WO2022102478A1 - 高圧ガス用容器およびその製造方法 - Google Patents
高圧ガス用容器およびその製造方法 Download PDFInfo
- Publication number
- WO2022102478A1 WO2022102478A1 PCT/JP2021/040464 JP2021040464W WO2022102478A1 WO 2022102478 A1 WO2022102478 A1 WO 2022102478A1 JP 2021040464 W JP2021040464 W JP 2021040464W WO 2022102478 A1 WO2022102478 A1 WO 2022102478A1
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- WO
- WIPO (PCT)
- Prior art keywords
- container
- metal cylinder
- stress
- lid
- metal
- Prior art date
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
- F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
- F17C2260/00—Purposes of gas storage and gas handling
- F17C2260/01—Improving mechanical properties or manufacturing
- F17C2260/017—Improving mechanical properties or manufacturing by calculation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
- F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
- F17C2270/00—Applications
- F17C2270/01—Applications for fluid transport or storage
- F17C2270/0134—Applications for fluid transport or storage placed above the ground
- F17C2270/0139—Fuel stations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
- F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
- F17C2270/00—Applications
- F17C2270/01—Applications for fluid transport or storage
- F17C2270/0165—Applications for fluid transport or storage on the road
- F17C2270/0168—Applications for fluid transport or storage on the road by vehicles
- F17C2270/0178—Cars
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
- F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
- F17C2270/00—Applications
- F17C2270/01—Applications for fluid transport or storage
- F17C2270/0165—Applications for fluid transport or storage on the road
- F17C2270/0184—Fuel cells
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
- Y02E60/30—Hydrogen technology
- Y02E60/32—Hydrogen storage
Definitions
- the present invention relates to a container for high-pressure gas and a method for manufacturing the same.
- a high-pressure gas container (also called a pressure accumulator) for accumulating hydrogen at a pressure of 80 MPa or more is installed in the hydrogen station for supplying hydrogen to the fuel cell vehicle.
- a cylinder-type container such as a gas cylinder, in which the end of the pipe is drawn to create a mirror part (dome part), and the other is a straight pipe with lids on both ends. It is a mold container.
- the cylinder type container has a shape in which the cross-sectional area inside the container decreases toward the gas outlet, that is, the end in the longitudinal direction, and the end is called a "mirror part".
- a mouthpiece for taking in and out gas is provided at the tip of the mirror portion, and the mouthpiece is sealed with a clasp having a screw. Since the area of the clasp is sufficiently smaller than the cross-sectional area of the cylindrical portion of the cylinder-shaped container, the stress applied to the threaded portion of the base is reduced, and therefore there is no problem with pressure sealing.
- a container for high-pressure gas such as for a hydrogen station, it is necessary to periodically inspect the inner surface after the start of use, and there is a problem that it is difficult to inspect the inner surface of the container in a cylinder type container.
- the metal container is usually heat-treated for the purpose of improving the strength.
- quenching is generally performed by heating a metal container and then quenching it with cooling water, but in the case of a bomb-type container, it takes time for the cooling water to enter and discharge into the container. Therefore, the cooling rate during the heat treatment becomes slow, and the variation in the steel structure becomes large.
- a straight type container If the structure is a straight pipe with a lid, the opening of the pipe is large, so that cooling during heat treatment is easy and the structure of the steel material can be finely controlled. In addition, the decarburized layer and scale generated during heat treatment can be easily removed by machining. Further, by removing the lid, it is easy to inspect the inner surface of the container after use. In addition, since the straight type container does not have a mirror portion that has been drawn, there is almost no variation due to processing, and a uniform container can be manufactured. Examples of such a container for high-pressure gas include those described in Patent Documents 1 and 2.
- the lid structure of the high-pressure gas container using the straight-shaped container is required to withstand extremely high pressure.
- a structure in which a flange is provided at the end of the straight-shaped container and the lid is bolted using the flange, or a structure in which the lid is screwed to the container can be considered.
- the present invention has been made in view of the above circumstances, and an object of the present invention is to relieve stress applied to a threaded portion in a high-pressure gas container provided with a metal container and prevent fatigue fracture.
- the present inventors have obtained the following findings as a result of studies to solve the above problems.
- the present invention has been made based on the above findings, and has the following gist.
- a container for high-pressure gas equipped with a metal container comprises a metal cylinder having a female threaded portion on the inner peripheral surface of at least one end, and a lid having a male threaded portion screwed to the female threaded portion on the outer peripheral surface.
- the maximum value of the residual compressive stress at the position of 0.4 mm in the depth direction from the screw bottom at the plurality of screw bottoms of the female screw portion and the male screw portion is 100 MPa or more, the tensile strength of the material of the metal cylinder or less, and A container for high-pressure gas having a tensile strength equal to or lower than the tensile strength of the material of the lid.
- the male threaded portion of the lid is screwed into the female threaded portion of the metal cylinder.
- a method for manufacturing a high-pressure gas container provided with a metal container, wherein the metal container has a metal cylinder having a female threaded portion on the inner peripheral surface of at least one end and a male threaded portion screwed to the female threaded portion. It is equipped with a lid that has on the outer peripheral surface.
- a method for manufacturing a high-pressure gas container provided with a metal container wherein the metal container has a metal cylinder having a female threaded portion on the inner peripheral surface of at least one end and a male threaded portion screwed to the female threaded portion. It is equipped with a lid that has on the outer peripheral surface.
- the cover is provided with a lid tightening step of tightening the lid to the metal cylinder so that the male threaded portion of the lid is screwed into the female threaded portion of the metal cylinder.
- the lid tightening step the maximum value of the residual compressive stress at a position 0.4 mm in the depth direction from the screw bottom at the plurality of screw bottoms of the female screw portion and the male screw portion is tightened so as to be more than 0.
- the screw bottom stress of the female thread portion is larger than the yield stress of the material of the metal cylinder
- C The axial stress of the metal cylinder is equal to or less than the tensile strength of the material of the metal cylinder
- D Circumferential direction of the metal cylinder The stress is less than or equal to the tensile strength of the material of the metal cylinder
- the container for high-pressure gas of the present invention can be used at a higher pressure and a larger cross section as compared with the conventional case.
- the high-pressure gas container is a high-pressure gas container provided with a metal container, and the metal container has a metal cylinder having a female threaded portion on the inner peripheral surface of at least one end. , A lid having a male threaded portion screwed to the female threaded portion on the outer peripheral surface thereof is provided.
- the lids are preferably provided at both ends of the metal container. That is, it is preferable that the metal container is provided with a female threaded portion provided on the inner peripheral surface of both end portions of the metal cylinder and a lid having a male threaded portion screwed to the female threaded portion on the outer peripheral surface.
- the high-pressure gas container can be used as a high-pressure hydrogen gas container, for example, a hydrogen station container, a mobile hydrogen station, or a vehicle mounting container, but the container is not limited thereto and can be used for any purpose. can.
- the maximum value of the residual compressive stress at a position of 0.4 mm in the depth direction from the screw bottom at the plurality of screw bottoms of the female screw portion and the male screw portion is 100 MPa or more, and the tensile strength of the material of the metal cylinder. It is important that the strength is equal to or less than the tensile strength of the material of the lid. The reason will be described below.
- FIG. 1 is a schematic diagram showing a position that defines compressive residual stress in the present invention.
- a plurality of threaded grooves 12 are provided in the female threaded portion 11 provided on the inner peripheral surface of at least one end of the metal cylinder 10, and the bottom of the threaded groove 12 is the threaded bottom 13 of the female threaded portion.
- the outer peripheral surface of the lid 20 is provided with a male threaded portion 21 screwed into the threaded groove 12 of the female threaded portion 11, and the male threaded portion 21 has a plurality of threads 22.
- the bottom portion when the space between the adjacent thread 22s is regarded as a thread groove is defined as the thread bottom 23 of the male thread portion.
- the maximum value of the residual compressive stress at the position P of 0.4 mm in the depth direction is controlled from each of the thread bottom 13 of the female thread portion and the thread bottom 23 of the male thread portion so as to satisfy the above conditions.
- FIG. 1 is a schematic diagram for explanation only, and does not show the actual shape and dimensions of the threaded portion.
- the maximum value of the residual compressive stress at a position 0.4 mm in the depth direction from the screw bottom is set to 100 MPa or more.
- the maximum value of the residual compressive stress is set to be equal to or less than the tensile strength of the material of the metal cylinder and equal to or less than the tensile strength of the material of the lid.
- the maximum value of the residual compressive stress is equal to or less than the yield stress of the material of the metal cylinder and equal to or less than the yield stress of the material of the lid.
- the maximum value of the residual compressive stress is defined to indicate a value in a state where no internal pressure is applied to the metal container.
- the maximum value of the residual compressive stress can be obtained by elasto-plastic analysis by the finite element method (FEM).
- FEM finite element method
- Metal cylinder As the material of the metal cylinder, any metal can be used without particular limitation. From the viewpoint of cost reduction, it is preferable to use low alloy steel as the material. Examples of the low alloy steel include chromium molybdenum steel (JIS SCM steel), nickel chromium molybdenum steel (JIS SNCM steel), manganese chromium steel (JIS SMnC steel), manganese steel (JIS SMn steel), ASEM SA-723, and the like. And it is preferable to use any one of boron-added steels N28CB, N36CB and N46CB.
- JIS SCM steel chromium molybdenum steel
- JIS SNCM steel nickel chromium molybdenum steel
- JIS SMnC steel manganese chromium steel
- ASEM SA-723 ASEM SA-723
- the chromium molybdenum steel (SCM435) has C: 0.33 to 0.38% by mass, Si: 0.15 to 0.35% by mass, Mn: 0.60 to 0.90% by mass, P: 0. 030% by mass or less, S: 0.030% by mass or less, Cr: 0.90 to 1.20% by mass, Mo: 0.15 to 0.30% by mass.
- the metal cylinder one manufactured by any method can be used.
- the inside of the steel material may be hollowed out to form a container, or a steel pipe may be processed.
- the steel pipe any one such as an electric resistance welded steel pipe and a seamless steel pipe can be used, but it is particularly preferable to use a metal cylinder made of a seamless steel pipe.
- a metal cylinder made of a seamless steel pipe is extremely suitable as a container for a high-pressure gas container because it has excellent toughness and other characteristics as compared with a metal cylinder manufactured by hollowing out and has no welded portion.
- a female screw portion for screwing the lid is provided on the inner peripheral surface of at least one end of the metal cylinder.
- the metal cylinder has an opening for attaching a lid at at least one end, and a female screw portion is provided on the inner peripheral surface of the opening.
- the female threaded portions are preferably provided at both ends of the metal cylinder.
- the ratio of the inner diameter Di of the metal cylinder to the inner diameter Ds of the female threaded portion of the metal cylinder, Di / Ds, is preferably 3.5 or less, more preferably 2.0 or less, and 1.5 or less. Is more preferable.
- the inner diameter Ds in the female threaded portion is defined as the distance between the threaded bottoms of the female threaded portions formed on the inner peripheral surface of the metal cylinder at opposite positions.
- the inner diameter Di of the metal cylinder refers to the inner diameter of the metal cylinder in the portion where the female screw is not formed, that is, the inner diameter of the gas storage portion.
- the Di / Ds is preferably 0.8 or more, and more preferably 0.9 or more.
- a carbon fiber reinforced resin layer can be provided on the surface of the metal container. By providing the carbon fiber reinforced resin layer, the pressure resistance and fatigue characteristics of the container can be further improved.
- Carbon fiber reinforced resin is a composite material in which carbon fiber as a reinforcing material is impregnated with resin to improve its strength, and is called CFRP (carbon-fiber-reinforced plastic).
- CFRP carbon-fiber-reinforced plastic
- the carbon fiber is not particularly limited, and any carbon fiber such as a PAN type or a pitch type can be used.
- the volume content of carbon fibers in the carbon fiber reinforced resin layer can be determined in accordance with Japanese Industrial Standards JIS K 7075 (1991), and is usually preferably in the range of 50% to 80%.
- the carbon fiber reinforced resin layer can cover the entire or part of the outer surface of the metal container.
- the high-pressure gas container may have a structure (full wrap) in which the entire outer surface of the metal container is covered with a carbon fiber reinforced resin layer.
- a treatment for preventing electrolytic corrosion for example, coating by powder coating or wrapping with glass fiber reinforced resin (GFRP), is applied to the outer peripheral surface of the metal container. It is preferable to apply. As a result, even if cracks or the like occur in the carbon fiber reinforced resin layer which is the surface layer and water accumulates at the interface between the liner layer and the carbon fiber reinforced resin layer, rust due to potential difference corrosion occurs in the metal container. Can be prevented.
- GFRP glass fiber reinforced resin
- a thermoplastic powder coating based on a vinyl chloride resin or the like, or a thermosetting powder coating based on a polyester resin, an acrylic resin, an epoxy resin or the like can be used. Considering the heat generated when filling with a gas such as hydrogen, it is preferable to use a thermosetting powder coating material.
- the lid of the metal container is not particularly limited, and any lid can be used as long as it has a male threaded portion screwed to the female threaded portion of the metal cylinder on the outer peripheral surface.
- the high pressure gas container of the present invention is provided with a screw-down lid that can be attached to at least one of the metal cylinders.
- the lid may have an integral structure or a structure composed of a plurality of members.
- the lid is provided with a sealing member on the outer peripheral surface for sealing the high-pressure gas in the container.
- the sealing member is not particularly limited, and any sealing member can be used. It is preferable to use an O-ring as the sealing member.
- the lid includes an O-ring, it is preferable that the O-ring is provided at a position inside the container rather than the male screw portion.
- the material of the lid is not particularly limited, but it is preferably made of metal, and more preferably made of steel.
- steel it is more preferable to use a steel material (low alloy steel) having a tensile strength (TS) of 750 MPa or more.
- TS tensile strength
- the same material as that mentioned as the material of the metal cylinder can also be used.
- the material of the lid and the material of the metal cylinder may be the same or different, but are preferably the same. Further, as in the example shown in FIGS. 3 and 4, when the lid is composed of a plurality of members, the material of each member can be independently selected and may be the same or different.
- the screw shape of the male screw portion of the lid is not particularly limited and may be, for example, a screw specified by JIS, but it is preferable to use a shape that further reduces stress concentration.
- Examples of the shape for reducing stress concentration include a screw having a large radius of curvature at the tip of the screw bottom (a shape in which the tip of a trapezoidal screw is rounded, etc.).
- a schematic diagram showing a structure in which a lid is attached to a metal cylinder is referred to, but the container for high-pressure gas of the present invention is not limited to a state in which a lid is attached to a metal cylinder. not.
- FIG. 2 is a schematic view showing the structure of the high-pressure gas container 1 according to the embodiment of the present invention, and shows a cross section of the high-pressure gas container 1 in a plane passing through the central axis.
- the high-pressure gas container 1 includes a metal cylinder 10, and the internal space of the metal cylinder 10 constitutes a storage unit 14 for storing high-pressure gas. Further, female threaded portions 11 are provided on the inner peripheral surfaces of both ends of the metal cylinder 10.
- Both ends of the metal cylinder 10 are provided with solid cylindrical lids 20.
- a male screw portion 21 to be screwed into the female screw portion of the metal cylinder 10 is provided.
- Such a one-piece lid has the advantage of being easy to manufacture.
- the lid 20 is provided with an O-ring 24 as a sealing member on its outer peripheral surface.
- the male screw portion 21 is provided on the outside of the container (on the side opposite to the storage portion 14) of the O-ring 24.
- FIG. 3 is a schematic cross-sectional view showing the structure of the high-pressure gas container 1 in another embodiment of the present invention. The points not particularly mentioned are the same as those of the embodiment shown in FIG.
- the lid 20 in this embodiment is composed of a head plate 25 and a screw-in nut 26.
- the end plate 25 is a substantially plate-shaped (disk-shaped) member for sealing the gas in the container, and is provided with an O-ring 24 as a sealing member instead of having a screw on the peripheral side surface thereof.
- the screw-in nut 26 is a solid columnar member, and a male-threaded portion 21 screwed into the female-threaded portion of the metal cylinder 10 is provided on the outer peripheral surface thereof.
- the end plate 25 can be supported by the screw-in nut 26. If the lid has such a separated structure, if the male threaded portion of the screwed nut is damaged, only the screwed nut needs to be replaced, and the end plate can be used as it is.
- FIG. 4 is a schematic cross-sectional view showing the structure of the high-pressure gas container 1 in another embodiment of the present invention. The points not particularly mentioned are the same as those of the embodiment shown in FIG.
- the lid 20 in this embodiment includes a end plate 25 and a screw-in nut 26.
- the end plate 25 is a substantially plate-shaped (disk-shaped) member for sealing the gas in the container, and is provided with an O-ring 24 as a sealing member instead of having a screw on the peripheral side surface thereof.
- the screw-in nut 26 is a hollow cylindrical member, and a male screw portion 21 to be screwed into the female screw portion of the metal cylinder 10 is provided on the outer peripheral surface thereof.
- the lid has such a separated structure, if the male screw portion of the screwed nut is damaged, only the screwed nut needs to be replaced, and the end plate can be used as it is. Further, in the present embodiment, since the screw-in nut 26 has a hollow cylindrical shape, the weight of the lid can be significantly reduced, and the weight of the high-pressure gas container can be reduced. Further, since the screwed nut 26 is more likely to apply stress to the thread bottom of the male threaded portion than when it is a solid cylindrical member, residual compressive stress is applied to the threaded bottom of the male threaded portion without applying excessive stress to the metal cylinder. Can be granted.
- the hollow cylindrical screw-in nut 26 can be manufactured by any method.
- the inside of the steel material may be hollowed out to form a hollow cylinder, or a steel pipe may be used.
- a steel pipe any one such as an electric resistance welded steel pipe and a seamless steel pipe can be used, but it is preferable to use a seamless steel pipe.
- both the metal cylinder 10 and the screwed nut 26 are made of seamless steel pipes, a part of the manufacturing process of the metal cylinder and the screwed nut can be shared, which is extremely preferable from the viewpoint of productivity.
- the tensile strength of the member having the male screw portion among the members constituting the lid is defined as “the tensile strength of the material of the lid”. ..
- the yield stress of the member having the male screw portion among the members constituting the lid is defined as “the yield stress of the material of the lid”.
- the tensile strength and yield stress of the material of the screw nut 26 are defined as the tensile strength and yield stress of the material of the lid.
- the tightening is usually performed by applying a certain torque.
- stress is applied to the threaded portion by tightening the lid, if the stress exceeds the residual compressive stress applied in advance, the residual compressive stress is canceled out. Therefore, when the lid is tightened to the high-pressure gas container of the present invention so that the male-threaded portion of the lid is screwed into the female-threaded portion of the metal cylinder, the lid is tightened so that the preliminarily applied compressive residual stress remains. It is preferable to adjust the torque. Specifically, it is preferable that the maximum value of the residual compressive stress at a position 0.4 mm in the depth direction from the screw bottom in the plurality of screw bottoms of the female screw portion and the male screw portion is more than 0.
- the male threaded portion of the lid is screwed into the female threaded portion of the metal cylinder, and the female threaded portion and the plurality of screw bottoms of the male threaded portion are described.
- the maximum value of the residual compressive stress at a position 0.4 mm in the depth direction from the screw bottom is more than 0.
- the high-pressure gas container assembly is a high-pressure gas container assembly provided with a metal container.
- the metal container comprises a metal cylinder having a female threaded portion on the inner peripheral surface of at least one end, and a lid having a male threaded portion screwed to the female threaded portion on the outer peripheral surface. The male threaded portion of the lid is screwed into the female threaded portion of the metal cylinder.
- the maximum value of the residual compressive stress at the position of 0.4 mm in the depth direction from the screw bottom at the plurality of screw bottoms of the female screw portion and the male screw portion is more than 0, equal to or less than the tensile strength of the material of the metal cylinder, and A container assembly for high-pressure gas having a tensile strength equal to or lower than the tensile strength of the material of the lid.
- the lower limit of the tightening torque may be 0.
- the lid may loosen due to vibration when transporting the high-pressure gas container. Therefore, it is preferable to tighten the lid with a torque of 10 Nm or more, and more preferably with a torque of 100 Nm or more.
- the method for manufacturing a metal container according to an embodiment of the present invention is a metal container under the conditions that satisfy at least one of the following (A) and (B) and satisfy both the following (C) and (D). It is provided with an internal pressure applying step of applying an internal pressure to the object. According to this manufacturing method, a container for high-pressure gas having the above-mentioned predetermined residual compressive stress can be manufactured.
- the screw bottom stress applied in the internal pressure application step is equal to or higher than the tensile strength of the material.
- the internal pressure applying step it is preferable to apply the internal pressure under the condition that at least one of the following (A') and (B') is satisfied.
- (A') The screw bottom stress of the female thread portion is larger than the tensile strength of the material of the metal cylinder
- (B') The screw bottom stress of the male thread portion is larger than the tensile strength of the material of the lid.
- the upper limit of the screw bottom stress of the female screw portion and the screw bottom stress of the male screw portion in the internal pressure applying step is not particularly limited, and adjustment may be made so that a desired residual compressive stress is applied.
- the stress on the outer surface (outer peripheral surface of the cylinder) facing the female thread portion of the metal cylinder is equal to or less than the yield stress of the material of the metal cylinder. Is preferable.
- the inner surface (cylindrical nut) facing the male screw portion of the screw-in nut is used in the internal pressure applying step. It is preferable that the stress on the inner peripheral surface of the screwed nut is equal to or less than the yield stress of the material of the screwed nut.
- the axial stress and the circumferential stress applied to the metal cylinder can be obtained by the following equations (1) and (2), respectively.
- Axial stress (pressure receiving area of lid x internal pressure) / minimum cross-sectional area of metal cylinder ...
- Circumferential stress (inner diameter of metal cylinder x internal pressure) / (2 x thickness of metal cylinder) ...
- the "pressure receiving area of the lid” is the area of the surface of the lid in contact with the storage portion, and refers to the area of the end plate when the end plate is used as shown in FIGS. 3 and 4.
- the "cross-sectional area" of the metal cylinder refers to the cross-sectional area of the metal portion in the cross section perpendicular to the axial direction of the metal cylinder, and does not include the cross-sectional area of the internal space of the metal cylinder.
- the cross-sectional area of the metal cylinder may differ depending on the position in the longitudinal direction of the metal cylinder, and the axial stress applied to the metal cylinder is maximum at the portion where the cross-sectional area is the smallest. Therefore, in the above equation (1), the minimum cross-sectional area of the metal cylinder is used.
- the axial stress and the circumferential stress obtained by the equations (1) and (2) are average stresses per cross-sectional area of the metal cylinder.
- the screw bottom stress which is a local stress, can be calculated by the finite element method or the like as described later.
- the axial stress and the circumferential stress applied to the metal cylinder portion are larger than the values calculated by the above equations (1) and (2), respectively. It gets lower. Therefore, when the carbon fiber reinforced resin layer is provided on the outer surface of the metal container, the axial stress and the circumferential stress applied to the metal cylindrical portion are evaluated by numerical analysis using the finite element method.
- the metal cylinder may be plastically deformed and the inner diameter of the metal cylinder may change. Therefore, from the viewpoint of suppressing the deterioration of the sealing property due to the plastic deformation of the metal cylinder, it is preferable that the axial stress and the circumferential stress applied to the metal cylinder portion are equal to or less than the yield stress of the material of the metal cylinder. It is more preferable that the yield stress is 90% or less.
- the internal pressure applying step it is preferable to apply the internal pressure under the conditions that satisfy both the following (C ′) and (D ′), and both of the following (C ′′) and (D ′′) are satisfied. It is more preferable to apply the internal pressure under the conditions.
- the axial stress of the metal cylinder is equal to or less than the yield stress of the material of the metal cylinder
- the circumferential stress of the metal cylinder is equal to or less than the yield stress of the material of the metal cylinder (C'').
- Axial stress is 90% or less of the yield stress of the material of the metal cylinder (D'')
- Circumferential stress of the metal cylinder is 90% or less of the yield stress of the material of the metal cylinder.
- an arbitrary pressure medium may be filled inside the metal container.
- the pressure medium any medium can be used without particular limitation, but from the viewpoint of safety, it is preferable to use an incompressible fluid such as water or oil. Further, from the viewpoint of preventing corrosion of the metal container, it is preferable to use an incompressible fluid containing a corrosion inhibitor or an aqueous solution of alcohol such as ethylene glycol.
- the method for manufacturing a metal container according to another embodiment of the present invention is as follows.
- the metal container is provided with a lid tightening step of tightening the lid so that the male threaded portion of the lid is screwed into the female threaded portion of the metal cylinder.
- the lid tightening step the maximum value of the residual compressive stress at the position of 0.4 mm in the depth direction from the screw bottom at the plurality of screw bottoms of the female screw portion and the male screw portion becomes more than 0.
- the screw bottom stress of the female thread portion is larger than the yield stress of the material of the metal cylinder
- C The axial stress of the metal cylinder is equal to or less than the tensile strength of the material of the metal cylinder
- D Circumferential direction of the metal cylinder The stress is less than or equal to the tensile strength of the material of the metal cylinder
- the above-mentioned manufacturing method can also be used to manufacture a container for high-pressure gas having the above-mentioned predetermined residual compressive stress.
- each step will be described.
- a jig having a male threaded portion on the outer peripheral surface is attached to the metal cylinder so that the male threaded portion of the jig is screwed into the female threaded portion of the metal cylinder (jig mounting step).
- any jig can be used as long as it has a male screw to be screwed into the female thread portion of the metal cylinder.
- the material of the jig is not particularly limited, but it is preferably made of metal, and more preferably made of steel.
- steel it is more preferable to use a steel material (low alloy steel) having a tensile strength (TS) of 750 MPa or more.
- TS tensile strength
- the same material as that mentioned as the material of the metal cylinder can also be used.
- the material of the jig and the material of the metal cylinder may be the same or different, but it is preferable that they are the same.
- the screw bottom stress of the female thread portion is larger than the yield stress of the material of the metal cylinder
- C The axial stress of the metal cylinder is equal to or less than the tensile strength of the material of the metal cylinder
- D Circumferential direction of the metal cylinder The stress is less than or equal to the tensile strength of the material of the metal cylinder
- the lid As described above, it is preferable to use the lid as a jig in the jig mounting process and to use the lid used in the jig mounting process again in the lid tightening process.
- the lid when the lid is provided with a sealing member such as an O-ring, the sealing member may be damaged due to the high internal pressure applied in the internal pressure applying step, and the sealing property may be impaired. Therefore, it is preferable to remove the jig in the jig removing step, replace the sealing member of the lid, and then tighten the lid. Further, considering that a high internal pressure is applied in the internal pressure applying step, it is preferable that the diameter of the sealing member used in the internal pressure applying step is larger than the diameter of the sealing member used in the final lid tightening step.
- the screw bottom stress was analyzed by elasto-plastic analysis by the finite element method (FEM) using the container model.
- the container model includes a type 1 container made of a low alloy steel metal container and not having a carbon fiber reinforced resin layer, and a low alloy steel metal container (liner) which is the same as the type 1 container.
- Two types of type 2 containers made of a carbon fiber reinforced resin layer formed by winding CFRP around the surface of the metal container so as to have a thickness of 5 mm were used.
- the metal cylinder constituting the metal container and the lid were made of the same low alloy steel, and the tensile strength (TS) of the low alloy steel was 821 MPa and the yield stress (YP) was 705 MPa.
- TS tensile strength
- YP yield stress
- As the stress-strain curve of the low alloy steel the stress-strain curve of TS: 900 MPa class SNCM439 steel was used.
- the lid has a structure composed of a disk-shaped end plate and a hollow cylindrical screw-in nut, and the wall thickness of the end plate is 75 mm and the wall thickness of the screw-in nut is 37 mm.
- the wall thickness of the screwed nut is the thickness from the apex of the threaded portion provided on the outer peripheral surface to the inner surface.
- the screw shape was a JIS trapezoidal screw having a pitch of 12 mm, a screw depth of 12 mm, and a screw shoulder radius of curvature of 2.2 mm.
- Table 1 also shows the axial stress and the circumferential stress of the metal cylinder when the load internal pressure is applied.
- the axial stress and the circumferential stress were calculated by the following equations (1) and (2).
- Axial stress (pressure receiving area of lid x internal pressure) / minimum cross-sectional area of metal cylinder ...
- Circumferential stress (inner diameter of metal cylinder x internal pressure) / (2 x thickness of metal cylinder) ... (2)
- the metal container is a type 2 container, the axial stress and the circumferential stress were obtained by analysis by FEM.
- the compressive residual stress satisfying the conditions of the present invention can be introduced into the screw bottom by applying the internal pressure under appropriate conditions.
- a metal container in which the maximum value of the residual compressive stress at a position of 0.4 mm in the depth direction from the screw bottom satisfies the condition of the present invention has a reduced screw bottom stress when an internal pressure is applied. As a result, it showed an excellent fatigue life.
- Example 2 Next, the effect of the condition of tightening the lid on the metal cylinder on the fatigue life was evaluated by FEM analysis. Specifically, first, No. 1 in Example 1. For each of the containers 6, 11, and 13, the lid was once removed after the internal pressure applying step, and then the lid was tightened again under the conditions shown in Table 3. Next, the screw bottom stress when the internal pressure was applied again and the fracture life of the threaded portion were determined by the same procedure as in Example 1. The results are shown in Table 3.
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Abstract
Description
前記金属製容器は、少なくとも一方の端部の内周面に雌ねじ部を有する金属円筒と、前記雌ねじ部に螺合する雄ねじ部を外周面に有する蓋とを備え、
前記雌ねじ部および前記雄ねじ部の複数のねじ底における、前記ねじ底から深さ方向に0.4mmの位置における残留圧縮応力の最大値が、100MPa以上、前記金属円筒の材料の引張強度以下、かつ前記蓋の材料の引張強度以下である高圧ガス用容器。
前記雌ねじ部および前記雄ねじ部の複数のねじ底における、前記ねじ底から深さ方向に0.4mmの位置における残留圧縮応力の最大値が0超である、上記1または2に記載の高圧ガス用容器。
下記(A)および(B)の少なくとも一方を満たし、かつ、下記(C)および(D)の両者を満たす条件で前記金属製容器に対して内圧を付与する内圧付与工程を備える、高圧ガス用容器の製造方法。
(A)前記雌ねじ部のねじ底応力が前記金属円筒の材料の降伏応力より大きい
(B)前記雄ねじ部のねじ底応力が前記蓋の材料の降伏応力より大きい
(C)前記金属円筒の軸方向応力が前記金属円筒の材料の引張強度以下
(D)前記金属円筒の周方向応力が前記金属円筒の材料の引張強度以下
前記金属円筒に、雄ねじ部を外周面に有する治具を、前記治具の雄ねじ部が前記金属円筒の雌ねじ部に螺合するよう取り付ける治具取付工程と、
下記(A)、(C)、および(D)を満たす条件で前記金属製容器に対して内圧を付与する内圧付与工程と、
前記治具を前記金属容器から取り外す治具取外し工程と、
前記蓋の雄ねじ部が前記金属円筒の雌ねじ部に螺合するよう前記金属円筒に前記蓋を締付ける蓋締付工程とを備え、
前記蓋締付工程においては、前記雌ねじ部および前記雄ねじ部の複数のねじ底における、前記ねじ底から深さ方向に0.4mmの位置における残留圧縮応力の最大値が0超となるように締付トルクを調整する、高圧ガス用容器の製造方法。
(A)前記雌ねじ部のねじ底応力が前記金属円筒の材料の降伏応力より大きい
(C)前記金属円筒の軸方向応力が前記金属円筒の材料の引張強度以下
(D)前記金属円筒の周方向応力が前記金属円筒の材料の引張強度以下
本発明の一実施態様における高圧ガス用容器は、金属製容器を備えた高圧ガス用容器であって、前記金属製容器は、少なくとも一方の端部の内周面に雌ねじ部を有する金属円筒と、前記雌ねじ部に螺合する雄ねじ部を外周面に有する蓋とを備えている。
上記金属円筒の材料としては、特に限定されることなく任意の金属を用いることができる。低コスト化の観点からは、前記材料として、低合金鋼を用いることが好ましい。前記低合金鋼としては、特に、クロムモリブデン鋼(JIS SCM steel)、ニッケルクロムモリブデン鋼(JIS SNCM steel)、マンガンクロム鋼(JIS SMnC steel)、マンガン鋼(JIS SMn steel)、ASEM SA-723、およびボロン添加鋼N28CB、N36CB、N46CBのうちいずれか1つを用いることが好ましい。中でも、材料強度との両立の観点からは、焼き入れ性を確保しやすいクロムモリブデン鋼、SA723鋼、またはクロムモリブデンニッケル鋼を用いることがより好ましい。例えば、クロムモリブデン鋼(SCM435)は、C:0.33~0.38質量%、Si:0.15~0.35質量%、Mn:0.60~0.90質量%、P:0.030質量%以下、S:0.030質量%以下、Cr:0.90~1.20質量%、Mo:0.15~0.30質量%である。
上記金属製容器の表面には、炭素繊維強化樹脂層を設けることができる。前記炭素繊維強化樹脂層を設けることにより、容器の耐圧性および疲労特性をさらに向上させることができる。
上記金属製容器の蓋としては、とくに限定されることなく、前記金属円筒の雌ねじ部に螺合する雄ねじ部を外周面に有するものであれば任意の蓋を用いることができる。言い換えると、本発明の高圧ガス用容器は、金属円筒の少なくとも一方に取る付けることができるねじ込み式の蓋を備えている。前記蓋は、一体構造であってもよく、複数の部材からなる構造であってもよい。
上述したように、ねじ底付近に所定の残留圧縮応力を予め付与しておくことにより、金属製容器にガスを充填した際にねじ部にかかる応力を緩和することができる。しかし、本発明の高圧ガス用容器を実際に使用する際には、蓋を締付ける力によって、前記残留圧縮応力による応力低減効果が変化する。
前記金属製容器は、少なくとも一方の端部の内周面に雌ねじ部を有する金属円筒と、前記雌ねじ部に螺合する雄ねじ部を外周面に有する蓋とを備え、
前記蓋の雄ねじ部が前記金属円筒の雌ねじ部に螺合された状態であり、
前記雌ねじ部および前記雄ねじ部の複数のねじ底における、前記ねじ底から深さ方向に0.4mmの位置における残留圧縮応力の最大値が、0超、前記金属円筒の材料の引張強度以下、かつ前記蓋の材料の引張強度以下である高圧ガス用容器組立体である。
次に、本発明の一実施形態における高圧ガス用容器の製造方法について説明する。上述したように、高圧ガス用容器に該高圧ガス用容器の常用圧力よりも高い内圧をかけると、過大な応力が発生し、ねじ底に局所的な塑性変形が生じる。塑性変形が生ずる領域は一部であり、その他の領域の多くは弾性域であるため、前記内圧を除荷した後には、ねじ底部に圧縮応力が残留する。したがって、高圧ガス用容器の製造過程において、該高圧ガス用容器に所定の条件で高い内圧をかけることにより、ねじ部に所定の残留圧縮応力を付与することができる。
そこで、本発明の一実施形態における金属製容器の製造方法は、下記(A)および(B)の少なくとも一方を満たし、かつ、下記(C)および(D)の両者を満たす条件で金属製容器に対して内圧を付与する内圧付与工程を備える。この製造方法によれば、上述した所定の残留圧縮応力を有する高圧ガス用容器を製造することができる。
(A)前記雌ねじ部のねじ底応力が前記金属円筒の材料の降伏応力より大きい
(B)前記雄ねじ部のねじ底応力が前記蓋の材料の降伏応力より大きい
(C)前記金属円筒の軸方向応力が前記金属円筒の材料の引張強度以下
(D)前記金属円筒の周方向応力が前記金属円筒の材料の引張強度以下
ねじ底付近に残留圧縮応力を付与するためには、ねじ底に塑性変形を生じさせる必要がある。そして、ねじ底に塑性変形を生じさせるためには、材料の降伏応力を超えるねじ底応力を付与すればよい。そこで本発明では、前記内圧付与工程において、上記(A)および(B)の少なくとも一方を満たす条件で内圧を付与することとする。条件(A)を満たす場合、金属円筒の雌ねじ部に残留圧縮応力を付与することができる。また、条件(B)を満たす場合、蓋の雄ねじ部に残留圧縮応力を付与することができる。
(A’)前記雌ねじ部のねじ底応力が前記金属円筒の材料の引張強度より大きい
(B’)前記雄ねじ部のねじ底応力が前記蓋の材料の引張強度より大きい
上述したように、残留圧縮応力を付与するためには内圧をかけて塑性変形を生じさせる必要があるが、内圧が高すぎると金属円筒が破壊されてしまう。金属円筒の破壊を防ぐためには、金属円筒にかかる軸方向応力と周方向応力の両者が、該金属円筒の材料の引張強度以下とする必要がある。上記(B)および(C)は、前記条件を具体的に定めたものである。
軸方向応力=(蓋の受圧面積×内圧)/金属円筒の最小断面積…(1)
周方向応力=(金属円筒の内径×内圧)/(2×金属円筒の板厚)…(2)
ここで、「蓋の受圧面積」とは、蓋の、貯蔵部と接する面の面積であり、図3、4に示すように鏡板を使用する場合、鏡板の面積を指す。また、金属円筒の「断面積」とは、該金属円筒の軸方向に垂直な断面における、金属部分の断面積を指し、該金属円筒の内部空間の断面積は含まない。なお、金属円筒の断面積は、該金属円筒の長手方向位置によって異なる場合があり、金属円筒にかかる軸方向応力は断面積が最小の部分で最大となる。そのため、上記(1)式では金属円筒の最小断面積を使用する。なお、(1)および(2)式で得られる軸方向応力および周方向応力は金属円筒の断面積当たりの平均的な応力である。一方、局所的な応力であるねじ底応力は、後述するように有限要素法等により算出することができる。
(C’)前記金属円筒の軸方向応力が前記金属円筒の材料の降伏応力以下
(D’)前記金属円筒の周方向応力が前記金属円筒の材料の降伏応力以下
(C’’)前記金属円筒の軸方向応力が前記金属円筒の材料の降伏応力の90%以下
(D’’)前記金属円筒の周方向応力が前記金属円筒の材料の降伏応力の90%以下
また、本発明の他の実施形態における金属製容器の製造方法は、
前記金属円筒に、雄ねじ部を外周面に有する治具を、前記治具の雄ねじ部が前記金属円筒の雌ねじ部に螺合するよう取り付ける治具取付工程と、下記(A)、(C)、および(D)を満たす条件で前記金属製容器に対して内圧を付与する内圧付与工程と、
前記治具を前記金属容器から取り外す治具取外し工程と、
前記蓋の雄ねじ部が前記金属円筒の雌ねじ部に螺合するよう前記金属容器に前記蓋を締付ける蓋締付工程とを備え、
前記蓋締付工程においては、前記雌ねじ部および前記雄ねじ部の複数のねじ底における、前記ねじ底から深さ方向に0.4mmの位置における残留圧縮応力の最大値が0超となるように締付トルクを調整する、高圧ガス用容器の製造方法である。
(A)前記雌ねじ部のねじ底応力が前記金属円筒の材料の降伏応力より大きい
(C)前記金属円筒の軸方向応力が前記金属円筒の材料の引張強度以下
(D)前記金属円筒の周方向応力が前記金属円筒の材料の引張強度以下
まず、金属円筒に、雄ねじ部を外周面に有する治具を、前記治具の雄ねじ部が前記金属円筒の雌ねじ部に螺合するよう取り付ける(治具取付工程)。前記治具としては、金属円筒の雌ねじ部に螺合する雄ねじを有する治具であれば、任意のものを用いることができる。前記治具としては、金属製容器の蓋として使用される部材と同等のものを用いることが好ましい。また、前記治具として用いた蓋を、後述する蓋締付工程において再度蓋として使用することがより好ましい。
金属円筒に治具を取り付けた後、下記(A)、(C)、および(D)を満たす条件で前記金属製容器に対して内圧を付与する(内圧付与工程)。なお、(A)、(C)、および(D)の各条件の限定理由は、上記第一の実施形態の説明において述べたとおりである。また、その他の点についても、特に断らない限り上記第一の実施形態と同様とすることができる。
(A)前記雌ねじ部のねじ底応力が前記金属円筒の材料の降伏応力より大きい
(C)前記金属円筒の軸方向応力が前記金属円筒の材料の引張強度以下
(D)前記金属円筒の周方向応力が前記金属円筒の材料の引張強度以下
上記内圧付与工程において内圧を付与した後、前記治具を前記金属容器から取り外す(治具取外し工程)。
その後、前記蓋の雄ねじ部が前記金属円筒の雌ねじ部に螺合するよう前記金属円筒に前記蓋を締付ける(蓋締付工程)。前記蓋締付工程においては、前記雌ねじ部および前記雄ねじ部の複数のねじ底における、前記ねじ底から深さ方向に0.4mmの位置における残留圧縮応力の最大値が0超となるように締付トルクを調整する。
容器モデルを用いた有限要素法(FEM)による弾塑性解析によりねじ底応力を解析した。前記容器モデルとしては、低合金鋼製の金属製容器からなり、炭素繊維強化樹脂層を有さないタイプ1容器と、前記タイプ1容器と同じ低合金鋼製の金属製容器(ライナ)と、前記金属製容器の表面にCFRPを厚さ5mmとなるように巻き付けて形成された炭素繊維強化樹脂層とからなるタイプ2容器の2種類を使用した。前記金属製容器を構成する金属円筒と蓋の材質は同じ低合金鋼とし、前記低合金鋼の引張強度(TS)は821MPa、降伏応力(YP)は705MPaとした。また、前記低合金鋼の応力-ひずみ曲線としては、TS:900MPa級 SNCM439鋼の応力ひずみ曲線を用いた。
ソフトウェア:ABAQUS Ver.6.12-4(ダッソー・システムズ株式会社)
計算モデル:軸対称モデル
メッシュ分割:応力集中部において50μm
境界条件:金属円筒の内面および鏡板のガス貯蔵部側にガス圧力を付与
拘束条件:金属円筒:Y対称面上の節点、Y方向変位拘束
鏡板、ねじ込みナット:積極的な節点の変位の固定は無し
接触条件:接触摩擦係数μ=0.05
上記金属製容器に対し、表1に示した負荷内圧をかけた際のねじ底応力をFEMにより求めた。雌ねじ部におけるねじ底応力の最大値と、雄ねじ部におけるねじ底応力の最大値は表1に示したとおりであった。また、ねじ底応力の最大値とは、ねじ底から、該ねじ底とは反対側の表面までの肉厚方向全体における応力の最大値を指す。なお、本実施例では、内圧負荷工程における雄ねじ部のねじ底応力の最大値は、表1に示したすべての例において雌ねじ部のねじ底応力の最大値よりも低かった。そのため、表1には雌ねじ部のねじ底応力の最大値のみを示した。
軸方向応力=(蓋の受圧面積×内圧)/金属円筒の最小断面積…(1)
周方向応力=(金属円筒の内径×内圧)/(2×金属円筒の板厚)…(2)
また、金属製容器がタイプ2容器である場合、前記軸方向応力と周方向応力はFEMによる解析で求めた。
次いで、FEMによる解析により、上記内圧を除荷した状態における、ねじ底から深さ方向に0.4mmの位置における残留圧縮応力を求めた。表2には、雄ねじ部における残留圧縮応力の最大値、雌ねじ部における圧縮残留応力の最大値、およびそれらの最大値を示す。
金属製容器を実際に高圧ガス容器として使用する際の条件を想定して、金属製容器に対し82MPaの内圧を負荷した際のねじ底応力の最大値を、FEMによる解析で求めた。得られた結果は表2に示したとおりであった。
FEMによる解析で求められた応力から、圧力サイクル試験におけるねじ部の破断寿命を評価した。破断寿命の評価は、高圧ガス保安協会が定めた「各種部位のき裂進展解析法」(KHKS 0220(2010)附属書IX)にしたがって実施した。圧力付与の条件は、最小圧力:2MPa、最大圧力:82MPa、温度:室温とした。
次に、蓋を金属円筒に締付ける条件が疲労寿命に与える影響をFEM解析により評価した。具体的には、まず、実施例1におけるNo.6、11、および13の容器のそれぞれについて、内圧付与工程の後に一旦蓋を取り外した後、再度、表3に示す条件で蓋を締付けた。次いで、再度内圧を負荷した際のねじ底応力と、ねじ部破断寿命を、実施例1と同様の手順で求めた。結果を表3に示す。
10 金属円筒
11 雌ねじ部
12 ねじ溝
13 雌ねじ部のねじ底
14 貯蔵部
20 蓋
21 雄ねじ部
22 ねじ山
23 雄ねじ部のねじ底
24 Oリング
25 鏡板
26 ねじ込みナット
P ねじ底から深さ方向に0.4mmの位置
Claims (5)
- 金属製容器を備えた高圧ガス用容器であって、
前記金属製容器は、少なくとも一方の端部の内周面に雌ねじ部を有する金属円筒と、前記雌ねじ部に螺合する雄ねじ部を外周面に有する蓋とを備え、
前記雌ねじ部および前記雄ねじ部の複数のねじ底における、前記ねじ底から深さ方向に0.4mmの位置における残留圧縮応力の最大値が、100MPa以上、前記金属円筒の材料の引張強度以下、かつ前記蓋の材料の引張強度以下である高圧ガス用容器。 - 前記残留圧縮応力の最大値が、前記金属円筒の材料の降伏応力以下、かつ前記蓋の材料の降伏応力以下である、請求項1に記載の高圧ガス用容器。
- 前記蓋の雄ねじ部が前記金属円筒の雌ねじ部に螺合された状態であり、
前記雌ねじ部および前記雄ねじ部の複数のねじ底における、前記ねじ底から深さ方向に0.4mmの位置における残留圧縮応力の最大値が0超である、請求項1または2に記載の高圧ガス用容器。 - 金属製容器を備えた高圧ガス用容器の製造方法であって、前記金属製容器は、少なくとも一方の端部の内周面に雌ねじ部を有する金属円筒と、前記雌ねじ部に螺合する雄ねじ部を外周面に有する蓋とを備えており、
下記(A)および(B)の少なくとも一方を満たし、かつ、下記(C)および(D)の両者を満たす条件で前記金属製容器に対して内圧を付与する内圧付与工程を備える、高圧ガス用容器の製造方法。
(A)前記雌ねじ部のねじ底応力が前記金属円筒の材料の降伏応力より大きい
(B)前記雄ねじ部のねじ底応力が前記蓋の材料の降伏応力より大きい
(C)前記金属円筒の軸方向応力が前記金属円筒の材料の引張強度以下
(D)前記金属円筒の周方向応力が前記金属円筒の材料の引張強度以下 - 金属製容器を備えた高圧ガス用容器の製造方法であって、前記金属製容器は、少なくとも一方の端部の内周面に雌ねじ部を有する金属円筒と、前記雌ねじ部に螺合する雄ねじ部を外周面に有する蓋とを備えており、
前記金属円筒に、雄ねじ部を外周面に有する治具を、前記治具の雄ねじ部が前記金属円筒の雌ねじ部に螺合するよう取り付ける治具取付工程と、
下記(A)、(C)、および(D)を満たす条件で前記金属製容器に対して内圧を付与する内圧付与工程と、
前記治具を前記金属容器から取り外す治具取外し工程と、
前記蓋の雄ねじ部が前記金属円筒の雌ねじ部に螺合するよう前記金属円筒に前記蓋を締付ける蓋締付工程とを備え、
前記蓋締付工程においては、前記雌ねじ部および前記雄ねじ部の複数のねじ底における、前記ねじ底から深さ方向に0.4mmの位置における残留圧縮応力の最大値が0超となるように締付トルクを調整する、高圧ガス用容器の製造方法。
(A)前記雌ねじ部のねじ底応力が前記金属円筒の材料の降伏応力より大きい
(C)前記金属円筒の軸方向応力が前記金属円筒の材料の引張強度以下
(D)前記金属円筒の周方向応力が前記金属円筒の材料の引張強度以下
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