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ASME-BTH June 5, | Author: Nanang Komarudin | Category: Strength Of Materials, Engineering, Mechanical Engineering, Science, Nature. Buy ASME BTH 1: DESIGN OF BELOW-THE-HOOK LIFTING DEVICES from SAI Global. ASME BTH Design Of Below-The-Hook Lifting Devices. Be notified when this Standard is updated or amended – Add to StandardsWatch. General.

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Fatigue Stress Amplification Factors. FSR shall be the smaller of the toe crack or root crack allowable stress range.

However, fatigue design must recognize stress ranges.

Thus, the prior design method, which is generally recognized as acceptable for lifters now classified as Design Category A, provided design factors with respect to the rated load of 1. They are intended to be used with cranes, hoists, and other bth-1-201 equipment. If larger holes are necessary, the capacity of the connection shall be reduced accordingly. At these temperatures, the mechanical properties of most materials are greatly reduced over bth-1-22014 at ambient. The static and shear stress equations represent modifications to those equations found in CMAA N is the expected number of constant amplitude stress range cycles and is to be provided by the owner.

It is the responsibility of a qualified person to determine when higher design factors are required and to determine the appropriate values in such cases. Members with drilled or reamed holes aske bolts for attachment of light bracing where there is a small longitudinal component of brace force.

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Since fatiguerelated bt-1-2014 initiate at points of stress concentration due to either geometric or metallurgical discontinuities, peak stresses created by these discontinuities may need to be considered in the design of a lifter. Any loss bhh-1-2014 strength in the fastener bty-1-2014 by the locking method shall be accounted for in the design. Verenski, Hunter Lift Ltd.

This Design Category should not be used in any environment where severe conditions or use are present. Some manufacturers of heavy equipment such as power generation machinery build lifters to be used for the handling of their equipment.

The fatigue design requirements in section are generally based on the provisions of AWS D The pitch diameter of a sheave has a direct relationship with wire rope wear and fatigue that determines the number of cycles that the assembly can withstand. AISC defines the same loading conditions, joint categories, and stress C Along with the forces produced by normal operation, mechanical components of lifting devices should be designed to ase the forces resulting from operating irregularities that are common in mechanical systems including jams, locked rotor torque, and overloads.

Consideration should be given to conditions such as surface temperatures, contamination, torsion, and bending loads of the vacuum pad, tested vacuum pad performance, and surface conditions of interfacing materials. Stress range is the algebraic difference between the maximum stress and the minimum stress.

ASME-BTH – Free Download PDF

For fillet welds in holes or slots, the effective length shall be the length of the centerline of the weld along the plane through the center of the weld throat.

Examples include, but are not limited to, drive systems on slab tongs that hold bth-1-20114 load, fasteners that hold hooks onto beams, and sheave shafts.

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Consistent units or unit conversions shall be used. Load Cycles nth-1-2014 1 2 3 4 0—20, 20,—, ,—, ,—2, Over 2, The Committee welcomes proposals for revisions to this Standard.

Below-the-hook lifters are not stand-alone machines. Again, the total load spectrum was developed and the statistical analysis performed.

ASME-BTH-1-2014-1

The coefficient CLTB in eqs. Fabricators that utilize personnel and procedures that are qualified under earlier editions of AWS D Thus, the theoretical maximum bending stress is 1. As with straight beam bending theory, the derivation of the equations by which the bending stresses of a curved beam may be computed are based on the fundamental assumption that plane sections remain plane Young and Budynas, The intent of this section is simply to call attention to the need for consideration of deflection in the design of lifting devices.

For example, a clamping device will not be able to maintain its grip if the members of the device flex excessively under load.

It is the responsibility of a qualified person to determine when a higher value is required and the appropriate value in such asmd.

It is not practical to define bt-1-2014 general acceptable slip resistance for such connections. The distribution of lifted loads relative to rated load is considered to be as shown in Table C