US3871313A - Method for increasing the strength of a multiple-layer shell type cylindrical presssure vessel - Google Patents

Method for increasing the strength of a multiple-layer shell type cylindrical presssure vessel Download PDF

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Publication number
US3871313A
US3871313A US389262A US38926273A US3871313A US 3871313 A US3871313 A US 3871313A US 389262 A US389262 A US 389262A US 38926273 A US38926273 A US 38926273A US 3871313 A US3871313 A US 3871313A
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Prior art keywords
shell
bending
vessel
solid wall
strength
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Expired - Lifetime
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US389262A
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English (en)
Inventor
Takeshi Yamauchi
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Kobe Steel Ltd
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Kobe Steel Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J12/00—Pressure vessels in general
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49826—Assembling or joining
    • Y10T29/49908—Joining by deforming

Definitions

  • the method provides at least one of such transition points a circumferential weld extending throughout the wall thickness of the shell or provides a solid wall type shell section extending from the joint between the head plate and the shell to the first transition point or pro vides a solid wall type shell section between the two transition points, thereby increasing the bending rigidity or strength at such transition points for the cyli11- drical pressure vessel.
  • This invention relates to a method for increasing the strength of a multiple-layer shell type cylindrical pressure vessel, and more particularly to a multiple-layer shell type cylindrical pressure vessel, the shell of which tends to present a sine-curve like bending behavior due to the bending force created at or in the vicinity of the weld joint between the head plate and the shell of said vessel by virtue of the inner pressure being applied to said vessel.
  • the multiple-layer shell type cylindrical vessel is used as a pressure vessel such as reactor or autoclave and thus is directly subjected to inner pressure.
  • the stress behavior created in the vessel shell due to the inner pressure is similar to that of the vessel having a solid wall type shell. such that it is a common practice to apply the same stress calculation method to both cases.
  • a close study of the stress behavior has revealed that what is important is the secondary or local bending caused in every portion of the vessel rather than the primary stress which is caused by the inner pressure. regardless of whether the vessel is of a solid wall type shell or of a multiple-layer type shell.
  • the calculation of the bending rigidity or bending force at the edge of the shell may be done in a similar manner to that of the pressure cylinder of a solid wall type shell.
  • the bending rigidity thereof will be smaller as compared with the solid wall shell type vessel if the ordinary calculation method is utilized.
  • the bending force. which is created secondarily at the edge portion adjacent to the weld joint between the shell and the head plate, is associated with the bending rigidity at such edge portion. and thus the smaller the rigidity. the smaller the bending force.
  • FIG. 1 is a cross-sectional view illustrative of a multiple-layer shell type cylindrical pressure vessel having bending curvatures similar in shape to a sine-curve. with the transition points in the bending-direction shown;
  • FIG. 2 is a cross-sectional view of one embodiment of a pressure vessel of the type described. showing circumferential welds provided in the shell at the transition points in the bending-direction according to the present invention
  • FIG. 3 and FIG. 4 are cross-sectional views of the shell of a pressure vessel using a section of solid wall type shell between the two transition points in the bending-direction so as to increase bending rigidity of a pressure vessel rather than the use of circumferential weldings;
  • FIGS. 5 and 6 are explanatory views of the multiple layer shell of a pressure vessel. referring to bending curvatures and transition points in the bending direction.
  • FIG. I whereon there is shown a shell of a cylindrical pressure vessel which shell is subjected to deformation or secondary bending caused by bending and shear forces at or in the vicinity of the welding joint between the shell and the head plate of the pressure vessel.
  • FIG. I there is shown a series of continuous bending curvatures appearing alternately on opposite sides with respect to the neutral line of the bending curvatures.
  • transition points in the bending-direction at 1,2,3, and The position of the first transition point in the bending-direction as viewed from the left in the figure depends on the correlation of the transition point to the weld joints with the head plates on the opposite edges of a vessel.
  • the positions of the transition points appear at spacings ll, 12 and 13 which are claculated by the diameter, wall thickness. bending rigidity, etc. of a cylinder, regardless of the external forces.
  • FIG. 5 shows a multiple-layer shell type pressure vessel which undergoes bending in one direction and thus has no transition point in the bending-direction.
  • FIG. 6 is a view similar to FIG. 5, but the bending has two directions of curvature and hence has one transition point in the bending-direction.
  • the transition points in the bending-direction appear at three points spaced 315 mm, 850 mm and 1,310 mm in the shell from the weld joint between said shell and the head plate of a pressure vessel.
  • another transition point appears at a distance of 1.500 mm from the aforesaid welding joint or the edge of the shell of a vessel.
  • circumferential weldings are provided through the wall thickness at four points, 5, 6, 7 and 8, as shown in FIG. 2, thus increasing the bending rigidity of a multiple-layer shell type pressure vessel.
  • the reason why the first three points do not appear at the same spacings is that the second point is determined by assuming the first point being a fixed or rigid point, i.e., the rigidity at such a point is increased by providing a circumferential welding throughout the wall thickness of the shell. In other words, this span is assumed as a solid wall type shell section.
  • the position of the third point is determined in the same manner, with the result of providing a spacing different from those of the first two points.
  • solid wall type shell sections may alternatively be used in place of such circumferential welds as is shown at 9 in FIG. 3. If two or more such solid wall type shell sections are continuous with each other, then there is no need to provide circumferential welding at the interface of such two shell sections. Furthermore, a substantial length of the shell portion may be replaced by the solid wall type shell section, as shown at 10 in FIG. 4.
  • the calculation of bending rigidity of the cylindrical wall or shell is generally in accordance with Timoschenkos calculation method (Timoschenko: Theory of Plates and Shells, A.SM.E. Code Section VII, Div. 2).
  • Timoschenkos calculation method Tischenko: Theory of Plates and Shells, A.SM.E. Code Section VII, Div. 2.
  • the total bending rigidity of a bending beam which has a given depth or thickness as well as a given typical radium of curvature running along the bending neutral line of the thickness. is obtained by integrating the individual rigidity of the imaginary longitudinal sections or layers included in the beam and ex tending from the inner side to the outer side of the beam. In this case, if the superposed layers maintain their relative positions, i.e.
  • the same bending rigidity may be obtained, whether the pressure vessel is of a solid wall type shell or a multiple-layer type shell.
  • the multiple-layer type shell in this case, corresponds to the case where multiple-layers maintain their mutual relative positions i.e,, cause no relative slippage.
  • the radius of curvature of the bend created between the transition point 1 and the edge of the shell adjoining the head plate appears on the upper side of the bending neutral line, and after passing through the transition point 1, it appears on the lower side of the neutral line.
  • the circumferential weld is provided at such transition point in the multiple-layer shell of a pressure vessel then the relative position with no slippage between the layers may be maintained with the result that the same assumption may be applied to the multiple-layer shell as that of the solid wall type shell.
  • the aforesaid consideration includes the assumption that the multiple-layer type shell would not be subjected to buckling or instable failures. To prevent instable failures such as buckling, it is a common practice to use an increased thickness of the innermost layer.
  • the positions of the transition points are dependent on the dimensions of the shell and head plate regardless of the levels of the inner pressure and temperature prevailing in the shell.
  • the aforesaid measures such as using a circumferential welding or solid wall type shell section, may be applied effectively.
  • the embodiment of the present invention which uses a solid wall type shell section in place of the circumferential weld may avoid complexity in production, thus presenting a considerable economic saving.
  • said shell of more than one section wherein at least one of said sections is constructed of more than one layer, providing a circumferential weld between one ofsaid head plates and one of said sections, and

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pressure Vessels And Lids Thereof (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
US389262A 1972-08-17 1973-08-17 Method for increasing the strength of a multiple-layer shell type cylindrical presssure vessel Expired - Lifetime US3871313A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP8239572A JPS545124B2 (ja) 1972-08-17 1972-08-17

Publications (1)

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US3871313A true US3871313A (en) 1975-03-18

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US (1) US3871313A (ja)
JP (1) JPS545124B2 (ja)
FR (1) FR2196697A5 (ja)
NL (1) NL7311165A (ja)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4095594A (en) * 1977-02-15 1978-06-20 Institut Electrosvarki Imeni E.O. Patona Akademii Nauk Ukrainskoi Ssr Method of manufacturing laminated shells
US5150831A (en) * 1989-04-28 1992-09-29 The B. F. Goodrich Company Reactor vessel
US20040247472A1 (en) * 2003-06-09 2004-12-09 Horton William Travis Multi-layer compressor housing and method of manufacture
US20220212136A1 (en) * 2019-05-08 2022-07-07 Linde Gmbh Pressure vessel

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62190176U (ja) * 1986-05-24 1987-12-03
CN111702412A (zh) * 2020-04-22 2020-09-25 安徽帮德电气有限公司 一种压力容器的制造方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3231338A (en) * 1962-04-19 1966-01-25 Chicago Bridge & Iron Co Multi-layer pressure vessel for high temperature hydrogenation processes
US3565275A (en) * 1966-10-06 1971-02-23 Mitsubishi Heavy Ind Ltd Hydrogen embrittlementproof vessel of layer
US3680584A (en) * 1971-02-22 1972-08-01 Babcock Atlantique Sa Welding construction for multilayered devices
US3704509A (en) * 1969-07-05 1972-12-05 Kobe Steel Ltd Annealing for stress relieving of multilayer pressure vessels

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3231338A (en) * 1962-04-19 1966-01-25 Chicago Bridge & Iron Co Multi-layer pressure vessel for high temperature hydrogenation processes
US3565275A (en) * 1966-10-06 1971-02-23 Mitsubishi Heavy Ind Ltd Hydrogen embrittlementproof vessel of layer
US3704509A (en) * 1969-07-05 1972-12-05 Kobe Steel Ltd Annealing for stress relieving of multilayer pressure vessels
US3680584A (en) * 1971-02-22 1972-08-01 Babcock Atlantique Sa Welding construction for multilayered devices

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4095594A (en) * 1977-02-15 1978-06-20 Institut Electrosvarki Imeni E.O. Patona Akademii Nauk Ukrainskoi Ssr Method of manufacturing laminated shells
US5150831A (en) * 1989-04-28 1992-09-29 The B. F. Goodrich Company Reactor vessel
US20040247472A1 (en) * 2003-06-09 2004-12-09 Horton William Travis Multi-layer compressor housing and method of manufacture
US7179061B2 (en) * 2003-06-09 2007-02-20 Tecumseh Products Company Multi-layer compressor housing and method of manufacture
US20220212136A1 (en) * 2019-05-08 2022-07-07 Linde Gmbh Pressure vessel

Also Published As

Publication number Publication date
NL7311165A (ja) 1974-02-19
JPS4938208A (ja) 1974-04-09
JPS545124B2 (ja) 1979-03-14
DE2341765A1 (de) 1974-03-07
FR2196697A5 (ja) 1974-03-15
DE2341765B2 (de) 1976-02-05

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