Design information for engineers, such as spring calculation formulas,

which are the basis of spring design, can be found here.

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- Compression Springs: Things To Note In Spring Design

Springs

This section describes the design of a compression spring with a regular cylindrical shape and equal pitch.

Fig 2. (a) to (g) shows the end shape of the compression spring. The closed end is often used for general use. To improve the washer of the spring, a material whose end surface is ground or tapered is used. Tapered materials are often used in mass-produced products, and tangent tails and pigtails are often used for automobile suspension springs.

Fig. 2 Shape of the end of compression spring

If the coil center line is oriented vertically, and the direction perpendicular to it is horizontal, the spring constant in vertical direction is defined by the expression (1). In this case, the spring constant in horizontal direction is called lateral stiffness, and can be obtained using the expression (2).

Spring constant in vertical direction

Spring constant in horizontal direction

ky=expression (1)=P/δs

kx：lateral stiffness

hs：spring height at vertical load P=h0-δs

C : a coefficient determined by aspect ration and (vertical deflection / free height)

As seen from the expression (1), if the spring shape is known, the ky value can be determined unambiguously. On the other hand, it is necessary to remember that the lateral stiffness depends on vertical deflection of the spring.

In any case, if kx and ky are required, they may be calculated by dividing the spring deflection caused by an oblique load in arbitrary direction into vertical and horizontal components.

Fig.4

Compression spring can also act on moments.

This property is used in suspension springs of passenger cars, where springs are incorporated in link mechanisms as shown on the fig.5. Here a moment is applied to the spring besides vertical and horizontal loads. Fig.6 shows the state where a compression spring is compressed to the height h by support plates tilted by angles φ1 and φ2.

The vertical P and horizontal Q components of reaction force of supports can be obtained using expressions (3) , (4) and the q is (5).

And the moment is M1(6) and M2(7)

P＝expression (3)

Q＝expression (4)

q＝expression (5)

The moment M1＝ expression (6)

The moment M2＝ expression (7)

When a sinusoidal forced oscillation is applied to a spring, the surge waveforms a stationary wave.

When the relationship between the frequency f of the external force and the natural frequency f1

of the spring satisfies the equation (a), a resonance phenomenon called surging occurs.

(a)

Here the first natural frequency f1 is determined by the following equation.

Here the first natural frequency f1 is determined by the following equation.

(b)

In practice, sinusoidal forced oscillations occur rarely. Generally, the forced displacement y is given as a function of time.

When the rotational speed ω of camshaft is constant like in valve springs of modern engines, the valve lift curve y(t) is represented by the Fourier series as shown below.

When the rotational speed ω of camshaft is constant like in valve springs of modern engines, the valve lift curve y(t) is represented by the Fourier series as shown below.

(c)

When the spring is in the primary resonance state with nth-order wave cosign (nωt + φn), the maximum fluctuating stress τs generated in the spring is the same stress τs (t) that occurs when the spring is statically compressed to y(t) only. This stress is given by the following equation.

When the spring is in the primary resonance state with nth-order wave cosign (nωt + φn), the maximum fluctuating stress τs generated in the spring is the same stress τs (t) that occurs when the spring is statically compressed to y(t) only. This stress is given by the following equation.

(d)

Here b is damping coefficient. It depends on complex factors and can not be determined unconditionally, but generally a value of (b) to (d) is used.

Fig.7. Stress variation due to surging

Fig.7 shows the stress diagram of a valve spring when the surging occurs. τ1 on the figure is the stress caused by initial compression applied to the spring at the closed vale position. The minimum τmin and the maximum τ2 stress values at this time can be calculated by equations (e) and (f) correspondently.

(e)(f)

The stress variation range τr is given by the equation (g).

(g)

An example of the resonance curve obtained by oscillation test of valve spring is shown on Fig.8. This curve represents the vibration amplitude of the central coil of the valve spring plotted against the camshaft rotation speed. Peaks on the figure represent the resonance vibrations occurring when the natural frequency of the valve spring matches upper harmonics of the valve lift curve. The heights of the peaks are not constant because the amplitudes cn of the harmonics are not constant.

For example, since the peak #10 corresponding to the 10th upper harmonic occurs at the camshaft rotation speed of 1200, the natural frequency of the valve spring subjected to the test is 10×(1200/60)=200cps=12000cpm.

To prevent the surging, the following methods can be considered.

Fig. 8. Valve spring resonance curve example

It is generally difficult to prevent the spring resonance at all harmonics of the valve lift curve within the engine speed variation range.

However, as can be surmised from the fig.8, since the amplitude of upper harmonics decreases as the order of the harmonic increases, the resonance oscillation also decreases inevitably. Therefore, if the spring natural frequency is made as high as possible so that the resonance occurs only at higher order harmonics, this can considerably reduce the effect of surging. However, care should be taken because high natural frequency tends to increase the stress due to initial compression.

Change the shape of cams

For example, if the lowest natural frequency of the valve spring for engine with rotation speed in the range of 2000-3000 rpm is set to 500cps, it will resonate at 10th-15th harmonics. Therefore, it is enough to design the cams so that the amplitude of these harmonics is small.

Use springs with nonlinear characteristics

Since the natural frequency of nonlinear compression coil springs depends on the deflection, it can prevent the resonance phenomenon on upper harmonics.

In compression coil springs, if the compression force is applied to two parallel ends of the springs, the diameter of the spring changes according to applied pressure causing the axis of vertical load to shift slightly off-center. This effect causes radial load (lateral load) of compression springs. This is an unavoidable effect in the compression coil springs. For example, in main steam safety valves, when radial load (lateral load) occurs to the coils’ vertical axis, it may shift the axis off the center, preventing the valve from closing properly and causing high-pressure steam leakage problem. At our company, by developing a testing machine to measure radial load (lateral load) and utilizing our know-how on radial load (lateral load) and modification technologies mastered by our craftsmen, it is possible to suppress the radial load (lateral load) to match the intended usage of the springs.
Picture: An eccentric force (thrust load) testing machine Click here for more information on our springs’ applications for safety valves.
### (6) Other Considerations

a. Spring index

When the spring index becomes small, the local stress becomes excessive, and when the spring index becomes large or small, the workability of the spring becomes a problem. Therefore, for the spring index, it is preferable to select within the range of 4 to 15 for hot-formed springs and 4 to 22 for cold-formed springs.

b. Aspect ratio

The aspect ratio (ratio of free height and average coil diameter：

)is set to 0.8 or more to secure a number of active coils, and in consideration of buckling, it is generally preferable to select within the range of 0.8 to 4.

c. Number of active coils

If the number of active coils is less than 3, the spring characteristics will be unstable, and so it is preferable to set the number of active coils to 3 or more.

d. Pitch

If the pitch exceeds 0.5 D, the coil diameter generally changes with an increase in deflection (load). Therefore, it is necessary to correct the deflection and torsional stress obtained from the basic formula, and so 0.5 D or less is deemed to be an appropriate pitch.

The pitch is generally estimated according to the following approximate formula.