A portion of a 19 mm (0.75 in.) diam structural steel bolt was found on the floor of a manufacturing shop. This shop contained an overhead crane system that ran on rails supported by girders and columns. Inspection of the crane system revealed that the bolt had come from a joint in the supporting girders and could be considered one of the principal fasteners in the track system. Analysis (visual inspection, metallographic exam, and hardness testing) supported the conclusions that fatigue induced by the overhead movement of the crane produced failure of the bolt. The bolt was deficient in strength for the cyclic applied loads in this case and probably was not tightened sufficiently. Recommendations included removing the remaining bolts in the crane support assembly and replacing them with a higher-strength, more fatigue-resistant bolt, for example, SAE grade F, 104 to 108 HRB. The bolts should be tightened according to the specifications of the manufacturer, and the system should be periodically inspected for correct tightness.

Drive cables from a rubber processing machine were failing in less than 8 h of operation, the expected service life being much greater than 100 h. Comparison cables were tested to failure under known stress conditions, including tensile overload, torsional loading, reversed bending alternating stress, and buckling (compressive) cyclic loading. The mode of failure was found to be reversed bending fatigue caused by drive cables moving over guide pulleys of small radii. Modifications of the machinery and drive cable system were suggested.

A 13 mm diam 18 x 7 fiber-core improved plow steel nonrotating wire rope, brought into service as a replacement for 6 x 37 improved plow steel ropes, failed after 14 months of service on a stacker crane. The change was reported to have been caused by difficulties twisting of the 6 x 37 rope. The hoist arrangement for this crane was found to consist of one rope with each end attached to a separate drum and the rope was wound around two 30-cm diam sheaves in the block and back up around an equalizer sheave. The rope section that had been in contact with the sheaves was deduced by measurement checks. The presence of broken wire ends, which indicated that the rope failed by fatigue, was revealed by reverse bending of the section of the rope which was normally subjected to this flexing. It was found that minimum sheave diam for a 13-mm 18 x 7 wire rope was 43 cm and hence the currently used smaller sheaves caused excessive bending stresses in the rope. The 18 x 7 rope was replaced by two 6 x 37 side-by-side counter-stranded steel-core ropes as a corrective measure.

A 60.3 mm (2.375 in.) diam drive shaft in the drive train of an overhead crane failed. The part submitted for examination was a principal drive shaft that fractured near a 90 deg fillet where the shaft had been machined down to 34.9 mm (1.375 in.) to serve as a wheel hub. A 9.5 mm (0.375 in.) wide x 3.2 mm (0.125 in.) deep keyway was machined into the entire length of the hub, ending approximately 1.6 mm (0.062 in.) away from the 90 deg fillet. A second shaft was also found to have cracked at a change in diameter, where it was machined down to serve as the motor drive hub. Investigation (visual inspection, inspection records review, optical and scanning electron microscopy, and fractography) supported the conclusion that the fracture mode for both shafts was low-cycle rotating-bending fatigue initiating and propagating by combined torsional and reverse bending stresses. Recommendations included replacing all drive shafts with new designs that eliminated the sharp 90 deg chamfers in favor of a more liberal chamfer, which would reduce the stress concentration in these areas.

Each of the ten studs on one wheel of a semitrailer used to haul coal broke in half while the trailer was in operation. Both halves of each of three studs were sent to the laboratory to determine the cause of failure. Visual examination of the fracture surfaces of the studs disclosed beach marks, indicative of fatigue cracking, starting at opposite sides of each stud, with final fracture occurring across the stud. Each failure occurred in the first thread of the stud. It was concluded that the wheel studs fractured by reversed-bending fatigue. To minimize the possibility of a recurrence, the wheel nuts were tightened with an air impact wrench to a torque of 610 to 678 J (450 to 500 ft · lb) dry. All wheel studs were checked at normal maintenance periods to ensure uniform and proper loading, and no further failures occurred.

The fan drive support shaft, specified to be made of cold-drawn 1040 to 1045 steel, fractured after 2240 miles of service. It was revealed by visual examination of the shaft that the fracture had initiated near the fillet at an abrupt change in shaft diameter. The cracks originated at two locations approximately 180 deg apart on the outer surface of the shaft and propagated toward the center. Features typical of reversed-bending fatigue were exhibited by the fracture. A tensile specimen was machined from the center of the shaft and it indicated much lower yield strength (369 MPa) than specified. It was disclosed by metallographic examination that the microstructure was predominantly equiaxed ferrite and pearlite which indicated that the material was in either the hot-worked or normalized condition. An improvement of fatigue strength of the shaft by the development of a quenched-and-tempered microstructure was recommended.

Six galvanized high-tensile steel bolts were used to hold the wheels of a four-wheel drive vehicle. The right hand rear wheel of this vehicle detached causing the vehicle to roll and resulting in considerable damage to the body. The wheel was detached by shearing of four of the bolts and stripping the nuts from the other two bolts, which remained unbroken. SEM fractography of the fracture surfaces of the four broken bolts indicated that the failure was due to reversed bending fatigue. Optical microscopy indicated that the bolts were heat treated to a tempered martensite structure and that the nuts were manufactured from low carbon steel. The paper discusses the influence of the microstructure on the failure process the events surrounding the nature of incident and the analysis of in-service failure of the failed components utilizing conventional metallurgical techniques.

An LNG tanker experienced a fracture of the solid tail shaft, which is a section of the main drive shaft. The tail shaft was made of a forged low-carbon steel. In spite of two ultrasonic inspections, a large defect the size of a football in the center of the shaft was missed. During heat treating following forging, it was surmised that the defect led to the propagation of an internal brittle crack, or clink. A fatigue crack propagated from this origin to the outer surface of the shaft after about a year of service. Finally a last ligament of a few square inches held the shaft together and broke, leading to the separation of the shaft. The cause of failure was fatigue crack initiation and crack growth under reverse bending cyclic stresses. There was no indication that misalignment existed because there was no indication of fretting at the bolt holes in the flange at the end of the shaft. In the case of this shaft, a solution would have been to machine the core of the shaft to remove the brittle material or to use a tubular shaft.

A 20 ton polar crane motor fell during a 3400 kg (7500 lb) lift, narrowly missing personnel working beneath the crane. Witnesses reported that the motor fall was preceded by a falling oil mass, and it was believed that the motor was intact prior to impact. The maintenance history of the crane showed that the motor had been removed, repaired, and reinstalled 2 years prior to the failure. Observations of oil leakage were noted yearly up to the failure. The motor casing was held onto the adapter plate by eight 14-20 UNC x 25 mm (1 in.) long hex socket cap screws. Examination of the motor adapter plate, motor casing shards (aluminum), the gear side of the motor housing, and seven fractured cap screws (ASTM A574) showed that the motor casing was intact at the time of “uncontrolled descent” and that the screws had failed by high nominal stress reverse bending load fatigue, which was probably the result of insufficient torque on the bolts.

Failure occurred in a type 304 stainless steel leaf spring attached to the undercarriage assembly of an airport shuttle train. Failure analysis showed that the fracture was caused by low-cycle, reversed bending fatigue. The stresses leading to failure were imposed by poor alignment. It was recommended that improved assembly procedures be used and that, if another failure occurred, a steel of higher fatigue strength be used.