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For any manufactured equipment, the geometry of the padeye must match the size of shackle to be used to ensure a rated connection between the equipment and the lifting set.

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DNV states two key sizing rules which are of importance:

The diameter of the holes in the padeye shall match the shackle used, clearance between shackle pin and padeye hole shall not exceed 6% of the shackle pin diameter.
The thickness of the padeye at the hole shall not be less than 75% of the inside width of the joining shackle

The correct design of padeye should be selected based on the particular load application. For straight lifting angles a symmetric padeye design should be used, for a multi-point lift as in a offshore container or frame then a nonsymmetric design can be used. If required plated supports can be added to the symmetric design to increase the lateral stiffness of the padeye, useful when the padeye will be subjected to dynamic load angles.

For a multi-point lift it is essential that the padeyes point directly to the lift point centre to prevent lateral bending moments on the padeyes, DNV suggest a tolerances of 2.5 degrees as an allowable misalignment.

For padeyes rated above 2000kg capacity cheek plates must be fitted to reduce the play in the shackle-padeye connection. These must be fitted as additional plates welded onto the padeye profile and not a single boss as shown below.

Padeye Materials

For equipment used in a marine environment, all padeye materials are to be S335J2 (BS EN 10025) supplied with 3.1 material inspection certificates to BS EN 10204.

Padeye Welding

All padeyes must be welded to the primary struture by use of full penetration welds. It is good practure to extend the base of the padeye to pass it completely through the structural member which it is connected to. If welding directly onto horizontal plate then the plate must be specified as EMZ grade to prevent delamination of the plate under tensile load.

When sizing the correct padeye for your application consider the following:

Maximum foreseen gross load
Load test requirements
Dynamic amplification factor (DAF)
Drag load on equipment when lifting through water
Potential captured water weight when lifting equipment out of water

This document has been created as a guide and should not be used as a substitute to correct design calculations. All lifting frames including padeye design should be checked by calculation and ideally independently checked and approved prior to manufacturing. Post manufacture load testing must be performed prior to equipment use.

For a complete dimensional overview of standard padeye designs please click below:

Padeye Design Guide 709.37 KB

A padeye (Fig 1; sometimes referred to as 'padear') is a term used to describe a specialised lug for attaching lifting or restraint shackles.

PadEyes uses the compatibility of a well-known shackle design⁽¹⁾ to dimension a suitable mating padeye.

Applications

Lifting

The applied load (F) for lifting appliances can be determined by any suitable calculation facility including CalQlata's lift rigging calculator. It is important, however, that appropriate factors (DAF, SF) are applied to any design load especially if the padeye is to be used repeatedly in ill-defined conditions.

Safety factors for lifting padeyes are normally slightly higher than those applied to restraint applications, such as seafastenings.

Seafastening

Padeyes may also be used for fastening equipment to a ship's deck, in such cases it is necessary to apply suitable factors for vessel motions (accelerations) in heavy seas (see CalQlata's vessel motions calculator).

Skewed Loading

A skewed load is a load applied out-of-plane with the padeye. Whilst it is not good practice to apply skewed loads to a padeye, if the skew is kept to an acceptable angle (<5°) and the applied load is significantly reduced (<50% SWL) to minimise localised bearing stress in the padeye and bending stress in the pin, it can be considered acceptable for non-critical applications. However, the resultant bending stress in the shackle and padeye should be considered in your calculations. In such circumstances, suitable (larger and tapered) clearances in the pin hole (C) and over the cheek plates (Cᴾ) should be considered.

Materials

In both the above applications, it is important to ensure that suitable materials are used for the manufacture of padeyes, such as certified carbon steel of a recognised grade and quality.

As it is essential that the welding used to anchor padeyes is also reliable, it should be carried out using coded welders and certified materials (welding rods) and recognised procedures.

Design Stresses

Fig 2. Padeye Design Stresses

Fig 2 shows the limiting stresses to be considered when designing a padeye.

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Bearing stress is distributed across the main plate and the cheek plates. A high bearing stress will dissipate as the material locally deforms to generate a 'land' (or flat) increasing the contact area and decreasing the stress. When the stress has reduced to yield stress the localised deformation will be elastic and the contact area will not increase further.

Tensile stress is exerted on both sides of the eye and only through the main plate. The cheek plates are not included in this calculation. Tensile stress is always considerably less than the bending or shear stresses in the eye. The force from this stress generates the shear forces in the mounting weld.

Bending stress is analogous to a bar laid across the pin and centrally loaded, however, no part of the bar is in compression so its neutral axis is no longer through the centre of the cross-section. The cheek plates are not included in this calculation. As the width of the padeye section (Fig 2) is increased, the bending stress becomes the dominant component in the combined stress in this plane.

Shear stress is theoretically constant through this plane. The cheek plates are not included in this calculation. As the thickness of the padeye plate (Fig 2) is decreased, the shear stress becomes the dominant component in the combined stress in this plane.

Combined stress is the principal stress through the plane of bending and shear. This is always the weakest plane in a properly designed padeye and is therefore used as the defining stress in the design.

Maximum allowable stress is the maximum permitted stress at the design load. This is normally 40% of SMYS plate material for design loads less than 25t; 50% for loads less than 100t and 67% for loads greater than 100t, but should be according to the design code prevalent for any given project.

Welding

The weld length considered in PadEyes' calculations is conservatively limited to twice the indicated length ('2R') shown in Fig 2, i.e. half the total weld length each side of the main padeye plate, irrespective of the loaded angle (see Weld Length below).

As high quality welding is essential for reasons of security and/or safety, all welding on padeyes should be carried out by coded welders using approved procedures and certified materials (welding rods). Moreover, no stitch welding should be permitted in the active area of the weld length (Fig 2; '2R'). For this reason, a weld joint factor of 0.9 to 1.0 is reasonable for padeyes.

Weld Length

The force (F) applied to a padeye is transferred to its mounting weld by induced strain in its main plate. The shortest distance from the source of the strain to the weld, in the same direction, will constitute the greatest strain and thus induce th

Program To Design A Pad Eye Type Lifting Lug V.02