Technical Guide to Coil Spring Manufacturing

Coil Spring Manufacturing Process

Whether you have an exist­ing spring application in need of re-engineering or a new one that requires designing this guide will help. The engineering team and MW Components has been manufacturing springs for well over 100 years and has refined the coil spring manufacturing process for the industry – for all types of coil springs.

The scope of this manual is limited to data which will be helpful to the design engineer in solving problems frequently encountered in helical springs. General information such as maxi­mum stress limits, relative costs of materials, and the more often used formulas are presented for references.

For the sophisticated engineer desiring more technical design information we highly recommend Dr. A.M. Wahl’s “Mechani­cal Springs” published by the McGraw-Hill Company.

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Coil Spring Tolerances

COLD WOUND SPRINGS MANUFACTURING

The Spring Manufacturers Institute composed of over 300 major cold wound spring manufacturers has produced a handbook for “Standards and Design for Com­pression, Extension, Torsion, and Flat Springs.” This manual, available from your spring manu­facturer, is highly recommended as a guide to practical tolerances and for its coverage of spring terminology, formulas and design infor­mation for cold-formed springs.

HOT WOUND SPRINGS MANUFACTURING

The accepted standard for manufacture and tolerances of how wound springs is ASTM-125, latest revision. This speci­fication covers such points as tolerance on out­ side diameter, free height, maximum solid height, loaded height, and squareness, as well as definitions and inspection procedure.

The ASTM committee, composed of tech­nical representatives of the major hot coil spring manufacturers, has cognizance over the updating of the specification to keep pace with technological advances.

Coil Spring Stress Correction

The conventional stress formulas for com­pression and extension springs shown in this guide give values in pure torsion. Most springs are used for light or moderate service where the life requirement will not exceed 10,000 cycles. It is generally accepted practice to ig­nore correction factors for such service.

For heavy duty service where life expect­ancy is 100,000 cycles or greater, total stress must be considered. The Wahl correction factor takes into account increased stresses caused by the curvature of the wire and shear. A corrected stress is obtained by multiplying the conven­tional stress by the appropriate Wahl factor.

In most elevated temperature tests where relaxation data are given for various tempera­tures and stresses, the stress figures include the Wahl correction factor.

Another stress correction factor, shown by H.C. Keysor, covers the increase in stress due to eccentric loading, being most pronounced in short springs. With only 2 active coils, this correction factor is 1.23, but with 4½ active coils, the factor drops to less than 1.10.

Formulas (COMPRESSION AND EXTENSION SPRINGS)

  • Formulas for compression and extension springs
  • Formulas for compression and extension springs
  • Key

    W = compression rate, lbs/in.

    S = uncorrected torsional stress, PSI

    G = torsional modulus (see tables I, II, and III)

    d = wire diameter or square size, in.

  • Key

    D = mean coil diameter, in.

    P = load, pounds

    N = number of active turns

    b = long side of rectangular wire, in.

    t = short side of rectangular wire, in.

    K1 and K2 = constants (see above)

Formulas (TORSION SPRINGS)

  • Key

    M = moment of torque, inch pounds

    M/T = torque rate, or moment of cause 360° angular deflection, inch pounds per 360° deflection

    b = width or axial dimension

    S ₜ = tension stress, PSI

    E = modulus in tension = 28,500 for hot wound carbon or low alloy steel springs or 30,500,000 for cold wound carbon or low alloy steel springs

    t = thickness of radial dimension

  • Square Wire Info.

    Square Wire: Coiling distortion creates a trapezoidal shape, increasing the size along the inside diameter, and hence the solid height. The increased side dl can be estimated:

    where d= side of square before coiling; C = D/d

Surface Protection

Rust and environmental pitting act as stress risers and may cause early failure in the best designed spring, carefully manufactured from otherwise sound material.

Where cost and other factors dictate against corrosion resistant materials, the spring surface, which is the most highly stressed area, must be protected. Unprotected shot peened steel springs start rust­ing almost immediately. Protection starts with choosing the right coating.

Powder Coating, often the coating of choice, offers impact, abrasion, salt spray, humidity, and chemical resistance that meets the majority of customer requirements.

Epoxy powder coatings are designed for gen­eral purpose interior use and for applications where maximum chemical and solvent resis­tance is required.

TGIC-Polyester powder coat­ings are substituted for those applications re­quiring PVC coating. They offer excellent exte­rior durability and good resistance to most chemicals and solvents except alkalis and ke­tones.

At DC Coil, we have our own in-house powder coating ca­pabilities, making TCIC-Polyester coating our preferred choice. It offers a lower cost and quicker turnaround times than other coatings.

Electroplating with zinc with .0002″ to .0006″ thickness is one of the more practical methods of coil protection.

Mechanical cleaning by blasting im­mediately prior to plating facilitates electroplat­ing without lengthy acid pickling (which must be avoided).

Controlled stress relieving after plating reduces the effect of hydrogen embrittlement, a constant danger, particularly to oil tempered wire.

Electroplating cold wound springs made from oil tempered chrome vana dium or chrome silicon wire is not advisable. Electroless nickel plating is an effective substitute when cadmium is environmentally objectionable.

Dip painting to assure complete coverage with lacquer or enamel is another practical method, particularly for large springs. Water-based paints are now available for all colors in both lacquer and enamel.

Baking can be used for faster drying time and better adhesion when using water-based paints. This process usually involves individual handling. For this reason, springs small enough for barrel plating can be protected in this manner at a lower cost.

Oxide or phosphate coatings with supple­mental oil or paint coatings are useful treat­ments, particularly for oil tempered chrome vanadium or chrome silicon wire springs. For limited protection against rusting on the shelf in inside storage, protective oils may be used.

The use of pre-coated wire, such as cadmium plated or galvanized wire, is practical for lim­ited protection in small sizes for extension springs and compression springs with unground ends.

Hot dip galvanizing for finished springs is not normally practical. It has been successful only where large volume justifies the cost of very closely controlled processing.

Plastic coatings, such as polyvinyl chloride and nylon can be applied at a reasonable cost by the fluidized bed process for particularly cor­rosive applications.

Buckling

Where the free length of a compression spring exceeds four times the mean diameter, lateral deflection or buckling becomes notice­ able during compression.

Piloting and guiding on the O.D. or I.D. helps correct this problem, although friction against a supporting member may be objectionable due to possible scoring and affected load reading.

For springs with squared and ground ends, one end on a plate and the other on a ball, ob­jectionable buckling will occur when the coor­dinates are to the right of line 1.

Objectionable buckling will occur to the right of line 2 when springs with squared and ground ends are compressed between parallel plates, as on a spring testing machine.

When possible the spring should be de­signed so the end of the coils (tip ends) are 180° apart. This is accomplished by having the num­ber of coils active and inactive always end on the half coil (i.e., 4.5 active and 6.5 total).

This allows for even distribution of the spring ma­terial preventing the spring from buckling sooner than shown on the graph above. This condition also helps prevent the spring from going out of square under load.

Natural Frequency

The natural frequency of springs should be considered where heavy duty service and rapid cycling are involved. If the natural frequency of the spring is too low, surge and coil clashing with augmented stresses will result.

It is best to design the spring with a natural frequency of at least 13 times the vibrating speed (cycles per minute). Samples for high-speed applications should be thoroughly tested to avoid prema­ture failures in the field.

The formula for calculating natural fre­quency of a spring is:

Key:

n = cycles per minute of spring vibrating between its own ends

d = wire diameter, in.

D = mean coil diameter, in.

N = number of active coils

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