited to an annular shape, and may be a strip shape, preferably a continuous strip shape.

The side view and partial sectional view which show the schematic structure about one Embodiment of the sealing structure by the gasket concerning this invention. Side surface sectional drawing which expands and shows the area | region Z part of FIG. Side surface sectional drawing shown as an enlarged view corresponding to FIG. 2 about the modification of the seal structure by the gasket concerning this invention. The hydraulic circuit diagram which shows schematic structure of the fuel supply system of the engine in which the high pressure fuel pump was incorporated. (A)-(c) is a schematic sectional drawing which shows the operation example in each timing of a high pressure fuel pump. The side view and partial sectional view which show the schematic structure about the sealing structure by the conventional gasket. The side view and partial sectional view which show the schematic structure about the seal structure by the other conventional gasket.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 2 ... Cam shaft, 2a ... Cam, 22 ... Fuel injection valve, 31 ... Screw part, 32 ... Housing, 33 ... Flange part, 34 ... Coupling part, 35 ... Tip part, 35b ... Top surface, 37 ... Bottom surface of circular hole 38 ... Through hole, 39 ... Screw hole, 39a ... Circular hole, 50 ... Delivery pipe (accumulation pipe), 50a ... Fuel pressure sensor, 54 ... High pressure fuel pump, 54a ... High pressure fuel passage, 54b ... Gallery, 54c ... Low pressure Fuel passage, 54d ... cylinder part, 54e ... plunger, 54f ... pressurizing chamber, 54g ... relief valve, 54h ... discharge path, 55 ... electromagnetic spill valve, 55a ... electromagnetic solenoid, 55b ... coil spring, 56 ... fuel tank, 58 ... feed pump, 58a ... pressure regulator, 60 ... electronic control unit (ECU), G, g1, g2 ... gasket, T ... check valve.

Claims (5)

A housing with a through hole on the side wall and a circular hole and a screw hole with a diameter expanded from the through hole, has a tapered surface at the tip, and a threaded part at the rear and a diameter increased from the threaded part. When fastening a tube body including a flange portion formed through screwing between the screw hole and the screw portion, a gasket is interposed between the housing and the tube body so as to connect the housing and the tube body. A seal structure with a gasket that seals
The gasket is a sealing structure using a gasket, wherein the gasket is interposed in a band shape between a tapered surface at a distal end portion of the tubular body and a circular hole having an enlarged diameter on a side wall of the housing. The seal structure with a gasket according to claim 1, wherein the gasket has an annular shape provided such that one of the inner peripheral edges thereof is in contact with a tapered surface of a distal end portion of the tubular body. The seal structure using a gasket according to claim 1 or 2, wherein the tube body is fastened to the housing in a manner in which the flange portion of the tube body is in contact with an outer peripheral surface of a side wall of the housing. The seal structure by the gasket as described in any one of Claims 1-3 in which the said housing consists of a cylinder and the said through-hole, the said circular hole, and the said screw hole are provided in the side wall. The seal structure with a gasket according to claim 4, wherein the cylindrical body is a cylinder part of a high-pressure fuel pump, and the pipe body is a check valve provided corresponding to a pressurizing chamber of the cylinder part.

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