200
MPa
100
MPa
0
MPa
173.21
MPa
20
200
MPa
100
MPa
0
MPa
173.21
MPa
20
The Pressure Vessel Calculator determines the stress state in cylindrical pressure vessels subjected to internal pressure. For thin-walled vessels where $$r/t > 10$$, the hoop (circumferential) and axial (longitudinal) stresses are $$\sigma_h = \frac{Pr}{t}, \quad \sigma_a = \frac{Pr}{2t}$$ For thick-walled vessels, the Lamé equations give the stress at the inner surface: $$\sigma_h = P\frac{r_i^2 + r_o^2}{r_o^2 - r_i^2}, \quad \sigma_a = \frac{Pr_i^2}{r_o^2 - r_i^2}$$
Pressure vessels are among the most critical engineered structures — from propane tanks and fire extinguishers to nuclear reactor containment and rocket motor casings. A failure can be catastrophic, which is why pressure vessel design follows strict codes such as ASME BPVC (Boiler and Pressure Vessel Code). This calculator also computes the von Mises equivalent stress for yield assessment under the combined multiaxial stress state.
Internal pressure in a cylindrical vessel creates a biaxial or triaxial stress state. The principal stresses act in three directions: hoop (circumferential), axial (longitudinal), and radial (through-thickness).
Thin-wall approximation (valid when r/t > 10):
$$\sigma_h = \frac{Pr}{t}, \quad \sigma_a = \frac{Pr}{2t}, \quad \sigma_r \approx 0$$
The hoop stress is always twice the axial stress, which is why cylindrical vessels that fail tend to split along their length (perpendicular to the hoop direction). The radial stress varies from −P at the inner surface to 0 at the outer surface but is negligible compared to the other components for thin walls.
Thick-wall (Lamé) equations:
$$\sigma_h = P\frac{r_i^2 + r_o^2}{r_o^2 - r_i^2}, \quad \sigma_a = \frac{Pr_i^2}{r_o^2 - r_i^2}, \quad \sigma_r = -P \text{ (at inner wall)}$$
For thick walls, radial stress is significant and equals −P at the inner surface (compressive). The hoop stress at the inner wall is the maximum stress in the entire vessel.
The von Mises equivalent stress combines all three principal stresses into a single scalar for yield comparison: $$\sigma_{VM} = \sqrt{\frac{1}{2}\left[(\sigma_h - \sigma_a)^2 + (\sigma_a - \sigma_r)^2 + (\sigma_r - \sigma_h)^2\right]}$$ If $$\sigma_{VM} \geq \sigma_y$$, the material begins to yield.
Design codes typically require a safety factor of 3–4 on burst pressure, meaning the allowable working pressure is one-third to one-quarter of the pressure that would cause failure. The ASME code uses allowable stress values that account for material variability, temperature derating, and weld efficiency factors.
The hoop stress is the dominant stress and the primary design driver — it determines the minimum wall thickness required. The axial stress is exactly half the hoop stress for thin walls. The r/t ratio indicates whether the thin-wall approximation is valid: above 10, the thin-wall formulas are accurate within about 5%. The von Mises stress should be compared to the material's yield strength to assess whether yielding will occur.
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Results
A thin-walled air tank (r/t = 50) at 1.2 MPa develops 60 MPa hoop stress. Using A36 steel (σ_y = 250 MPa), the safety factor is ~4.2 against yield — adequate for static service.
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Results
A thick-walled hydraulic cylinder (r/t = 1.7) at 70 MPa has a von Mises stress of 157 MPa at the inner wall. AISI 4140 steel (σ_y = 655 MPa) provides a safety factor of ~4.2.
Hoop stress (also called circumferential or tangential stress) is the stress acting around the circumference of a cylindrical vessel due to internal pressure. It equals $$\sigma_h = Pr/t$$ for thin walls and is always the largest stress component, which is why vessels fail by splitting lengthwise along a line parallel to the axis.
Use thin-wall formulas when the ratio r/t > 10; the error is less than 5%. For r/t < 10, the Lamé thick-wall equations are necessary because the stress variation through the wall thickness becomes significant. Most piping and storage tanks qualify as thin-walled, while hydraulic cylinders and gun barrels are thick-walled.
This comes from equilibrium. The hoop stress resists pressure acting on a rectangular strip of length L and width 2r (force = P × 2rL), while axial stress resists pressure on the circular end cap (force = P × πr²). The geometry leads to σ_h = 2σ_a for thin walls. This 2:1 ratio is why sausages split lengthwise when overcooked.
Von Mises stress combines the three principal stresses into a single equivalent value that can be compared to the uniaxial yield strength. According to the von Mises yield criterion, yielding begins when $$\sigma_{VM} \geq \sigma_y$$. It is the most widely used failure criterion for ductile metals under multiaxial loading.
ASME BPVC Section VIII Division 1 uses a safety factor of 3.5 on ultimate tensile strength (or equivalently ~2.4 on yield). Division 2 (with more detailed analysis) permits a factor of 2.4 on UTS. European standard EN 13445 uses similar values. Higher factors apply for fatigue-critical or high-consequence applications.
This calculator is designed for internal pressure. External pressure (vacuum vessels, submarine hulls) involves buckling failure, which requires different analysis. Under external pressure, the critical failure mode is elastic instability rather than yielding, and the formulas involve vessel length and buckling coefficients.
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