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04 / ENGINEERING VERIFICATION

Check what the
geometry means.

Explore one calculation at a time. The section properties, fits and engagement checks connect the model to mechanical design.

Section properties, guide spacing, fits and engagement
ENGINEERING BEYOND CAD

Geometry → Mechanics → Verification

The dimensions establish geometry. Section properties, load paths, engagement and tolerances establish the questions that an engineering design must answer.

A / SECTION PROPERTIES

Guide pillar: geometry becomes mechanics

For a solid circular guide with d = 25 mm:

A = πd² / 4 = 490.87 mm²
I = πd⁴ / 64 = 19,174.76 mm⁴
Z = I / (d/2) = 1,533.98 mm³
r = √(I/A) = 6.25 mm

Area A comes from the circle’s geometry. The second moment I is the area integral of squared distance from a centroidal bending axis; it describes how effectively the section distributes material against bending. Section modulus Z converts bending moment to maximum nominal stress. Radius of gyration r connects area and bending distribution.

These geometric properties provide the link between the CAD dimensions and analytical stress/stiffness calculations.

B / COLUMN SCREENING

Check the slenderness before choosing a model

λ = L/r = 200 / 6.25 = 32

The geometric slenderness ratio is approximately 32 for the full 200 mm pillar. This is not a highly slender member, so a simple Euler result should not automatically be treated as the governing compressive capacity. Material yielding, actual effective length, end restraint and contact conditions must be established before a column capacity is claimed.

The effective slenderness for a column model is KL/r, where K represents its end restraint. The calculation above uses geometric length only; it is not an allowable-load calculation.

C / GUIDE-BUSH CONTACT

Projected bearing area

For one bush, d = 25 mm and L = 60 mm. The projected cylindrical interface is a rectangle d wide and L long.

Ab = dL = 25 × 60 = 1,500 mm² per bush
Ab,total = 4dL = 6,000 mm²
pavg = F / (4dL)

The pressure expression applies if a total lateral load F distributes equally among all four bushes over the full contact length. With F in newtons and area in mm², pressure is in MPa.

This projected-area calculation provides a first screening method for interface bearing pressure. A production design would additionally require bush material, clearance, lubrication, loading distribution and wear criteria.

D / GUIDE FOOTPRINT

Spacing gives a moment its reaction couple

sx = 190 mm   ·   sy = 90 mm
sdiag = √(190² + 90²) = 210.24 mm
F ≈ M/s

The diagonal follows the Pythagorean theorem. The reaction relation follows moment equilibrium: two equal and opposite forces separated by s create a couple M = Fs.

A wider guide spacing reduces the reaction force required to resist the same overturning moment. The actual force distribution among four guides depends on the direction of loading, clearances and structural stiffness. Use the separation perpendicular to the force couple; the diagonal is not automatically the governing lever arm.

E / FIT & CLEARANCE

Equal nominal diameters do not define a sliding fit

dp = 25 mm   ·   Db = 25 mm
Cd = Db − dp = 0 mm nominal
Cmin = Db,min − dp,max
Cmax = Db,max − dp,min

The source geometry defines both mating diameters nominally as Ø25 mm. Nominal CAD dimensions alone do not define a manufacturable sliding fit. Production design would require an intentional tolerance class based on accuracy, lubrication, temperature, manufacturing process and service conditions.

ISO 286 fit selection would be a logical next design step.

F / GUIDE ENGAGEMENT

Motion needs remaining overlap

eremaining = einitial − S

einitial = initial pillar/bush engagement
S = upward stroke
eremaining = remaining engagement

This relation describes withdrawal where overlap reduces one-for-one with upward travel. While a pillar still extends fully through a bush, its full bush engagement can remain constant; use the actual endpoint geometry to identify the applicable travel interval.

The animation stroke should remain within the geometry that maintains pillar/bush engagement. The website does not claim a design stroke until it is measured from the actual CAD configuration.

Mass and moving weight
ASSUMPTION-BASED MASS CHECK

From volume to moving weight

EDUCATIONAL ASSUMPTION — NOT A SPECIFIED PROJECT MATERIAL

Illustrative steel-density calculation only. Material was not specified by the original exercise.

Steel density ρ = 7,850 kg/m³. Chamfers neglected in hand calculation.

m = ρV   ·   ρ = 7.85 × 10−6 kg/mm³
ComponentQtyMass each
Bottom Plate1≈ 7.91 kg
Top Plate1≈ 9.03 kg
Guide Pillar4≈ 0.771 kg
Guide Bush4≈ 0.361 kg
Trace the volumes behind the mass check

All dimensions below are in mm. The Bottom Plate has four Ø25 guide holes and a Ø50 central hole. The Top Plate has four Ø40 bush holes and an integral Ø50 × 90 boss.

Vbottom = 250 × 150 × 30 − [4π(25²)/4 + π(50²)/4] × 30
Vtop = 250 × 150 × 30 − 4π(40²)/4 × 30 + π(50²)/4 × 90
Vpillar = π(25²)/4 × 200
Vbush = π(40² − 25²)/4 × 60

The totals use unrounded component values. The source drawing is used privately for dimensional checks and is not distributed with this study.

COMPLETE ASSEMBLY

≈ 21.47 kg

Both plates + four pillars + four bushes

MOVING GROUP

≈ 10.48 kg

Top Plate + four Guide Bushes

W = mg ≈ 10.48 × 9.81 ≈ 102.8 N

Moving weight is a gravitational force, not the press force or an actuator rating. Actual SolidWorks Mass Properties should be used for final CAD verification after the intended materials are assigned.

Hand calculation and FEA method
HAND CALCULATION ↔ FEA METHOD

Verify simulation with first principles

FEA verification — planned extension

A Guide Pillar lateral-load study provides a focused verification exercise. For a prismatic, linearly elastic pillar idealized as a fixed cantilever with an end force F, use effective unsupported length Leff:

Mmax = F × Leff
σ = M/Z
σmax = 32FLeff / (πd³)
δ = FLeff³ / (3EI)

Moment follows equilibrium; stress follows elastic beam bending. Integrating beam curvature M/(EI) with zero deflection and rotation at the fixed end gives the tip-deflection expression. E is Young’s modulus. Use consistent units: F in N, lengths in mm and E in N/mm².

This cantilever is a comparison model. Actual bush contact, plate restraint and guide engagement can change the load path. Match the analytical and simulated boundary conditions before comparing their outputs.

  1. Define actual material
  2. Define realistic support/contact
  3. Apply documented study load
  4. Generate mesh
  5. Perform mesh refinement
  6. Record stress/displacement
  7. Compare against hand calculation
Difference % = |FEA − Hand| / |Hand| × 100

Compare the same quantity at the same location using a nonzero hand value. Evaluate nominal bending stress away from an idealized fixed-edge singularity; demonstrate convergence rather than interpreting a single peak. No stress, displacement, safety factor or mesh result is claimed here.

Bill of materials
BILL OF MATERIALS

The component structure

ItemComponentQtyFunction
1Bottom Plate1Fixed structural base
2Top Plate1Guided moving member
3Guide Pillar4Linear alignment
4Guide Bush4Sliding guide interface

4 unique part designs · 10 component instances

Engineering drawings
ENGINEERING COMMUNICATION

Make design intent inspectable

The next step from a parametric model is controlled engineering communication: orthographic views, dimensions, tolerances, assembly balloons and a bill of materials.

The component structure and calculations above establish the basis for that drawing set. A finished drawing gallery can be added when the project’s own engineering drawings are available.

Lessons learned
LESSONS LEARNED

Three principles to carry forward

Model relationships

Robust CAD captures relationships between features rather than isolated dimensions.

Mates represent physics

Assembly constraints should represent the mechanism rather than merely remove every degree of freedom.

Verify the model

Analytical calculations provide an independent check on CAD and simulation results.