Custom drive assemblies: decisions after the estimate
A custom drive assembly integrates a motor, transmission, wheel, bearings and mounting interfaces around an application’s load, motion and packaging requirements. This guide covers AMR and AGV wheel-drive assemblies; conveyor and linear-axis drives need different load models.
The tool estimates straight-line traction demands. The report helps turn those numbers into a reviewable assembly specification: mounting loads, packaging, environment, energy handling and delivery responsibilities. Updated .
Published · By AMRDriveUnit. Author-derived concept calculations; no independent hardware testing or customer results are claimed.
C / P · Dynamic rating and equivalent load
Review the load path before selecting a bearing
Wheel load is not the same as each bearing reaction. Overhang, support spacing, side loads and the load spectrum must be resolved before requesting rating life.
ISO 281:2007 — Rolling bearings: Dynamic load ratings and rating lifeCAD · Envelope review required
Package suspension and transmission together
A wheel fitting below a deck does not establish assembly clearance. Compare CAD envelopes at full suspension travel, steering rotation and service access.
Page method and assumptionsmu × N · Illustrative traction limit
Check traction before increasing torque
Compare force demand with mu × driven normal load. Added motor torque cannot recover grip lost through unloading, contamination or unsuitable tread.
Page method and assumptionsTest · Compound and floor dependent
Treat tread numbers as assumptions
The compound name alone does not establish rolling resistance, contact pressure or wet-floor grip. Request wheel-specific load/speed curves and application tests.
Vulkollan® — Polyurethane elastomer overview20 Jan 2027 · Machinery Regulation application date
Separate component delivery from vehicle conformity
Classify the delivered scope. A drive system may be partly completed machinery; its documents do not establish conformity of the finished robot.
Machinery — Compliance and conformity35 mm · Illustrative offset, not a requirement
Steering offset needs its own load case
Stationary steering depends on pivot offset, footprint and floor friction. This tool illustrates one geometry and does not select a steering motor.
Page method and assumptionsJ and W · Energy and power review
Assess regenerated energy, not only peak watts
Battery acceptance, drive bus capacity, stop repetition and compatible resistor ratings decide the braking energy path. A low-power result is not proof of safe absorption.
Regeneration resistors — sizing and drive compatibilityDuty · Hours per day are insufficient
Verify heat on the actual duty cycle
A motor loss estimate is not winding temperature. Obtain thermal resistance, ambient conditions and a representative loaded cycle before deciding on passive cooling.
IEC 60034-1:2026 — Rotating electrical machines: Rating and performanceCalculation method, known inputs and uncertainty
These are author-derived concept models, not standard-prescribed ratings. With gross mass M, gravity g = 9.80665 m/s², grade angle θ = atan(grade% / 100), drive count n and wheel radius r:
- Static normal load per module
- M × g × cos(θ) × assumed driven weight fraction / n. Side loads, shocks and load transfer are excluded.
- Steady and acceleration torque
- Steady force = Crr × M × g × cos(θ) + M × g × sin(θ). Peak adds M × speed / acceleration time. Wheel torque = force × r / n.
- Wheel RPM, power and DC current
- RPM = speed × 60 / (2πr). Wheel output power = torque × speed / r. DC current = wheel power / (0.75 × bus voltage).
- Traction feasibility
- Assumed available grip = mu × driven normal force. Demand ≥ available grip triggers a warning. A lower result is conditional on the assumptions, not a wet-floor approval.
- Illustrative steering and regeneration
- Swerve scrub = mu × module normal load × (0.035 m + 2/3 × 0.025 m). Regen = M × (1.2 m/s² + g × sin(θ)) × speed × 0.85 / n; rolling losses omitted.
- Illustrative motor heat and holding
- Motor heat = wheel power / 0.90 × (1 / 0.88 − 1). Wheel-side holding target = grade force × r × 1.5 / n when selected. No motor-side brake ratio or stopping-distance model is included.
Driven weight fractions (60/65/70/75%) and tread Crr/mu are illustrative presets; mounting type does not determine vehicle weight distribution. Measure normal loads and grip. Equal module sharing is assumed. Dual-wheel module results combine both traction motors. Daily duty and environment selections describe RFQ context; they do not change these steady-state equations or prove a product rating.
Unknown here: bearing life, winding temperature, safe battery acceptance, resistor rating, protective-field distance and conformity. Request supplier calculations and application tests before hardware approval.
Bearing reference method: L10h = 10⁶ / (60 × RPM) × (C/P)^p, with p = 3 for ball bearings or 10/3 for rollers. C is dynamic rating, not static C0. This page does not have the bearing inputs to evaluate it. SKF bearings and mounted products — Bearing life
1. Mounting topology and load-path review
Qualitative engineering comparison; payload limits and stress ratios require a specific design.
| Topology | Useful when | Trade-off | Release evidence |
|---|---|---|---|
| Cantilevered axle | Exterior tire service matters | Overhang creates a bearing reaction couple | Shaft fatigue and bearing reactions from actual geometry |
| Straddle fork | Support can fit on both wheel sides | Wider package and additional interfaces | Alignment, fork stiffness and assembly tolerance review |
| Steerable swerve | Independent drive and azimuth are needed | Steering torque and cable routing add complexity | Pivot/traction load cases and steering endurance |
| Dual-wheel differential | Two traction motors can create pivot motion | Module demand must be split between two motors | Unequal wheel load, control and residual scrub tests |
2. Transmission and packaging options
No universal minimum chassis height or efficiency is implied. Request drawings and efficiency maps.
| Option | Packaging benefit | Cost or performance risk | Verify |
|---|---|---|---|
| Inline planetary | Simple coaxial load path | Axial stack may constrain integration | Output bearing rating, ratio and service access |
| Right-angle reducer | Routes motor alongside axle | Losses and mounting cost vary with design | Backdrivability, lubrication and mounting orientation |
| In-wheel transmission | Moves parts inside wheel envelope | Heat rejection and tire replacement access | Loaded temperature, shock and complete CAD envelope |
3. Suspension compliance choices
Tool travel and preload values are discussion placeholders; they are not design prescriptions.
| Mechanism | Potential benefit | Risk | Validation |
|---|---|---|---|
| Rigid mounting | Simple, compact and inexpensive | Wheel unloading on uneven floors | Chassis/caster compliance and measured wheel normal load |
| Elastomer stack | Compact compliance and damping | Temperature dependence and creep | Force-deflection and aging over operating temperatures |
| Disc spring stack | High force in limited axial space | Friction and stack tolerances | Installed preload and fatigue under actual cycling |
| Coil/rocker | Longer controllable travel | More packaging, joints and maintenance | Jounce/rebound clearance and contact over floor joints |
4. Known and missing bearing inputs
ISO 281 addresses rating life; it does not supply a universal bearing type or lifetime for a vehicle mass.
| Input | Available here | Missing evidence | Consequence |
|---|---|---|---|
| Wheel radial load | Static estimate in N | Side loads, overhang, bearing spacing and shocks | Calculate individual bearing reactions |
| Dynamic load rating C | Unknown | Specific bearing catalog entry | No numerical L10h output |
| Equivalent dynamic load P | Unknown | Bearing-specific radial/axial factors and duty spectrum | Wheel normal force cannot substitute for P |
| Speed and environment | Wheel RPM estimate only | Actual bearing speed, lubrication and contamination | Supplier life review remains necessary |
5. Wheel tread assumptions and procurement checks
These Crr/mu pairs are editable-model presets in the source, not manufacturer-certified values or wet-floor claims.
| Tread option | Illustrative Crr / mu | Useful comparison | Supplier evidence |
|---|---|---|---|
| NDI PU 95A | 0.011 / 0.65 | Dynamic load, rolling loss and tread heating | Specific wheel load/speed curve and compound data |
| General PU 92A | 0.016 / 0.60 | Initial cost, floor marking and comfort | Grip and rolling tests on the actual floor |
| ESD PU | 0.018 / 0.55 | Electrical resistance versus wear and grip | Complete discharge path and resistance test conditions |
| Cold-storage PU | 0.022 / 0.45 | Cold flexibility and moisture exposure | Cold-soak grip, material and seal test results |
6. Environment targets and acceptance tests
An IP code concerns ingress under defined tests. It does not establish chemical compatibility, cleanliness or cooling.
| Target | What to specify | Common mismatch | Acceptance evidence |
|---|---|---|---|
| Indoor IP54 target | Dust and splash exposure | Dust accumulation at seals and cooling paths | Assembly test scope and maintenance access |
| IP65 jet-exposure target | Water jet conditions and cleaning agents | Hot/high-pressure washdown assumed from IP65 | Exact cleaning protocol and complete-assembly report |
| IP67 immersion target | Immersion conditions and moving shaft state | Immersion rating treated as continuous underwater service | Test depth/time and dynamic operating limitations |
| Cleanroom target | Particle budget and vehicle operating cycle | Ingress rating mistaken for cleanroom qualification | System particle measurements and lubricant/tread suitability |
7. Controller placement and electrical interfaces
Compare complete installation costs and serviceability; no standard topology is always best.
| Layout | Benefit | Integration risk | Verify |
|---|---|---|---|
| Integrated inverter | Short motor cabling | Motor heat shares enclosure with electronics | Thermal derating, connector and EMC results |
| Remote inverter | Accessible electronics and cooling | Longer phase/encoder harnesses | Cable limits, shielding and feedback integrity |
| Shared DC bus | Potential energy sharing across axes | A bus fault can affect multiple drives | Fault containment, fusing and simultaneous regen cases |
8. EU delivery classification and documentation
As of 25 October 2026. Confirm placing-on-market date and actual supply scope before agreeing the deliverables.
| Case | Framework | Documents or action | Boundary |
|---|---|---|---|
| Machinery placed before 20 Jan 2027 | Directive 2006/42/EC | If PCM: Article 13, Annex II 1 B declaration and Annex VI instructions | Classify the delivered product; do not infer from marketing name |
| PCM under Regulation from 20 Jan 2027 | Regulation (EU) 2023/1230, Article 3(10) | Article 11; Annex V Part B declaration and Annex XI assembly instructions | PCM documents do not certify the finished robot |
| Finished driverless truck | Applicable law and vehicle safety assessment | OEM completes assessment and applicable declaration/marking | ISO 3691-4 concerns the truck/system, not a calculator certification |
| Other applicable legislation | Depends on supplied electrical equipment | Review applicable EMC and other requirements | No machinery CE on PCM does not prohibit marks required by other legislation |
9. Steering geometry decisions
Engineering model, not a VDMA-prescribed sizing method. Actual footprints and friction must be measured.
| Configuration | Model treatment | Risk | Next step |
|---|---|---|---|
| Offset swerve pivot | mu × N × offset plus illustrative patch torque | Unknown friction and footprint dominate uncertainty | Supply pivot offset, wheel width and measured steering torque |
| Near-coaxial pivot | Offset term can reduce | Contact patch still resists stationary pivoting | Verify steering actuator over worst floor/load case |
| Dual-wheel pivot | Not modelled | Residual scrub and unequal loading remain possible | Review wheel spacing, motor split and control |
| Fixed wheels / skid steering | Not modelled | Wheelbase and lateral slip can dominate | Use complete vehicle geometry and turning tests |
10. Regeneration energy review
Example deceleration is 1.2 m/s², with 85% recovery and rolling losses omitted. Neither value is an ISO requirement.
| Operating condition | Unknown here | Risk | Mitigation to evaluate |
|---|---|---|---|
| Full battery | BMS charge-current permission | Regen rejected despite a small power estimate | Controller/BMS coordination and compatible energy sink |
| Cold battery | Temperature-dependent acceptance | Charge limits differ from room-temperature behavior | Cold-condition stopping tests |
| Repeated downhill stops | Pulse energy, frequency and resistor limits | Resistor overheats although peak watts appear acceptable | Energy/duty calculation and supplier-approved chopper/resistor |
| Power loss | Available braking path | Dynamic braking is not power-off holding | Holding brake and complete-vehicle stopping assessment |
11. Thermal design review
No universal 35 W passive-cooling limit, TIM specification or temperature reduction can be established here.
| Item | Tool treatment | Missing input | Release test |
|---|---|---|---|
| Motor loss | Wheel power / 0.90 × (1 / 0.88 - 1) | Actual efficiency map and acceleration/stall losses | Representative load-cycle energy and temperature |
| Chassis conduction | Possible integration option | Contact area, flatness, preload and thermal resistance | Measure winding/housing/chassis temperatures |
| Sealed housing | Environment target only | Ambient, airflow and external surface area | Hot ambient and worst installation test |
| Operating hours | RFQ context only | Time at each torque and speed, rest and starts | Supplier duty classification and derating review |
12. Steering power and data routing
Cable-cycle life and network reliability depend on the specified product and installed motion profile.
| Choice | Benefit | Trade-off | Evidence required |
|---|---|---|---|
| Torsion-rated harness | Continuous conductors without sliding contacts | Limited angular travel and unwind planning | Bend/twist limits and cycle test under actual temperature |
| Slip ring | Can support continuous rotation | Contact wear, protocol compatibility and maintenance | Rated power, fieldbus tests, sealing and debris containment |
| Limited-angle routing | Simplifies cable path | May constrain maneuver planning | Hard stops, software limits and fault recovery |
| Separate data/power paths | Can ease interface selection | More joints and integration cost | EMC, shielding, strain relief and maintenance validation |
Misuse, cost and scenario mismatch
Misuse risk
A green-looking number is not release evidence. Treat grip, stopping, life and thermal validation as separate acceptance items; request signed calculations and loaded tests.
Cost risk
Custom forks, seals, steering interfaces, special compounds and test fixtures add tooling, qualification and service costs. Quote these separately, agree NRE ownership and compare a modified catalog module. Prices and lead times are unknown until quoted.
Scenario mismatch
Cold rooms, oily ramps, cleanrooms and aggressive washdown can invalidate the dry-floor model. Share the actual environment and duty. Consider slower travel, a different route, shielding or a revised chassis before adding complexity.
Six illustrative engineering scenarios
Design exercises, not customer deployments or measured performance. Each scenario ends with the evidence still needed for a decision.
165 mm deck concept
Illustrative design scenario · no customer test results claimed
- Vehicle mass
- 800 kg gross
- speed
- 1.2 m/s
- envelope
- 165 mm deck target
- mounting
- Straddle or in-wheel
- environment
- Indoor
Constraint: A low deck can fit the wheel yet leave insufficient space for a gearbox, steering sweep or suspension travel.
Approach: Compare inline, right-angle and in-wheel layouts using a common vehicle CAD envelope. Reserve ground clearance and tire replacement access.
Validation status: Pending: check full jounce/rebound and steering sweep in CAD, then instrument the loaded drive on the intended shift cycle.
Trade-off: A compact layout may increase machining and cooling costs. A higher deck or revised wheel diameter may be a simpler alternative.
3,500 kg four-module swerve concept
Illustrative design scenario · no customer test results claimed
- Vehicle mass
- 3,500 kg gross
- speed
- 1.2 m/s
- envelope
- 350 mm deck target
- mounting
- Four swerve modules
- environment
- Indoor
Constraint: Stationary steering and uneven wheel loading can govern pivot and bearing selection even when straight-line wheel torque appears modest.
Approach: Use the heavy swerve preset for traction demand, then request steering torque and bearing reaction calculations using real offset and footprint dimensions.
Validation status: Pending: weigh each driven module, measure steering current/torque at standstill and rolling turns, and review pivot fatigue loads.
Trade-off: Near-coaxial pivots can ease steering but constrain packaging. Four modules add actuators, calibration and service tasks.
Washdown drive concept
Illustrative design scenario · no customer test results claimed
- Vehicle mass
- 1,200 kg gross
- speed
- 1.0 m/s
- envelope
- 300 mm deck target
- mounting
- Straddle fork
- environment
- IP67 target
Constraint: An immersion target does not settle resistance to detergents, hot jets or shaft-seal wear during cleaning and motion.
Approach: Agree the actual washdown protocol, exposed materials, drain paths and seal arrangement with the supplier before selecting the ingress test scope.
Validation status: Pending: complete-assembly ingress and chemical exposure tests, followed by functional checks with the shaft operating as specified.
Trade-off: Added sealing raises drag and thermal integration demands. Shielding the drive from the wash zone may reduce complexity.
−30°C cold-storage concept
Illustrative design scenario · no customer test results claimed
- Vehicle mass
- 1,500 kg gross
- speed
- 1.4 m/s
- envelope
- 280 mm deck target
- mounting
- Dual-wheel module
- environment
- Cold-soak target
Constraint: Cold tread behavior, lubricant viscosity and restricted battery charge acceptance affect traction and stopping; a room-temperature model is insufficient.
Approach: Use the cold-storage preset only as a discussion baseline. Request temperature-specific wheel, lubricant, seal, controller and BMS data.
Validation status: Pending: cold-soak start/stop and loaded ramp tests, plus repeated transitions to a warm humid dock to assess condensation.
Trade-off: Low-temperature formulations and heaters can add cost and battery draw. Reduce speed or isolate temperature zones where practical.
Cleanroom transport concept
Illustrative design scenario · no customer test results claimed
- Vehicle mass
- 500 kg gross
- speed
- 1.0 m/s
- envelope
- 220 mm deck target
- mounting
- Limited-angle swerve
- environment
- Cleanroom target
Constraint: An ingress-rated assembly can still emit particles from tread wear, seals and steering contacts, so cleanliness needs a separate acceptance plan.
Approach: Compare limited-angle torsion harnesses and qualified slip-ring assemblies against maneuver requirements and a defined particle budget.
Validation status: Pending: measure particles on the moving vehicle under its actual load cycle, and test network integrity across the steering travel.
Trade-off: Limited rotation requires unwind planning. Special lubricants, containment and test programs add cost without automatically qualifying the vehicle.
Repeated ramp-stop concept
Illustrative design scenario · no customer test results claimed
- Vehicle mass
- 2,000 kg gross
- speed
- 1.5 m/s
- envelope
- 300 mm deck target
- mounting
- Two traction modules
- environment
- 10% ramp target
Constraint: High charge state and repeated downhill braking can remove battery acceptance or overload a resistor even if the drive torque is adequate.
Approach: Compare traction demand to measured grip, specify a power-off holding path and review stop energy against drive/BMS and resistor capabilities.
Validation status: Pending: stopping and holding tests at worst load, full charge and battery temperature; record DC bus voltage and resistor temperature.
Trade-off: A different route, lower speed or shallower grade can reduce demand. None of these replaces the vehicle risk assessment.
Assembly engineering and sourcing FAQ
mechanical
What is included in a custom drive assembly?
Agree the supplied boundary: wheel, hub, bearings, gearbox, traction motor, brake, suspension and optional steering. The word assembly alone does not define the bill of materials or interface responsibility.
Does a straddle fork always outperform a cantilever axle?
No. A straddle layout supports both sides but occupies more width and introduces alignment constraints. Compare actual overhang, support spacing, side loads, service access and fatigue calculations rather than a fixed stress multiplier.
Can the tool predict bearing life in hours?
No. It estimates static wheel radial load, not individual bearing reactions or equivalent dynamic load P. A rating-life calculation needs the selected bearing dynamic rating C, speed/load spectrum and operating conditions. See the ISO 281 and SKF references.
Does mounting topology determine driven weight share?
No. Vehicle center of gravity, support locations, preload and load transfer determine it. The calculator uses disclosed illustrative shares of 60%, 65%, 70% or 75% by preset topology; replace them with measured loads for selection.
What does the height clearance validation establish?
It only checks that the entered deck envelope exceeds the wheel diameter. A valid result does not prove clearance for the gearbox, steering sweep, tire growth, suspension movement or service access; review these in CAD.
Is the calculated radial load a shock or bearing load rating?
No. It is a static normal-load estimate on a constant incline, shared equally across modules. Floor impacts, load transfer, lateral forces, axle bending and individual bearing reactions require separate vehicle and structural models.
transmission
How should a gearbox ratio be selected?
Start with wheel RPM and torque demand, then compare motor speed, output bearing ratings, gearbox efficiency maps and acceleration duty. This tool does not select a ratio or establish motor-side peak and stall current.
Are suspension travel and preload design requirements?
No. The displayed travel values and 85% preload are discussion placeholders. Spring geometry, force-deflection curves, floor survey, load variation and wheel contact tests must establish the required design.
Can more motor torque prevent wheel slip?
Only while grip is available. The tool compares demand to an assumed mu times driven normal load. If demand exceeds that limit, revise acceleration, grade, load distribution or tread and measure grip; torque alone cannot fix slip.
Are the tread Crr and friction values verified specifications?
No. They are transparent illustrative modeling inputs, not certified material constants. Wheel size, load, speed, temperature and floor contamination can change both values; obtain wheel-specific supplier data and tests.
Does a dual-wheel differential have zero steering resistance?
No zero-scrub guarantee is made. Counter-rotation can reduce some pivot resistance, but spacing, unequal loads and tire deformation matter. Steering scrub is shown as not modelled for that architecture.
How do cold storage and washdown change selection?
Specify actual temperature cycles, moisture, cleaning chemistry and exposure. Confirm tread, lubricant, seal and electronics compatibility through application tests; selecting an environment target in the tool does not qualify a product.
electrical
Is displayed DC current the motor phase current?
No. It is an estimate from traction wheel power divided by 75% combined efficiency and nominal DC voltage. It excludes steering, auxiliary loads, stall and cable losses; phase current depends on motor torque and winding design.
Does a low regenerative power estimate prove battery acceptance?
No. Battery acceptance may be restricted at full charge or low temperature regardless of the estimated watts. Review BMS charge limits, bus voltage and stop energy/repetition with the drive supplier before deciding on an energy sink.
Is 1.2 m/s² a mandatory ISO emergency-stop deceleration?
No. It is an illustrative value used only in this page’s regenerative power model. Safe stopping behavior must be derived and verified for the actual truck, load, floor and operating zone; this tool supplies no protective-field setting.
Can the tool size a braking resistor?
No. Peak power alone does not determine resistance, pulse energy or average thermal rating. The selected drive/chopper limits, kinetic and grade energy, stopping time and repeated duty are needed; request supplier approval.
Does a heat-loss result establish safe winding temperature?
No. The heat estimate assumes 90% gearbox and 88% motor efficiency at steady wheel power. Temperature needs thermal resistance, ambient, cooling, acceleration duty and supplier limits, followed by a representative loaded test.
Are slip rings or torsion harnesses always more reliable?
Neither is universally preferable. Compare rotation range, protocol compatibility, power, sealing, wear debris and maintenance using specified products and motion-cycle tests; no generic cycle count or error-free transmission is promised.
regulatory
Is every drive assembly partly completed machinery?
Classification depends on the supplied scope and intended function. A drive system intended for incorporation may be PCM, but a component or complete machine needs its own assessment. Ask the supplier to document the classification and applicable legislation.
Which EU machinery framework applies in October 2026?
The Commission states that machinery placed on the market before 20 January 2027 must comply with Directive 2006/42/EC. Regulation (EU) 2023/1230 generally applies from that date; agree the placing-on-market date and review transition details.
Which documents accompany partly completed machinery?
For PCM under the Directive, review Article 13, Annex II section 1 B and Annex VI. Under the Regulation, review Article 11, Annex V Part B and Annex XI. The correct delivery scope and placing-on-market date decide the document set.
Does PCM status prohibit every CE mark on electrical equipment?
PCM is not CE-marked as completed machinery under machinery legislation. Other applicable EU legislation may impose its own marking duties. Supplier documents should identify the applicable rules; incorporation does not certify the completed vehicle.
Does ISO 13849-1 require PL d Category 3 for every function?
No. ISO’s public scope states that ISO 13849-1 does not specify application-specific safety functions or required performance levels. Determine the function and PLr from applicable requirements and risk assessment, then validate the architecture.
What is the next step after copying the engineering brief?
Paste the brief into the contact form’s 4,000-character Project Summary and add quantity, destination and timing. Attach or offer CAD, measured wheel loads, duty and environment details; request a technical review before approving component selection.
Sources, dates and evidence limits
Reviewed 25 October 2026. Public standards summaries establish scope and editions; they do not substantiate unquoted clause-level requirements or this tool’s illustrative constants. Use the applicable full standards for a formal assessment. VDMA 24186 is a building-maintenance reference and is not used for steering sizing; no generic cable cycle guarantee is attributed to DIN EN 50525.
ISO 3691-4:2023 — Driverless industrial trucks and their systems
ISO · 2023-06
Public scope: truck/system safety requirements and verification. It does not substantiate this page’s illustrative 1.2 m/s² value.
Open official source: ISO 3691-4:2023 — Driverless industrial trucks and their systemsISO 13849-1:2023 — Safety-related parts of control systems
ISO · 2023-04
Public scope: design methodology. It explicitly does not prescribe application-specific safety functions or PLr.
Open official source: ISO 13849-1:2023 — Safety-related parts of control systemsISO 281:2007 — Rolling bearings: Dynamic load ratings and rating life
ISO · 2007-02; confirmed 2021
Public scope: dynamic rating and fatigue-life method, not life promised from vehicle mass or mounting type.
Open official source: ISO 281:2007 — Rolling bearings: Dynamic load ratings and rating lifeRegulation (EU) 2023/1230 on machinery
European Union / EUR-Lex · 2023-06; consolidation 2026-07-27; reviewed 2026-10-25
Article 3(10) defines PCM. Article 11 and Annex V Part B / Annex XI cover its delivery obligations.
Open official source: Regulation (EU) 2023/1230 on machineryIEC 60034-1:2026 — Rotating electrical machines: Rating and performance
IEC · 2026-03-13
Public catalog scope for motor rating/performance. Not evidence for a universal sealed-hub cooling limit.
Open official source: IEC 60034-1:2026 — Rotating electrical machines: Rating and performanceVulkollan® — Polyurethane elastomer overview
Covestro · Undated; accessed 2026-10-25
Manufacturer material-family overview only. No wheel-specific Crr, mu, pressure or temperature rating is established here.
Open official source: Vulkollan® — Polyurethane elastomer overviewIEC 60529:1989+A1:1999+A2:2013 — IP Code
IEC · 2013-08-29
Public catalog scope: enclosure protection classification. Application-specific cleaning and operating conditions need separate review.
Open official source: IEC 60529:1989+A1:1999+A2:2013 — IP CodeMachinery — Compliance and conformity
European Commission · Undated; accessed 2026-10-25
Confirms Directive compliance before 20 January 2027 and the Regulation’s mandatory application date.
Open official source: Machinery — Compliance and conformityDirective 2006/42/EC on machinery
European Union / EUR-Lex · 2006-05-17
Article 13, Annex II 1 B and Annex VI: PCM incorporation procedure, declaration and assembly instructions.
Open official source: Directive 2006/42/EC on machineryRegeneration resistors — sizing and drive compatibility
Kollmorgen · Undated; accessed 2026-10-25
Explains DC bus energy dissipation and the need to match resistor sizing to the drive. Not an AMR product endorsement.
Open official source: Regeneration resistors — sizing and drive compatibilitySKF bearings and mounted products — Bearing life
SKF · 2018 catalog; accessed 2026-10-25
Basic rating-life relationship using C, P, exponent and speed; service conditions affect actual life.
Open official source: SKF bearings and mounted products — Bearing lifeTurn the estimate into an engineering review
Copy the tool brief into Project Summary and add quantity, destination and timing. Share CAD envelopes, measured wheel loads, floor/grade conditions and a speed/torque duty profile. Request interface drawings, bearing calculations, thermal/stop tests, itemized NRE and the applicable delivery documents.