Transient Load Analysis and stress analysis of Six Cylinder Crankshaft

In this study, adhesive T-joint with crack in urea granulator fluidization bed was analyzed by finite element (FE) analysis. Objectives of this project were to examine a series of adhesively bonded T- joints with crack under mode I loading, to evaluate stress analysis of adhesive T-joint with crack at top and bottom and to identify the effective bond thickness. The path was drawn in ANSYS at the top and bottom of adhesive from side view to find which part has higher stress. The result of both paths top and bottom analysis shows the stress distribution always higher at both edges. So, the crack was inserted at interface edges and the stress distribution was evaluated. From interface edges stress distribution result of top and bottom, it shows that bottom edge has higher stress compare with top edge. The failure load analysis will compare with other analysis and experiment result. It is found that adhesive T-joint with 1.5mm is the best thickness for granulator fluidization bed application because always has higher failure load.

Download Full-text

Pipe Stress and Turbine Nozzle Load Analysis for HP Steam Inlet and MP Steam Extraction on Turbine Generator 51G201T Capacity 10MW

International Journal of Engineering & Technology ◽

10.14419/ijet.v7i4.33.23562 ◽

2018 ◽

Vol 7 (4.33) ◽

pp. 214

Author(s):

Udin Komarudin ◽

Iftika Philo, Nia Nuraeni ◽

Nissa Syifa Puspani

Keyword(s):

Stress Analysis ◽

Stress Ratio ◽

Turbine Generator ◽

Maximum Displacement ◽

Maximum Hoop Stress ◽

Field Information ◽

Turbine Casing ◽

Allowable Load ◽

Load Analysis ◽

Perspective Calculation

Thermal pipe expansion on the turbine greatly affects the performance of the turbine, mainly produces misalignment in turbines. The stress analysis on the pipe and the load on the nozzle is very important to ensure that the stress that occurs is still safe and the load that occurs on the nozzle is still below the allowable load. Field information is known, Steam type of 51-G-201-T, capacity 10 MW, total weighs 58 tons, weight casing 37 tons, which has been operating since July 1989, has been occur misalignment on turbines. Stress pipe and load analysis of turbine nozzles on the turbine using software (Autopipe V8i Select Series 3 Edition by Bentley). In this perspective, calculation methodologies were developed in order to do quick analysis of the most common configurations, according to the codes ASME B31.1 (Piping Power). The results of the pipe stress analysis showed that the maximum sustained stress ratio occurred at point A39 (0.32), maximum displacement stress ratio at point A39 (0.97) and maximum hoop stress ratio at point A09 (0.44), all values below 1. This shows that the stress is still safe. The result of load analysis on the turbine casing is the direction x = -880 kg, y = 6246.4kg, z = -3697.7kg, smaller than the weight of the 37 tones turbine casing, so misalignment is not caused by shifting the turbine casing.

Download Full-text

Load Analysis and Critical Area Stress Analysis of the 126-AR00036 and 126-AR00037 Parachute Testers when Installed on the F-4C/D Aircraft Centerline Station

10.21236/adb022406 ◽

1976 ◽

Author(s):

Jr Dyess ◽

William W.

Keyword(s):

Stress Analysis ◽

Critical Area ◽

Load Analysis

Download Full-text

A Comparison Study of Pressure Vessel Design Using Different Standards

Volume 1: Offshore Technology ◽

10.1115/omae2013-10684 ◽

2013 ◽

Author(s):

Frode Tjelta Askestrand ◽

Ove Tobias Gudmestad

Keyword(s):

Stress Analysis ◽

Elastic Stress ◽

Limit Load ◽

Technical Committee ◽

Pressure Vessels ◽

Analysis Method ◽

Elastic Plastic ◽

Load Analysis ◽

American Society ◽

Division 2

Several codes are currently available for design and analysis of pressure vessels. Two of the main contributors are the American Society of Mechanical Engineers providing the ASME VIII code, Ref /4/ and the Technical Committee for standardization in Brussels providing the European Standard, Ref /2/. Methods written in bold letters will be considered in the discussion presented in this paper. The ASME VIII code, Ref /4/, contains three divisions covering different pressure ranges: Division 1: up to 200 bar (3000 psi) Division 2: in general Division 3: for pressure above 690 bar (10000 psi) In this paper the ASME division 2, Part 5, “design by analysis” will be considered. This part is also referred to in the DNV-OS-F101, Ref /3/, for offshore pressure containing components. Here different analysis methods are described, such as: Elastic Stress Analysis Limit Load Analysis Elastic Plastic Analysis The Elastic Stress Analysis method with stress categorization has been introduced to the industry for many years and has been widely used in design of pressure vessels. However, in the latest issue (2007/2010) of ASME VIII div. 2, this method is not recommended for heavy wall constructions as it might generate non-conservative analysis results. Heavy wall constructions are defined by: (R/t ≤ 4) with dimensions as illustrated in Figure 1. In the case of heavy wall constructions the Limit Load Analysis or the Elastic-plastic method shall be used. In this paper focus will be on the Elastic-plastic method while the Limit Load Analysis will not be considered. Experience from recent projects at IKM Ocean Design indicates that the industry has not been fully aware of the new analysis philosophy mentioned in the 2007 issue of ASME VIII div.2. The Elastic Stress Analysis method is still (2012) being used for heavy wall constructions. The NS-EN 13445-3; 2009, Ref /2/, provides two different methodologies for design by analysis: Direct Route Method based on stress categories. The method based on stress categories is similar to the Elastic Stress Analysis method from ASME VIII div. 2 and it will therefore not be considered in this paper.

Download Full-text