# US 12,006,011 B2 · Pyram-shaped deep-sea pressure-resistant shell and design method thereof > Agents: this data is available as JSON from the patentgrep API and MCP server — see https://patentgrep.com/llms.txt - Number: US 12,006,011 B2 - Document ID: US12006011B2 - Status: Granted - Kind: B2 - Application number: 18/276,451 - Filed: 2022-03-18 - Published: 2024-04-11 - Granted: 2024-06-11 - Earliest claimed: 2021-11-16 - Assignees: Jiangsu University of Science and Technology - Applicants: Jiangsu University of Science and Technology - Inventors: Jian Zhang; Xiaobin Liu; Chenyang Di; Ming Zhan; Yongsheng Li; Tan Zhao; Fang Wang; Wenxian Tang - Web page: https://patentgrep.com/patent/US12006011B2 ## CPC - B63G 8/04: Superstructure - G06F 30/17: Mechanical parametric or variational design - B63B 3/13: Hulls built to withstand hydrostatic pressure when fully submerged, e.g. submarine hulls - Y02T 90/00: Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation - B63G: OFFENSIVE OR DEFENSIVE ARRANGEMENTS ON VESSELS; MINE-LAYING; MINE-SWEEPING; SUBMARINES; AIRCRAFT CARRIERS (means of attack or defence in general, e.g. turrets F41H) - G06F: ELECTRIC DIGITAL DATA PROCESSING (computer systems based on specific computational models G06N) - B63B: SHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING (arrangements of vessel ventilation, heating, cooling, or air-conditioning B63J2/00; floating substructures as supports of dredgers or soil-shifting machines E02F9/06) - Y02T: CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION ## Abstract A pyram-shaped deep-sea pressure-resistance shell and a design method therefor. The shell comprises a conical shell, an annular combined shell, a cylindrical shell, a flange bolt, and a perforated thick plate; a bottom end of the conical shell is connected with a top end of the annular combined shell, the conical shell being in communication with an interior part of the annular combined shell; the perforated thick plate blocks the bottom end of the annular combined shell, the perforated thick plate and the annular combined shell being connected by means of multiple flange bolts; the cylindrical shell is disposed inside the annular combined shell, a lower end of the cylindrical shell being inserted in a gap between the annular combined shell and the perforated thick plate. ## Claims ### Claim 1 A pyram-shaped deep-sea pressure-resistant shell, comprising a conical shell, an annular combined shell, a cylindrical shell, a flange bolt, and a perforated thick plate; wherein a bottom end of the conical shell is connected with a top end of the annular combined shell, an interior part of the conical shell is in communication with an interior part of the annular combined shell; the perforated thick plate blocks a bottom end of the annular combined shell, the perforated thick plate and the annular combined shell are connected by means of multiple flange bolts; the cylindrical shell is disposed inside the annular combined shell, a lower end of the cylindrical shell is inserted in a gap between the annular combined shell and the perforated thick plate, and an upper end of the cylindrical shell and the lower end of the cylindrical shell are respectively connected to an inner peripheral surface of the annular combined shell. ### Claim 2 (depends on 1) The pyram-shaped deep-sea pressure-resistant shell according to claim 1, wherein the annular combined shell includes a first annular shell, a second annular shell and a third annular shell connected from an upper end of the annular combined shell to a lower end of the annular combined shell in sequence, and the first annular shell, the second annular shell and the third annular shell are internally connected, an upper end of the first annular shell is connected to the conical shell, a bottom end of the third annular shell is connected to the perforated thick plate, the cylindrical shell is arranged inside the third annular shell. ### Claim 3 (depends on 2) The pyram-shaped deep-sea pressure-resistant shell according to claim 2, wherein an outside peripheral surface of the cylindrical shell is provided with at least two channels, such that the first annular shell, the second annular shell and the third annular shell are interconnected with each other. ### Claim 4 (depends on 2) The pyram-shaped deep-sea pressure-resistant shell according to claim 2, wherein outer shell surfaces of the first annular shell, the second annular shell and the third annular shell are all circular arc surfaces, with outer diameters of the first annular shell, the second annular shell and the third annular shell increasing in sequence, and centers of circular cross-sections of the circular arc surfaces of the first annular shell, the second annular shell and the third annular shell are all located on an extension line of an outer profile of the conical shell. ### Claim 5 (depends on 2) The pyram-shaped deep-sea pressure-resistant shell according to claim 2, wherein the conical shell, the first annular shell, the second annular shell and the third annular shell are sequentially welded and fixed into a whole. ### Claim 6 (depends on 1) The pyram-shaped deep-sea pressure-resistant shell according to claim 1, wherein the flange bolt includes a bolt, a first flange, a sealing ring, a second flange, a washer and a nut, the first flange is fixed to a bottom surface of the annular combined shell, the second flange is fixed to a bottom surface of the perforated thick plate, the bolt is threaded and arranged in the first flange and the second flange in sequence, such that the first flange and the second flange are in securely threaded-connection with each other through the nut, the sealing ring is arranged between a connection surface of the first flange and the second flange, and the washer is arranged between a contact surface of the nut and the second flange. ### Claim 7 (depends on 2) A method of designing the pyram-shaped deep-sea pressure- resistant shell according to claim 2 comprising following steps: Step 1, given that a height of an isosceles triangle inside the pyram-shaped deep-sea pressure-resistant shell is H, then: H=(L+2r2+2r3+2r4)cos α; where L represents a length of a generatrix of the conical shell, r2 represents a circumference radius of the first annular shell, r3 represents a circumference radius of the second annular shell, r4 represents a circumference radius of the second annular shell, and α represents a half-cone angle; obtaining, through design values for circular radii of the shells, rotation radii of the conical shell, the first annular shell, the second annular shell, the third annular shell and the cylindrical shell by calculation; Step 2, given that a thickness of the conical shell is t1:t1=Max{t1e,t1b}; wherein t 1 ⁢ e = 3 ⁢ pR 1 8 [ σ ] ⁢ cos ⁢ α ; and t 1 ⁢ b = 0.75 pK 1 ( R 1 + r ) [ σ ] ⁢ cos 2 ⁢ α ; where p represents a calculated pressure, [σ] represents an allowable stress, α represents the half-cone angle, R1 represents a radius of a large end of the conical shell, r represents a radius of a small end of the conical shell, and K1 represents a parameter related to reinforcing ribs; a meridional thin film stress σφ, a circumferential thin film stress σθ and an equivalent stress σe of the conical shell being respectively according to a theory of thin shells: σ φ = - p ⁢ R 8 ⁢ t · 1 cos ⁢ α ; σ θ = - p ⁢ R 4 ⁢ t · 1 cos ⁢ α ; and σ e = σ φ 2 + σ θ 2 - σ φ ⁢ σ θ ; substituting the meridional thin film stress σφ and the circumferential thin film stress σθ into the equivalent stress σe, to obtain an equivalent stress of the shell, and determining, based on a criterion of a maximum equivalent stress [σe]max being less than or equal to the allowable stress [σ] of materials, a thickness of a conical shell with equal thickness t1e, in consideration of the maximum equivalent stress [σe]max being equal to the allowable stress [σ] of the materials during design; determining, according to a calculation formula of a buckling load for the conical shell, that is, p = 2 [ σ ] · cos 2 ⁢ α · t 1 . 5 ⁢ K 1 ( R + r ) , a thickness of the conical shell with equal thickness t1b by calculation; respectively calculating the thickness of the conical shell derived from a principle of thin films and the formula of the buckling load above, and determining a maximum thickness of the two as an ultimate thickness of the conical shell; Step 3, given that a thickness of annular shells of the first annular shell, the second annular shell and the third annular shell ti is: ti=Max{tie,tib} (i=2,3,4); wherein t ie = pr i ⁢ 1 + R i R i + r i ⁢ sin ⁢ α + ( R i R i + r i ⁢ sin ⁢ α ) 2 2 [ σ ] ; and t ib = [ p · ( R i 2 r i 5 ) 1 3 0 . 1 ⁢ 738 ⁢ E · ( 1 - μ 2 ) 2 3 ] 3 7 ; where i takes 2, 3, 4, p represents the calculated pressure, [σ] represents the allowable stress, Ri represents a rotating pitch diameter of the annular shell, ri represents a circumference radius of the annular shell, a represents the half-cone angle, E represents an elastic modulus, μ represents a Poisson's ratio; a maximum meridional thin film stress σφ, a maximum circumferential thin film stress σθ and a maximum equivalent stress σe of the annular shell are respectively according to the theory of thin shells: σ φ = - pr 2 ⁢ t · 2 ⁢ R + r ⁢ sin ⁢ α R + r ⁢ sin ⁢ α ; σ θ = - pr 2 ⁢ t ; and σ e = σ φ 2 + σ θ 2 - σ φ ⁢ σ θ ; substituting the maximum meridional thin film stress σφ, and the maximum circumferential thin film stress σθ into the maximum equivalent stress σe, and determining, based on a criterion of the maximum equivalent stress [σe]max being less than or equal to the allowable stress [σ] of materials, a thickness of an annular shell with equal thickness tie, in consideration of the maximum equivalent stress [σe]max being equal to the allowable stress [σ] of the materials during design; expressing, according to Jordan Formula, a critical buckling load for the annular shell as: p = 0 . 1 ⁢ 7 ⁢ 3 ⁢ 8 ⁢ E [ ( t r ) 7 ⁢ ( 1 - μ 2 ) 2 ( R r ) 2 ] 1 3 ; determining, according to the above formula, a thickness of the annular shell with equal thickness tib by calculation; respectively calculating the thickness of the annular shell derived from the principle of thin film and the formula of the load above, and determining a maximum thickness of the two as an ultimate thickness of the first annular shell, the second annular shell and the third annular shell; and Step 4, given that a thickness of the cylindrical shell t5 is: t5=Max{t5e,t5b}; wherein t 5 ⁢ e = 3 ⁢ p ⁢ R 2 [ σ ] ; and t 5 ⁢ b = ( plR 3 2 0 . 9 ⁢ 2 ⁢ E ) 2 5 ; where p represents the calculated pressure, [σ] represents the allowable stress, R represents a rotating radius of the cylindrical shell, l represents a height of the cylindrical shell and E represents the elastic modulus; a meridional thin film stress σφ, a circumferential thin film stress σθ and an equivalent stress σe of the cylindrical shell are respectively according to the theory of thin shells: σ φ = - p ⁢ R 2 ⁢ t ; σ θ = - p ⁢ R t ; and σ e = σ φ 2 + σ θ 2 - σ φ ⁢ σ θ ; substituting the meridional thin film stress σ100 and the circumferential thin film stress σθ into the equivalent stress σe, and determining, based on a criterion of the maximum equivalent stress [σe]max being less than or equal to the allowable stress [σ] of materials, a thickness of a cylindrical shell with equal thickness t5e, in consideration of the maximum equivalent stress [σe]max being equal to the allowable stress [σ] of the materials during design; a calculation formula of a buckling load for the cylindrical shell being: p = 0 . 9 ⁢ 2 ⁢ E ⁢ t l ⁢ ( t r ) 3 2 ; determining, according to the above formula, a thickness of the cylindrical shell with equal thickness t5b; and respectively calculating the thickness of the cylindrical shell derived from the principle of thin films and the formula of the load above, and determining a maximum thickness of the two as an ultimate thickness of the cylindrical shell. ### Claim 8 (depends on 7) The method of designing the pyram-shaped deep-sea pressure-resistant shell according to claim 7, wherein in Step 2, K1=1.