VALICALC / MECHANICAL ENGINEERING SUITE / DS11
Review duty and stress at the actual selected gear dimensions. Linked DS10 geometry updates when teeth, module or profile shift change. Classical spur stress estimates are separated from complete ISO/AGMA rating, material qualification and fatigue-life verification.
Verified mathematical models with explicit assumptions. Component capacity and applicability are shown as separate checks.
Labeled example inputs • SI calculations • Project revision 0 • No account or cloud upload
01 / ENGINEERING INPUTS
02 / CALCULATE → SELECT → RECALCULATE
Peak tangential mesh force
5,000 NNominal peak radial force
1,819.85117 NNominal peak helical axial force
0 NPeak pinion shaft power
15.70796 kWPinion load-cycle count
112,500Gear load-cycle count
37,500Actual pitch ratio
3Peak preliminary Lewis pinion stress
185.18519 MPaPeak preliminary Lewis gear stress
158.73016 MPaPeak ideal Hertz pitch-point pressure
920.05414 MPaReduced pitch-point contact radius
7.69545 mmReduced elastic contact modulus
115,384.61538 MPa| Case | T1 (N·m) | RPM1 | Ft (N) | P1 (W) | Pinion cycles | Gear cycles | Lewis pinion (Pa) | Lewis gear (Pa) | Hertz (Pa) |
|---|---|---|---|---|---|---|---|---|---|
| 1 | 100 | 1,500 | 3,333.333333 | 15,707.963268 | 90,000 | 30,000 | 123,456,790.123457 | 105,820,105.820106 | 751,221,056.734507 |
| 2 | 150 | 750 | 5,000 | 11,780.972451 | 22,500 | 7,500 | 185,185,185.185185 | 158,730,158.730159 | 920,054,136.516958 |
Inputs are read directly from the current project and recalculated, not from stale saved results.
Lewis estimate only; no calibrated full rating factors. No positive applicable limit was supplied.
Lewis estimate only. No positive applicable limit was supplied.
Ideal elastic pitch-point pressure; not a pitting life prediction. No positive applicable limit was supplied.
Example Y and elastic modulus are not approved material or tooth factors. Applicability and actual duty spectrum require engineering review.
Complete applicable standard, material/heat-treatment data, load factors, accuracy, lubrication and independent benchmark are not available. No certified load capacity.
Actual working pitch diameter gives Ft = 2T/dw. Each supplied case contributes n t/60 times the entered mesh-count convention.
Lewis factor is module-based Y; do not substitute a circular-pitch y without its π conversion. No historical lookup table or empirical load factor is applied.
Hertz uses local involute curvature rb tan(αw), full single-pair normal load and reduced elastic modulus; helical/internal stress is deliberately withheld.
Geometry changes rerun every duty/stress case. Spectrum aggregation into fatigue capacity is method-specific and remains blocked.
Classical Lewis σ = Ft/(b m Y) uses the supplied dimensionless module-based Y convention (not a circular-pitch y without π conversion). Full single-tooth tangential load is assumed; dynamic/distribution factors are not fabricated.
Hertz estimates ideal elastic line contact at the working pitch point for external spur gears. Surface roughness, load sharing, misalignment, lubrication and pitting life require a complete applicable rating method.
Helical/internal linked geometry still gives duty and nominal force calculations; the classical spur root/contact stress models are blocked. No full ISO 6336/AGMA capacity or fatigue life is certified.
An unshifted external 20/60-tooth, 3 mm module pair has a 60 mm pinion pitch diameter. At 100 N·m, Ft = 3333.33 N. With 30 mm face and illustrative Lewis Y = 0.30, nominal pinion bending is 123.457 MPa. A separate 150 N·m duty case controls peak stress; material approval stays unresolved.
Actual working pitch diameter and explicitly entered per-member mesh-count convention. Magnitudes and peak stresses are not equivalent fatigue-life ratings.
Independent torque/work and revolution counting; Tập 1 6.6 printed p93 / PDF92 and geometry context pp99–106.
External spur, module-based supplied Y. The circular-pitch form uses y = Y/π. A simple cantilever reduction gives Y = tRoot²/(6 m hLoad); exact tooth form, root concentration and dynamic factors remain unqualified.
Independent cantilever bending reduction and supplied dimensionless tooth form. Current ISO/AGMA rating is not implemented; empirical Y/material tables are not copied.
External spur working-pitch point, local involute curvatures R1 = rb1 tanαw, R2 = rb2 tanαw; full single-pair load and ideal elastic parallel-cylinder approximation. No pitting-life approval.
Textbook references identify the method context. Historical numerical catalog, material and service-factor tables have not been copied or treated as current product ratings.
Existing component-selection Jobs → · All mechanical worksheets →
No. The worksheet separates mathematical results from criterion-specific checks. Actual motor, belt, gear, shaft, bearing and joint capacity need applicable current source data and engineering review.
The worksheet recalculates the outputs and geometry from the entered actual dimensions or discrete tooth/link count. Dependent checks are reevaluated; previously saved results are not restored as approvals.