DOI:10.23883/IJRTER.2018.4149.QLJI6 430
DESIGN AND ANALYSIS OF EXPANSION JOINTS AND BELLOWS
S.VARUNRAJ1, SUDHARSAN.K2 1assistant Professor, Mechanical Department, Vels Institute Of Science, Technology And Advanced Studies,
Pallavaram, Chennai-117 2assistant Professor, Mechanical Department, Velammal Engineering College, Velammal Nagar, Ambattur-Red
Hills Road, Chennai - 600 066.
Abstract: An Expansion Joints is an assembly designed to absorb the expansion and contraction of
various construction materials, to absorb vibration, or to allow movement due to ground settlement or
earthquakes. An Expansion joint refers to a metal bellows expansion joint designed to absorb axial,
lateral and angular motions in piping system. The bellows is the flexible element of the expansion joint.
It must be strong enough circumferentially to withstand the pressure and flexible enough longitudinally
to accept the deflections for which it was designed, and as repetitively as necessary with a minimum
resistance. This strength with flexibility is a unique design problem that is not often found in other
components in industrial equipment. Since the bellows must accept deflections repetitively, and
deflections result in stresses, these stresses must be kept as low as possible so that the repeated
deflections will not result in premature fatigue failures. In this project a metal expansion joint along with
the bellows and the entire pipe cross over and the pressure parts in the cross over is designed by
considering above words while designing. In the cross over “In line Pressure Balanced Expansion Joint”
is replaced instead of Single Expansion Joints and Elbow Pressure Balanced Expansion Joints is also
present in the cross over. Pressure is applied in the cross over. Design calculation is done manually.
Then the design is modeled in the software Inventor. Then the model is imported by converting it in to
STEP file format to the software Hyper Works. Finite Element Analysis is continued in the software
Hyper Mesh and the results are compared with the manual results. Based on the results, suggestions are
given to the industry.
I. INTRODUCTION
An expansion joint is simply a bellows element with end connections. Regardless of accessories, such as
liners and covers, it will deflect in any direction or plane that the bellows will. It is the least expensive
type, but requires that the piping be controlled as to the direction of the movements required of the
unit. The expansion joint should not be expected to control the movement of the pipe. If the piping
analysis shows that the expansion joint must accept axial compression, then the piping must be guided
and constrained so that only that movement will occur. This expansion joint will not resist any
deflections with any force other than the resistance of the bellows, which is a function of the spring rate
times the deflection amount. It is incapable of resisting the pressure thrust along its axis, which is the
product of the pressure times the effective, or cross sectional, area of the bellows. Large diameter units,
even with low pressures, can generate very large axial pressure thrust forces, which must be reacted by
main and directional anchors. Otherwise the expansion joint will extend with disastrous results.
The bellows is the flexible element of the expansion joint. It must be strong enough circumferentially to
withstand the pressure and flexible enough longitudinally to accept the deflections for which it was
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designed, and as repetitively as necessary with a minimum resistance. This strength with flexibility is a
unique design problem that is not often found in other components in industrial equipment.
Most engineered structures are designed to inhibit deflection when acted upon by outside forces. Since
the bellows must accept deflections repetitively, and deflections result in stresses, these stresses must be
kept as low as possible so that the repeated deflections will not result in premature fatigue failures.
Reducing bending stress resulting from a given deflection is easily achieved by simply reducing the
thickness of the bending member, which in the case of the bellows, is the convolution. However, in
order to withstand the pressure, the convolution, which is also a pressure vessel, must have a thickness
great enough that the pressure induced membrane stresses are equal to or less than the allowable stress
levels of the materials at the design temperatures. This conflicting need for thickness for pressure and
thinness for flexibility is the unique design problem faced by the expansion joint designer.
Most bellows fail by circumferential cracking resulting from cyclic bending stresses, or fatigue. Since
the best design is a compromise, or balance, between pressure strength and flexibility considerations, it
can be concluded that their designs have had lower margins of safety regarding fatigue than they had
regarding pressure strength. The years of experience of the engineers who developed these bellows
assures that the designs contained in this catalog and those offered to satisfy customer specifications,
will have the performance reliability which yields trouble free, safe use. Occasionally, a bellows will
appear to develop a fatigue crack prematurely, i.e., after being subjected to fewer cycles than analysis
indicates they should.
These premature failures usually are the result of one or more of the following causes:
Insufficient margin of safety in the design permitting acceptance of a unit manufactured within a portion
of the dimensional tolerance range to yield a part which will not satisfy the design. Metallic bellows
bending stresses are extremely sensitive to changes in some dimensions, such as the thickness and the
height of the convolution. These dimensional characteristics often affect the various bending stresses by
the square or cube of their differences. An understanding of these dimensional factors and how they can
be controlled during design and manufacture is the key to preventing this cause of early failure. A poorly
manufactured bellows or one that is made to the "wrong" side of the dimensional tolerances will
disappoint the best design and analysis.
Gh. Faraji et al, stated that “Metal bellows have wide applications in aerospace, micro-
electromechanical and industrial systems. Forming process of the metal bellows is v ery sensitive
to increasing the ratio of crown to root diameter. In this state, precise control of the parameters is very
important in order to form high-quality metal bellows with good thickness distribution and desirable
dimensions and resilience. In this paper, a new method has been proposed for manufacturing of the
metal bellows and important parameters such as initial length of tube, internal pressure, axial feeding
and velocity, mechanical properties and the type of materials were investigated by finite element (FE)
analysis (LS-Dyna) and experimental tests. The explicit time integration method is used for modeling
the tube-bulging and folding processes. Meanwhile, the implicit time integration method is used for the
spring back stage. Finally, the results of finite element method (FEM) and experiments show a very
good agreement. The results of the present work could be used as a basis of designing a new type of the
metal bellows.”
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James F. Wilson stated that “A bellows, or a closed thin-walled elastic tube with corrugated walls,
undergoes longitudinal extension when subjected to internal fluid pressure. Investigated herein is the
mechanical behavior of several pressurized bellows in clusters, which are designed to bend and twist as
well as to extend and compress longitudinally. Bellows in clusters can be employed as robotic limbs,
such as manipulator arms and legs for walking machines. For limb bending, analysis shows that there is
an optimal geometry for satellite bellows, or a set of identical bellows clustered longitudinally about a
central core. For limb torsion, the bellows are clustered in a cylindrical helix whose angle is chosen to
produce the desired load–displacement relationships, for instance the highest rotation for a given torque.
For both bending and torsional limbs, experimental results are included that exhibit the predicted
mechanical behavior.”
Moon Yong Lee stated that “The Tubular bellows are one of the most efficient energy-absorbing
elements for various automotive systems. The conventional manufacturing of metallic tubular bellows
consists of a four-step process: (1) deep drawing, (2) ironing, (3) tube bulging, and (4) folding. In the
present study, a single-step tube hydro forming process is used to make prototype tubular bellows with
simultaneous control of the internal pressure and the axial feed. A number of prototype tubular bellows
were formed with the use of various hydro forming die shapes, such as rectangular, circular, and
triangular. For each shape, the hydro formability of the tubular bellows, in conjunction with the forming
process, was evaluated. The effect of the friction was also investigated. Good lubrication is an effective
method for improving the hydro formability of metallic tubular bellows. The present study shows that a
single-step hydro forming process can be used to form tubular bellows with various shapes”.
G. Wang et al stated that “A new forming technology was developed for bellows expansion joints. This
technology uses super plastic forming (SPF) method of applying gas pressure and compressive axial
load. It is developed and can be used to manufacture large diameter “U” type bellows expansion joints
made of titanium alloys. The forming technology for bellows expansion joints made of titanium alloys is
presented to make a two-convolution bellows expansion joint of Ti–6Al–4V alloy as an example.
Welded pipe bent by a hot bending method with a set of specific dies and welded by plasma arc welding
was used as a tubular blank in the SPF. During the SPF process the tubular blank is restrained in a multi-
layer die block assembly which determines the final shape of convolution. The forming load route is
divided into three steps in order to obtain optimum thickness distribution. This technology can also be
used to fabricate stainless steel bellows expansion joints.”
Y.Z.Zhu et al stated that “As experimental research, the effect of environmental medium on corrosion
fatigue life has been proposed in this paper. The research proves the fact that the presence of corrosive
medium will accelerate both crack initiation and propagation rates and reduce the failure life for the
expansion joints. Furthermore, an important suggestion should be made that the effect of environmental
medium on fatigue life must be paid more attention to when dealing with fatigue analysis for bellows
expansion joints.”
Kaishu Guan et al stated “The failure of a bellow expansion joint of 304 stainless steel has been
analysed. Stress corrosion cracking (SCC) caused by wet hydrogen sulfide was responsible for the
failure. Observation of metallographic sections indicated that the crack is transgranular SCC (TGSCC)
with cracking in a direction perpendicular to axial stress. Scanning electron microscopy (SEM) analysis
of the fracture surface showed that the cracks are cleavage and quasi-cleavage with obvious fan-shaped
marking and branched propagation, which indicated that the cracking mode is hydrogen-induced
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cracking (HIC). Metallographic and SEM analysis showed strain-induced marten site transformed from
austenite during the cold working process. This resulted in a considerable susceptibility to sulfide stress
corrosion cracking (SSCC). The quantitative analysis results of XRD indicated that the content of
marten site was up to 44%. The location of HIC at the expansion joint located at crests with maximum
cold work deformation and hardness.”
M. Radhakrishna et al stated that “Previous work by Li et al. in the area of axial vibrations of bellows
dealt with fixd end conditions. However, it is seen on several occasions that bellow ends are welded to a
small pipe spool that has a lumped mass such as a valve or an instrument. Hence, the present paper aims
at finding out the effect of elastically restrained ends on the axial natural frequencies. The analysis
considers finite stiffness axial restraints on the bellows, i.e. solving the set of equations with non-
homogeneous boundary conditions. Two bellow specimens are considered for comparison having the
same dimensions as taken by Li in his analysis. The transcendental frequency equation deduced is
accurate as the first, second and third mode frequencies computed are in close agreement to the ones
obtained by Li.”
S.W.Lee , et al Stated that “The manufacturing process of the metal bellows consists of the four main
forming processes: deep drawing, ironing, tube-bulging and folding. The tube-bulging and folding
processes are critically important because the quality of the metal bellows is greatly influenced by the
forming conditions of these processes. Also, the final convolution shape of the bellows is determined
just after the spring back stage. There are many forming factors pertinent to the overall process of the
metal bellows. The representatives are the wall thickness of the pre-form tube, the pressure applied
during the tube-bulging and the die stroke for the folding stage. In this paper, a finite element analysis
technique is applied to the tube-bulging and folding processes as well as the spring back stage. The
explicit time integration method is used for analyzing the tube-bulging and folding processes.
Meanwhile, the implicit time integration method is used for the spring back stage. Combination of these
two different time integration methods is widely accepted for simulating the forming and spring back
stages consecutively. In addition to the FE simulation, effects of the representative forming factors
mentioned above are examined by using the Taguchi method. From the factor study, the most important
factor influencing the final shape of convolution of the metal bellows is found out. The results of the
present study could be used as a basis of designing a new type of the metal bellows.”
Lu Zhiming et al stated that “The in-plane instability of U-shaped bellows is analyzed. The in-plane
instability critical pressures of bellows which are subjected to zero, tensile and compressive deformation
are measured experimentally. The in-plane instability critical pressure of bellows under compressive
deformation is apparently lower than that under zero deformation, and the in-plane instability critical
pressure of bellows under tensile deformation is higher than that under zero deformation.”
C. BechtIV, et al stated that “Consideration of fatigue is generally an important aspect of the design of
metallic bellows expansion joints. These components are subject to displacement loading which
frequently results in cyclic strains well beyond the proportional limit for the material. At these high-
strain levels, plastic strain concentration occurs. Current design practice relies on use of empirical
fatigue curves based on bellows testing. Prediction of fatigue behavior based on the combination of
analysis and polished bar fatigue data is not considered to be reliable. One of the reasons for the
unreliability is plastic strain concentration. It is shown that the difference between bellows and polished
bar fatigue behavior, as well as the difference between reinforced and unreinforced bellows, can be
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largely attributed to this strain concentration. Further, it is shown that fatigue life of bellows can be
better predicted by partitioning the bellows fatigue data based on a geometry parameter. Determining
dynamic characteristics of bellows by manipulated beam finite elements of commercial software.”
G.I.Broman et al , stated that “A procedure for determining dynamic characteristics of bellows by
manipulating certain parameters of the beam finite elements of I-DEAS Master Series 6 is presented.
The method will work in any software in which these parameters can be set by the user. Compared to a
shell elements model the model size is reduced by at least a factor of 100. This is especially design
parameters. Stress in the bellows cannot be predicted by this method, but when the dynamic behaviour is
known it can be used as input for stress calculations, if desired. In contrast to existing “semi-analytical”
methods this method has the potential of considering axial, bending and torsion degrees of freedom
simultaneously, and it facilitates the interaction between the bellows and the rest of the system, also
modelled by beam or shell finite elements. The procedure is verified by experimental results from other
investigators.”
V. JAKUBAUSKAS et al stated that “This paper considers the transverse vibrations of fluid-filled
double-bellows expansion joints. The bellows are modelled as a Timoshenko beam, and the fluid added
mass includes rotary inertia and bellows convolution distortion effects. The natural frequencies are given
in terms of a Rayleigh quotient, and both lateral and rocking modes of the pipe connecting the bellows
units are considered. The theoretical predictions for the first six modes are compared with experiments
in still air and water and the agreement is found to be very good. The flow-induced vibrations of the
double bellows are then studied with the bellows downstream of a straight section of pipe and a 90°
elbow. Strouhal numbers are computed for each of the flow-excited mode resonances. The bellows
natural frequencies are not affected by the flowing fluid but the presence of an immediate upstream
elbow substantially reduces the flow velocity required to excite resonance.
Tianxiang Li investigates the stresses of Ω-shaped bellows with ideal and elliptic toroids imposed by
internal pressure or deflection, and analyzes the stress distribution state. The calculated stress results of
Ω-shaped bellows with elliptic toroid correspond with our experiment. This paper also analyzes the
effect of the toroid elliptic degree on the bellows stresses. It shows that the toroid elliptic degree needs
to be greatly reduced in the manufacturing process. On the pressure buckling of rectangular bellows for
fusion reactors
Isoharu Nishiguchi and Shinya stated that “Bellows are planned for use in the torus vacuum vessel of
ITER to absorb the relative displacements resulting from thermal expansion. Though both sides of the
bellows are in vacuum during normal conditions, these bellows would be subjected to external or
internal pressures of several MPa during accidents. Since the vacuum vessel forms the tritium boundary
during postulated accidents, the prevention of bellow failure in these events is very important in the
ITER design. For equipping the internal components, rectangular bellows are preferable to circular
bellows in the ITER design. However, investigations concerning pressure buckling of rectangular
bellows are few. Therefore, we investigated the buckling behavior of rectangular bellows and proposed a
simplified evaluation method based on the half pitch model for bellows with a relatively high length-to-
diameter ratio, where elastic column squirm is dominant. For bellows with a lower number of
convolutions, however, inplane squirm buckling should be considered, therefore, we have investigated
inplane squirm of rectangular bellows and compared it with that of circular bellows in this paper.”
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V. F. JAKUBAUSKAS and D. S. WEAVER, Department of Mechanical Engineering, McMaster
University, Hamilton, Ont., Canada, L8S 4L7, stated that “This paper presents the results of an analysis
of the fluid-added mass in bellows expansion joints during bending vibrations. The added mass is shown
to consist of two parts, one due to transverse rigid-body motion and the other due to distortion of the
convolutions during bending. The latter component, neglected in previous analyses, is shown to be
important for relatively short bellows, as are commonly used for expansion joints, and to become
increasingly important for higher vibration modes. The distortion component has been determined using
finite element analysis, and the results are presented in a graphical form for a typical range of bellows
geometries. The total added mass is given in a form suitable for hand calculations.”
II. SOFTWARE USED:
Autodesk® Inventor® 3D mechanical design software provides a comprehensive set of 3D mechanical
CAD tools for producing, validating, and documenting complete digital prototypes. The Inventor model
is a 3D digital prototype that helps users visualize, simulate, and analyze how a design will work under
real-world conditions before a product or part is ever built—helping manufacturers get to market faster
with fewer physical prototypes and more innovative products.
Experience the benefits of Digital Prototyping at your own pace with the most trusted resource for
leveraging and safeguarding your DWG™ data. Inventor software is not only the leader in bringing
innovative capabilities to the manufacturing market, but is also the best-selling 3D mechanical design
software, having outsold all competitors seven years running.
Features & Specifications
The Autodesk® Inventor® software line provides a comprehensive set of tools for producing,
validating, and documenting complete 3D digital prototypes. Learn how Autodesk Inventor software
helps designers create accurate 3D digital prototypes and bring better products to market faster and at
less cost.
Hyper Mesh:
Hyper Mesh is a high performance finite element method pre-processor for popular finite element
solvers that allows engineer to analyze product design performance in a highly interactive and visual
environment. Hyper Works is a user interface is easy to learn and supports number CAD geometry and
finite element model file formats, thereby increasing interoperability and efficiency.
Advanced functionally within the Hyper mesh allows users to efficiently manipulate geometry and
highly complex models. These functionalities include extensive meshing and model control, morphing
technology to update existing meshes to new design proposals and automatic mid-surface generation for
complex designs with varying wall thickness.
Solid geometry enhances tetra-meshing and hexa-meshing by reducing interactive modeling times, while
batch meshing enables large-scale meshing parts with no manual clean-up and minimal user input.
III. BENEFITS
1. Open-Architecture Design With the broadest set of direct CAD and CAE interfaces coupled with the users-defined integrations,
Hyper Works fits seamlessly with any simulation environment.
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2. High-Speed, High-Quality Meshing
With both automatic and semi-automatic shell, tetra-and hexa-meshing capabilities, Hyper Works
simplifies the modeling, process of complex geometries.
3. Closes the loop between CAD and FEA
Create surfaces from the finite elements enabling analysis engineers to communicate results and design
modifications back into the design environment.
4. Reduces Model Assembly Time
Leverage highly automated methods for rapid model assembly that create connections such as
bolts, spot welds, adhesives and seam welds.
IV. OUTPUT OBTAINED :
MODELLING OF EXPNSION JOINTS ALONG WITH THE CROSS OVER USING
INVENTOR
Figure 1 Metal Expansion Joints Along with Cross Over
Figure 2 Elbow Pressure Balanced Expansion Joints
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Figure 3 Elbow Pressure Balanced Expansion Joints
Figure 4 In Line Pressure Balanced Expansion Joint
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Figure 5 Side View
Figure 6 Mitter
Modeling is done by using the software INVENTOR. Modeling was completed using the student
licensed version of Autodesk Inventor Professional 2009.
V. ANALYSIS OF EXPANSION JOINTS
MESHING:
In this project analysis part is continued in two software’s. One is Hyper Mesh which is used
only for the MESHING purpose. Finally solving was proceeded in ANSYS.
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DATAS OF LP TURBINE A:
Table 1 DATAS OF LP TURBINE A
COMPONENTS PIPE TIE ROD SUPPORT RING BELLOW
MATERIAL USED A 516 Gr. 74 A 193 Gr. 2H A 516 Gr. 70 A 240 TYP 316
YIELD STRENGTH 264 MPA
YOUNGS MODULUS 25058000 PSI 25996000 PSI 25058000 PSI 24562000 PSI
THICKNESS 25 94 95
TOAL LOAD 298091.278 kgs
DATAS OF LP TURBINE B:
Table 2 DATAS OF LP TURBINE B
COMPONENTS PIPE TIE ROD
SUPPORT
RING BELLOWS
MATERIAL USED A 516 Gr. 74 A 193 Gr. 2H A 516 Gr. 70
A 240 TYP
316
YIELD STRENGTH 264 MPA
YOUNGS MODULUS 25058000 PSI 25996000 PSI 25058000 PSI 24562000 PSI
THICKNESS 16 72 80
TOAL LOAD 173320.55 kg
7.2 LOAD CONSTRAINTS:
Young’s Modulus E FOR PIPE = 25058000 PSI, CARBON STEEL – A 105, A516, A515
Young’s Modulus E FOR ROD = 25996000 PSI
Young’s Modulus E FOR BELLOW = 24562000 PSI
TENSILE MUST ACTS ON THE TIE ROD,
BENDING LOADS ON SUPPORT RING, NO GROOVES ON SUPPORT RING,
Total load acts on the 95 mm (LP Turbine A) thickness Support Ring = 298091.278 kg
Total load acts on the 80 mm(LP Turbine B) thickness
Support Ring = 173320.55 kg
Height of the bellow A = OD=1610 mm, ID= 1490 mm
Height of the bellow B = OD= 1217 mm, ID = 1097 mm
Thickness of bellow is 2 mm
Number of convolution is 6
Total Pressure applied in the entire model is 15 bars and it is maintained throughout the system.
Total pressure thrust load created by Bellow acts on the support ring that on support ring of LP TURBINE A and B
So, bending moment on the support thing and because of this load there is a formation of tensile
stress on the tie rods.
Pressure thrust load acts on the gusset or Shear Lug which is welded with the support ring.
Tie rod is connected with the support ring and because of load transfers to tie rod.
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7. 3. MESHING IN HYPER MESH
Figure 7 Meshing Done In Expansion Joint Using Hyper Mesh
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7.4. ANALYSIS IN ANSYS
7.4.1. LOAD CONSTRAINTS
Figure 8 load constraints in LP Turbine A
Figure 9 Constraints in LP Turbine B
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Fig 7.4.1.3 Pressure applied entirely in Cross over
Figure 10 Nodal solution in Y
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Figure 11 Nodal solution in Z
Figure 12 Stress formation
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Figure 13 Stress formation in Mitter
Figure 14 Stress formation Elbow Expansion Joint
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Figure 15 In Line Pressure Balanced Expansion joints
Figure 16 Stress formation in Support ring
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Figure 17 Stress in support ring area
Figure 18 Max Displacement of Tie Rod
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7.4.2. MODIFICATION BY CHANGING THICKNESS IN THE AFFECTING AREA
Figure 19 Nodal solution in X
Figure 20 Nodal solution in Y
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Figure 21 Nodal solution in Z
Figure 22 Stress Formation
Figure 23 Stress Formation
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Figure 24 Max Displacement
Figure 25 Stress Formation in Mitter
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Figure 26 Stress Formation on Elbow area
Figure 27 Stress Formation on In Line area
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Figure 28 Stress Formation on Support Area
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Figure 29 Stress and maximum displacement of Support Ring and Rod
VI. RESULTS
Given design is modeled and analyzed by using Hyper Mesh 9 and
Ansys 10
Max yield strength for the material in PIPE is 264 MPA
For the first result it came as 214 as maximum
Here stress concentrated areas are Elbow Joint, In Line Joint and Mitter
For the Safety factor the thickness of that area it is increased to 25 mm
Once again analyzed and solved it came below 140 MPA.
Allowable Stress is 157 MPA and considering factor safety 10% and allowable stress is (157-15.7 = 142.3 MPA), so allowable stress is above.
Stress diagrams are attached above which came as output in Ansys 10
Support Ring is very much safe in this pressure
Displacement of tie rod is calculated
VII. SUGGESTIONS
Support ring and gusset thickness can be reduced up to 10 mm
Mitter thickness can be reduced to 5 mm
So, it will reduce the self weight of the Cross over
Cost of material can be minimized
Thickness of the stress concentrated areas can be raised up to 2 to 4 mm considering the safety
factor.
REFERENCES I. Failure of 304 stainless bellows expansion jointKaishu Guana, Xinghua Zhangb, Xuedong Guc, Longzhan Caic, Hong
Xua and Zhiwen Wanga. from Science Direct Experimental and Finite Element Analysis of Metal Bellows
Manufacturing
III. G. Faraji, H. Kashanizadeh, M. Mosavi, and M.K. Besharati The effect of environmental medium on fatigue life for u-
shaped bellows expansion joints
IV. Y.Z. Zhu, H.F. Wang and Z.F. Sang. From Science Direct. Active Damper using Fuzzy Controller, Rafael Luís
Teixeira Federal University of Uberlândia College of Mechanical Engineering Campus Santa Mônica - Uberlândia-
MG- Brazil. From IEEE
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V. METAL EXPANSION JOINT INSTALLATION AND HANDLING INSTRUCTIONS, by Expansion Joint Systems,
Inc
VI. Bellows Design for the PEP-II High Energy Arc Chambers, M.E.Nordby, N.Kuirta
VII. g. Strain and Fatigue Testing Of Large Expansion Bellows, by D.K.Sharma, R. Henschel and M.Krawchuk
VIII. Expansion joint covers,Expansion joint covers, portal plus 639, Thomas drive, Bensenville, IL60106
IX. Expansion Joint covers, published by felt tips, Contributed by Scott Sider, ccs ,april 1995
X. INFLUENCE OF MICRO-DAMAGE ON RELIABILITY OF CRYOGENIC BELLOWS IN THE LHC
INTERCONNCTIONS, C. Garion1, B. Skoczen*
XI. Expansion joint designs for inquiries and fabrication. Compensator design reviews. KOG Fabricators, 2006
XII. Design of various high temperature expansion joints and special items, 3D modeling and manufacturing drawings, J
Tolonen Services cc, KOG Fabricators
XIII. Complex expansion joint designs for inquiries and fabrication. Arminco, 2002
XIV. Expansion joints bellows and stress analysis, by engineering applicances.
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