Frp Vessel Design as Per ASME Sec X

International Journal of Emerging Technology and Advanced Engineering Website: www.ijetae.com (ISSN 2250-2459, ISO 9001:2008 Certified Journal, Volume 4, Issue 11, November November 2014)

Design of Fiber Reinforced Plastic Pressure Vessel by ASME Section X A. A. Shaikh1, Rajiv A. Mistry 2, 1

Associate Professor, Mechanical Engg. Dept., S.V. National Insti tute of Technology, Surat (India) 2 Deputy General Manager, Essar Learning Centre, Essar Steel India Ltd., Hazira, Surat (India) 1

2

[email protected] [email protected]

Abstract — One Glass Fiber Reinforced Plastic pressure vessel, 2 subjected to internal design pressure of 1.089 kg/cm (15.5 psig) was designed in accordance with the procedures set out in ASME Section X, mandatory design rules for class II vessels with Method A - Design Rules. Destructive testing was done to find out the modulus of elasticity and flexural modulus as per ASME Section X. All the design factors were considered and designed the safe pressure vessel.

Ss

Secondary bond strength in shear (1000 psi maximum)

r

Internal radius of nozzle (in.)

F

Design factor

t b

Thickness of secondary overlay on nozzle (in.)

t p

Thickness of reinforcement pad on shell (in.)

β

Beta factor

K t

Stress concentration factor

— ASME Keywords — ASME Section X, Design Factor, Design of GlassFiber Reinforced Plastic Pressure Vessel, Material Testing, Reinforcement Reinforcement Pad Dimensions.

Smax

Maximum stress at the opening (psi)

M

Moment associated with S max

Sf

Allowable stress [0.001times E f (psi)]

Nomenclatures

L p

Length of reinforcing pad on shell (in.)

Lc

Maximum chord length of the opening (in.)

E1

Tensile modulus in axial direction (psi)

E2

Tensile modulus in hoop direction (psi)

E1f

Flexural modulus in axial direction (psi)

E2f

Flexural modulus in hoop direction (psi)

ν1

Poisson‘s ratio for stress in axial direction and contraction in hoop direction

ν2

Poisson‘s ratio for stress stress in hoop direction and contraction in axial direction

P

Hydrostatic pressure pressure vessel (psi)

Pd

Design Pressure (psi)

γ

The product of specific gravity to weight density of water

h

The vertical distance of the component to the surface of the liquid contents

t

Shell thickness (in.)

R

Inside radius of shell (in.)

L b

Length of secondary overlay on nozzle (in.)

at

particular component

I.I NTRODUCTION Glass-Fiber-Reinforced Plastic (GRP) pressure vessels are widely used in industry particularly in the chemical and process industries. The main reasons for this are GRP material has good corrosion resistance, low weight but high strength and high stiffness. It is specially used in making chemical processing tanks and pressure vessels. These tanks and vessels are usually large in size. Pipe branch connections, manholes etc. in the vessels are very common and are potential weak points. These opening contain discontinuities in the structure. The large size combining with the discontinuities limit the operating pressure of these vessels. Each tank and vessel is custom made and they are different. Economic consideration does not allow manufacturers to destructively test one vessel to prove that another identical one meets the design requirements. These vessels therefore fall under the standard code.

of

For design and fabrication of FRP pressure vessels, ASME has published Boiler and Pressure Vessel Code ―Section ―Section X: Fiber-Reinforced Fiber-Reinforced Plastic pressure vessels‖ [1]. 523


Work has been reported for investigation of design of FRP vessels based on philosophy of ASME Boiler and Pressure Vessel Code. Hisao Fukunaga et al. [2] discussed the optimum design of helically wound composite pressure vessels. J. Blachut [3] analysed filament wound torispheres under external pressure. Paul et al. [4] discussed damage criterion approach to design fiber reinforced vessel. Baoping Cai et al. [5] presented reliability-based load and resistance factor design of composite pressure vessel under external hydrostatic pressure.

specimen and the test were conducted in general accordance with the procedures set out in ASTM D 790: Standard Test Methods for Flexural Properties of Unreinforced and Reinforced Plastics and Electrical Insulating Materials [7]. Table I shows the mean value of flexural modulus for eight specimens.

Work related to investigation of design of FRP pressure vessels based on philosophy of ASME Boiler and Pressure Vessel Code has been reported but very little work has been reported about the step by step procedure for the design of various components of FRP pressure vessel and selection of dimensions of certain components as per the standards given in ASME section X. The present work deals with the design of small FRP pressure vessel subjected to internal design pressure of 15.5 psig with methodology given in ASME Section X including material testing. After design, this vessel will be fabricated and burst test will be carried out by applying hydrostatic pressure for research work.

Fig. 1 Tension Specimens.

II. MATERIAL TESTING Fig.2 Flexural Test Specimens.

As per the methodology of ASME, section X, to design FRP pressure vessel, mechanical properties of FRP material like Modulus of Elasticity, Flexural Modulus and Poisson‘s Ratio are required. To find out these properties one flat sample panel was manufactured. The thickness was taken as per ASTM D 3039: Standard Test Method for Tensile properties of Polymer Matrix Composites Materials [6]. The selection of resin and fiber for this panel was done as per ASME Section X. It was manufactured from Isophthalic Polyester resin and ‗E‘ glass fiber, Chopped Strand Mat (CSM) by a commercial fabricator using a hand lay-up technique. After design, one small FRP pressure vessels will also be made by the same resin, fiber, fabrication method and manufacturer. Tension tests were carried out on specimens cut from flat sample panel. Seven specimens of the same type were cut which are shown in Fig.1.The standard dimensions of specimens and the test was conducted in general accordance with the procedures set out in ASTM D 3039. Table 1 shows the mean value of Modulus of Elasticity for seven specimens. To find out Flexural Modulus of elasticity of material, eight specimens of the same type were cut from the sample panel which is shown in Fig. 2. T he standard dimensions of

For Chopped Stand Mat made by glass fiber and polyester resin, the Poisson‘s Ratio varies in between 0 .30 to 0.34.[8] For design purpose of FRP pressure vessel the value of Poisson‘s Ratio has been taken as 0.32. TABLE I MECHANICAL PROPERTIES OF TEST SPECIMEN (LAMINA PROPRTTIES)

Mean value of Modulus of Elasticity for 7 specimens.

184714.27 psi

Mean Value of Flexural Modulus for 8 Specimens.

938131.58 psi

Poisson‘s Ratio Ratio

524

0.32


Method A was used to design the vessel. It will be constructed of mat laminate with contact molding method. Section X requires the use of lamina properties coupled with lamination analysis to determine the laminate properties for use in method A design. These properties were used together with the lamination theory equations in Section X, Article RD-12 to obtain the mechanical properties of the mat laminate listed in Table III.

III DESIGN OF FRP PRESSURE VESSEL ASME Section X has two classes of vessels: I and II, both of which differ in scope. The classes are distinguished as follows: 1) Class I vessel design is qualified through possibly destructive fatigue and pressure testing of a prototype. 2) Class II vessel design is qualified through mandatory design rules and non-destructive acceptance testing, which includes an Acoustic Emission examination. In present work, class II vessel design approach was used. The pressure scope for Class II vessels is more complicated, depending on the size of the vessel. There are two methods for design calculations of Class II Vessels: Method A that uses design rules, and Method B that provides for design by b y stress analysis. I rrespective t o class c lass or methods, Section X vessels must be between 6 in. and 192 in. in internal diameter. Vessels designed by Method A are limited to 100 psi internal design pressure and 144 in. internal diameter. Vessels designed by Method B rules shall have pressure and diameter restrictions as follows: 1.

2. 3.

Fig. 3: Overall dimensions of shell and nozzle with nozzle location. TABLE II SPECIFICATION OF NOZZLE

The algebraic product of the internal pressure in psig and the diameter in inches shall not exceed 14,400 lb/in.

Mark

The maximum internal pressure shall not exceed 250 psig.

A

The maximum inside diameter shall not exceed 192 in.

Nominal

Elevation

Orientation

Size (in.)

(in.)

(Deg.)

3

6

90

Location

Shell

TABLE III LAMINATE PROPERTIES FOR DESIGN CALCULATIONS

Vessels may be designed using a combination of Methods A and B. For such vessels the maximum design pressure is limited to 100 psig with a maximum inside diameter of 144 in. Vessels designed by either Methods A or B are limited to a maximum external pressure of 15 psig.

Tensile modulus direction(E1) Tensile modulus direction(E2)

in

axial

184714.27 psi

in

hoop

184714.27 psi

axial

938131.58 psi

hoop

938131.58 psi

axial hoop

0.32

hoop axial

0.32

Flexural modulus in direction(E1f ) Flexural Direction in direction(E2f ) Poisson‘s ratio for stress in direction and contraction in direction(ν1) Poisson‘s Poisson‘s ratio for stress in direction and contraction in direction(ν2)

In present work, Method A was used and the internal diameter of vessel was considered as 12 in. (304.8 mm) and internal design pressure of vessel was considered as 15.5 psi. (106.868 kPa.). Fig. 3 shows the overall dimensions of shell and nozzle with nozzle location. The specification of nozzle has been given in Table II. A. Design Calculation The vessel was designed with the methodology of ASME Section X, Class II vessel. In this approach also 525


Component Pressure: Pressure: After design, this vessel will be fabricated and burst test will be carried out by filling the vessel with water and applying hydrostatic pressure. So in this case the internal pressure used in design computations for each component is the sum of the design pressure and the hydrostatic pressure at the component. This pressure (P) is given by the following

minimum thickness of shell required is t = 0.5614 in. (14.2613 mm)

Nozzle, nozzle attachments and reinforcing pad design: Table RD-620.1 of ASME Section X gives the dimensions of nozzles and their flanges constructed of hand layup and pressure-moulded FRP. Nozzles and flanges of these dimensions satisfy the design requirements of Section X. Flanges or nozzle designs not listed in this table can be designed by using Article RD-1176. Table V lists the nozzle and nozzle flange dimensions and Table VI lists the shell flange dimensions for the test vessel, which were taken from Table RD-620.1 of ASME section X and are for 25 psig internal pressure. Article RD-1174 of ASME section X gives the methodology to design the reinforcement for openings in shell and head. Typical dimensions of reinforcement pad and nozzle overlay are given in Fig. 4. For the reinforcing pad and the nozzle overlay to be fully defined, criteria (I) through (IV) below must be met.

Where Pd = the design pressure, γ = the product of specific gravity to weight density of water = 1 X 0.0361 lb/in3 = 0.0361 lb/in3, h = the vertical distance of the component to the surface of the liquid contents. The external pressure is the same for all components that is atmosphere pressure. Table IV lists the component wise internal pressures for different components. TABLE IV COMPONENT WISE INTERNAL PRESSURE

Component

h ( in.)

P (psig)

Shell

24

16.3664

Nozzle A

12

15.9332

Design of Shell: Article Shell: Article RD-1171.1 of ASME section X gives the following rule for the minimum thickness of a cylindrical shell subjected to internal pressure. The minimum thickness of cylindrical shells under internal pressure s hall be greater of (a) and (b) below, but not less than ¼ in. (6 mm). (a) Longitudinal Stress t1 = (b)

Fig.4: Dimensions of reinforcing pad and nozzle overlays [1]

Circumferential Stress

t2 =

I) Length of secondary overlay on nozzle (L b ): The secondary bond length, L b on the nozzle shall be sufficient to withstand the internal pressure acting against the crosssectional area of the nozzle.

Where t1= structural wall thickness for longitudinal stress, t2= structural wall thickness for circumferential stress, P = internal pressure = 16.3664 psig (Table IV), R= inside radius of shell = 6 in. So for above values, t 1 = 0.2807 in. and t 2 = 0.5614 in. and hence the internal pressure hoop stress governs, and the

L b =

or 3 in, whichever is greater.

TABLE V: NOZZLE AND NOZZLE FLANGE DIMENSIONS [1]

Mark A

Nominal Size(in.) 3

Flange OD(in.) 7 1/2

Bolt Circle ( in.) 6

Bolt Hole Dia. (in.) 3/4

Bolt Size(in.) and Number 5/8 and 4

Flange Thickness (in.) 1/2

Nozzle Thickness (in.) 1/4

TABLE VI:SHELL FLANGE DIMENSIONS [1]

Nominal Size(in.) 12

Flange OD(in.) 19

Bolt Circle (in.) 17

Bolt Hole Dia. (in.) 1

Bolt Size(in.) and Number 7/8 and 12

526

Flange Thickness(in.) 13/16

Shell Thickness (in.) 0.5614 (As per design calculations)


Where P = Internal pressure which is 15.9332 psi (Table IV), r = Internal radius of nozzle which is 1.5 in.,Ss = secondary bond strength in shear which is 1000 psi maximum as per ASME section X and F= Design Factor which is 5 for external pressure on cylinders and 10 for external pressure on spheres and heads and internal pressure on reinforcements as per ASME section X. So for test vessel F= 10. By putting above values one gets L b = 0.1194 in. which is less than 3 in. So L b = 3 in.(76.2 mm).

Step 2: Figure 2: Figure RD-1174.3 of ASME section X, gives the value of stress concentration factors (K t) for a circular hole in a pressurized cylindrical shell. For test vessel the value of K t for membrane plus bending from this graph is K t = 5 Step 3: 3: Compute maximum stress at the opening which is given by

II) Thickness of secondary overlay on nozzle (t b ): ): The secondary overlay thickness t b on the nozzle shall be sufficient to withstand the nozzle internal pressure. t b =

Smax = S2K t Where S2 = allowable stress for the shell laminate in the circumferential direction, defined as 0.001 E 2 = 0.001 x 184714.27 psi = 184.7142 psi

or 0.25 in., whichever is greater

So Smax = 923.57 psi

By putting values one gets t b = 0.0241 in. which is less than 0.25 in. So t b = 0.25 in. (6.35 mm).

Step 4: 4: Determine the moment M associated with the stress Smax being applied at the edge of the opening. Assume a moment beam 1 in. wide and having a thickness equal to the shell thickness, with the stress decreasing away from the edge of the opening.

III) Thickness of reinforcement pad on shell or head (t p ): The thickness t p of the reinforcing pad shall be the greater of (1) and (2) below: (1) a thickness of secondary overlay with strength equivalent to the tensile strength in the circumferential direction of the shell thickness removed :

M

=

Where t= vessel shell thickness = 0.5614 in So M = 48.5135 in. lb/in.

t p = Step 5: 5: Determine the thickness of reinforcement that will reduce the stress imposed by the moment M to the allowable Sf , defined as 0.001E f , Assume an effective equivalent moment to be M/2.

By putting values one gets t p = 0.5175 in. (2) a thickness of secondary overlay, which when added to the shell thickness, will reduce the bending stress at the opening to an allowable level. The allowable bending stress shall be defined as 0.1% of the flexural modulus of the reinforcing laminate in its circumferential direction. It will be calculated as follows.

t p

Step 1: Compute 1: Compute Beta factor β

(

Where Sf = allowable stress, defined as 0.001 E f . Here Ef is nothing but the flexural modulus of reinforcing laminate in the circumferential direction which is equal to 938131.58 psi (Table III). t = thickness of vessel shell = 0.5614 in. By putting above values, one can find out thickness of reinforcing pad (t p) as t p= -0.1675 in. The thickness of the reinforcing pad shall be the greater of the thickness computed for (1) and (2) above. So t p= 0.5175 in.(13.1457 mm)

)

Putting R = 6 in., r = 1.5 in., t = thickness of shell =0.5614 in and ν1, ν2 equal to 0.32 and 0.32 respectively one gets β= β= 0.5234

527


IV) Length of Reinforcing Pad on shell (L p ): ): The reinforcing pad shall project a distance L p from the edge of the opening. The distance L p shall be at least as great as the greater of (1) and (2) below. The pad shall terminate in a taper over an additional distance six times the thickness of the pad. (1) (1) A secondary bond area on the shell shall provide sufficient shear area to resist the internal pressure force on the nozzle. By convention this area will be expressed in terms of a distance L p that the reinforcing pad will extend out from the nozzle and will be computed as follows:

1) Shell Thickness (t) = 0.5614 in. 2) Length of secondary overlay on nozzle (L b) = 3 in. 3) Thickness of secondary overlay on nozzle (t b) = 0.25 in. 4) Thickness of reinforcement pad on shell (t p) = 0.5175 in. 5) Length of Reinforcing Pad on shell (L p) = 3 in. 6) Nozzle flange thickness = 0.5 in. 7) Nozzle thickness = 0.25 in. 8) Shell flange thickness = 0.8125 in. Acknowledgement The authors are greatly indebted to the M/S Rangoli Fiber Reinforced (P) Ltd., Vapi, for providing support during the fabrication of flat sample panel.

L p Where F= design factor = 10,L c = Longest chord length of opening = 3 in., P = internal pressure = 15.9332 psi, S s= Secondary bond shear strength= 1000 psi Lc is the maximum chord length of the opening. Hill side nozzles and those nozzles installed in the shell so that the nozzle axis does not intersect the shell axis have L c greater than the nozzle diameter. The nozzle A centreline intersects the vessel centreline and is normal to it so that L c = 3 in. By putting above values in equation for L p, one gets L p = 0.3754 in.

References [1] ―Section X: Fiber -Reinforced Plastic pressure vessels‖, ASME Boiler and Pressure Vessel Code, (2007) [2] Hisao Fukunaga & Masuji Uemura, ―Optimum Design of Helically Wound Composite Pressure Press ure Vessels‖, Composite Structures, 1 (1983) 31-49 [3] J. Blachut, ―Filament wound torisphere under external pressure‖, Composite Structures 26 (1993) 47-54 [4] Paul H. Ziehl & Timothy J. Fowler, ―Fiber reinforced vessel design with a damage criterion‖, criterion‖, Composite Structures 61 (2003) 395- 411 [5] Baoping Cai, Yonghong Yonghong LiuZengkai Liu, Liu, Xiaojie Tian, Renjie Renjie Ji, Hang Li, ―Reliability-based ―Reliability-based load and resistance factor design of composite pressure vessel under external hydrostatic pressure‖ , Composite Structures 93 (2011) 2844 – 2844 – 2852 2852 [6] ASTM D 3039: 3039: Standard Test Method for Tensile properties properties of Polymer Matrix Composites Materials. (2008) [7] ASTM D 790: Standard Test Test Methods for Flexural Flexural Properties Properties of Unreinforced and Reinforced Plastics and Electrical Insulating Materials. (2002) [8] K.R.Rao, ―Companion Guide to the ASME Boiler and Pressure Vessel Code‖, Volume 2, Third Edition, Chapter 25(2009)

(2) Minimum (2) Minimum Reinforcing Pad Requirements (a) For nozzles 6 in. diameter and less, L p shall be at least as great as Lc. (b) For nozzles greater than 6 in. (152 mm) diameter, but less than or equal to 12 in. (305 mm) diameter, L p = 6 in. or ½ Lc, whichever is greater. (c) For nozzles greater than 12 in. diameter, L p shall be at least as great as ½ L c. See Fig. 4 So for test vessel, the diameter of nozzle is 3 in. which is less than 6 in. so L p shall be at least as great as L c. that is 3 in. So finally L p = 3 in.(76.2mm) IV CONCLUSION In the present work, an attempt has been made to design glass-fiber reinforced plastic pressure vessel 2 subjected to internal pressure of 1.089 kg/cm (15.5 psig).Design is based on general accordance with the procedures set out in ASME Section X, mandatory design rules for class II vessels with Method A - Design Rules. All the design factors were considered and designed the safe pressure vessel. Following dimensions of FRP pressure vessel and reinforcement pad are drawn from present design. 528

Frp Vessel Design as Per ASME Sec X

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