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Positioning Cranes vs. Standard Overhead Cranes for Precision Lifts

A positioning crane is an overhead crane specified for what happens in the last few inches of a lift: how slowly and steadily the hook can move, whether the load swings, what the hoist drive proves before it lets go of the brake, and how the lift is planned and watched. UTEC Industrial designs, engineers, machines, fabricates, and installs custom material handling systems for aerospace and heavy industry from its Spokane Valley, WA facility, integrating Allen-Bradley PLC and motion control with in-house CNC machining, heat treating, and stress relief. This article defines the difference by function rather than by product label, and ties each function to the below-the-hook device that actually holds the load. The crane sits on the same build chain as every heavy handling system, design → engineering → parts machining → fabrication → assembly → weld fatigue → stress relief → drives → controls → tuning → monitoring, and the drive, control, and sensing functions that define a positioning crane sit in its last four links: drives, controls, tuning, and monitoring.

What separates a positioning crane from a standard overhead crane?​

Read at the level of their titles and scope lines, the crane standards are organized by construction and service, and a precision-lift crane is still one of those cranes:

  • Top-running bridge and gantry cranes: ASME B30.2-2022.
  • Underhung cranes and monorails: ASME B30.17-2026.
  • The hoist: ASME B30.16-2022 for safety, and ASME HST-4-2021, a performance standard for overhead electric wire rope hoists whose performance chapter has sections on hoist duty service classification, on lift, headroom, and reach, and on hoist and trolley speeds.
  • Design: CMAA Specification No. 70-2025 for multiple-girder cranes, CMAA Specification No. 74-2025 for single-girder cranes, and AIST Technical Report No. 6-2018 for steel mill service.
  • Nuclear facilities: ASME NOG-1-2025.
  • Regulation: OSHA 29 CFR 1910.179 for overhead and gantry cranes in general industry.

None of their titles or scope lines names a "positioning" crane type. In this article the term means a crane specified for four functions on top of its class and capacity:

  1. fine speed control and micro-positioning on the hoist and on the travel motions;
  2. suppression of load sway;
  3. drive-level torque proving, brake proving, and brake-slip monitoring;
  4. the sensing and procedures that critical-lift practice expects.

In engineering terms, the failure mode is a crane bought on capacity, duty class, and top speed alone, none of which says how steadily the hook moves at its slowest or what the load does when the trolley stops (ASME B30.2-2022; ASME B30.17-2026; ASME B30.16-2022; ASME HST-4-2021; CMAA Specification No. 70-2025; CMAA Specification No. 74-2025; AIST Technical Report No. 6-2018; ASME NOG-1-2025; OSHA 29 CFR 1910.179-2016).

Why does a load hanging from a hook resist precise placement?​

A suspended load is a pendulum, and the crane moves its pivot. Siemens' operating instructions for its drive-based sway control state the problem: every movement of a crane trolley makes the load sway, which makes positioning harder and slower, by an amount that depends on the operator's experience. The same manual gives the oscillation model the package uses, f = (1/2π) · √(g / L), where f is the sway frequency, g is 9.81 m/s², and L is the effective pendulum length.

The model has two practical consequences:

  • Long hook drops swing slowly. The period is T = 2π · √(L / g). For illustration, it is about 3.5 s at an assumed effective length of 3 m and 6.9 s at 12 m.
  • Load weight does not appear. A light fixture and a heavy casting on the same effective length swing at the same period.

A 1992 NIST paper on a six-cable research crane compares it with conventional cranes, which, the authors write, cannot stabilize loads in rotation or sway. Under ideal conditions a highly skilled operator can provide some measure of oscillation damping; for precise orientation, however, a crew of riggers is needed to stabilize the load by hand and guide it into its final position. Even expert operators cannot prevent perturbations such as wind from swaying the load, in some cases by more than a meter, and existing cranes have no means of controlling forces or torques on the load. A 2003 review of crane dynamics and control classifies the crane models and control strategies in the literature and discusses their applications and limitations (Siemens 2015, Sway Control V1.0 SP1, §2.1 and §6.1.3.4; Albus et al. 1992, §4; Abdel-Rahman et al. 2003).

How does drive-based anti-sway control damp load sway, and what can it not see?​

Drive-based anti-sway works inside the travel drive, not on the load. In the Siemens V1.0 SP1 package, travel speed is still specified during manual travel, for example by a master controller; the package reads the output of the drive's ramp-function generator and adds a speed value ahead of the speed controller, and the manual states that little or no load sway remains after the axis stops. ABB's crane control program describes an open-loop version for indoor cranes that adjusts the operator's speed reference and works without any additional anti-sway sensors.

Both manuals state limits. The Siemens package needs:

  • orthogonal trolley and gantry axes;
  • a linear relationship between drive speed and axis velocity;
  • a drive whose actual speed follows its setpoint sufficiently well;
  • a hoist encoder, so the pendulum length is known, with a travel-axis encoder recommended;
  • load behavior that roughly matches the sway model, with no mechanical sway-control system such as separate cable tensioning.

Because the Siemens package has no camera, it cannot detect sway that exists before travel starts, sway from a collision, wind, or an asymmetrical load, or sway from oblique hoisting. ABB likewise states that its function cannot compensate for wind, indirect lifting, or wrong settings made at start-up. With sway control active, the path from a stop command to standstill gets longer, and an adapted velocity profile must be used instead of the fastest possible braking.

Capability also depends on the version. The SP1 manual states that target positions and position-controlled travel are not possible; Siemens' 2018 overview of V1.0 SP2 lists, for its Basic Control package, a positioning mode alongside manual mode, with sway damping in positioning, switchover between the two modes, and target changes on the fly. On a large bridge crane at Georgia Tech, operators driving the crane through obstacle courses performed manipulation tasks faster and more safely when input shaping was used to reduce payload sway (Siemens 2015, Sway Control V1.0 SP1, §2.2, §2.4, and §4.3; Siemens 2018, Sway Control V1.0 SP2, p. 5; ABB 2020, 3AXD50000027678 Rev E, pp. 128–131; Khalid et al. 2006).

How does a below-the-hook device change the sway model and the lift?​

The pendulum that swings is the rope plus everything hung from the hook, so the below-the-hook device is part of the sway model. ABB's firmware manual defines the total pendulum arm length as the rope length plus an offset: the distance between the hook and the center of gravity of the lifted object. The offset can vary for different load types, and the manual states that anti-sway accuracy is as good as the known real pendulum arm length. The offset can be supplied as one of three step values selected by digital inputs, a parameter pointer, or hoist load, as a linear offset set against hoist load where load weight correlates with load shape, directly from a fieldbus or analog input, or automatically for loads always lifted from the same floor level; in some cases a device fixed permanently to the hook, such as a lifting magnet, needs no separate offset.

A short illustration shows why this matters. Assume 4 m of rope below the drum and a spreader-and-fixture arrangement that puts the load's center of gravity 2 m below the hook. The effective length is 6 m and the sway period is about 4.9 s, against about 4.0 s for the rope alone, so a controller set up for the empty hook works from a period about 18 percent too short.

The device also carries its own rules. ASME B30.20-2025 is the safety standard for below-the-hook lifting devices and ASME BTH-1-2023 is their design standard. DOE-STD-1090-2020 calls for below-the-hook devices to be designed, constructed, installed, inspected, tested, operated, and maintained in conformance with both, subject to the additions and exceptions in its below-the-hook section. It also states that rated-load markings are required. Where a device cannot be marked with its rated capacity and weight, for example because of the load's security classification or for other reasons the responsible manager approves, it is marked with an identification number and its documentation describes both. In engineering terms, the failure mode is an anti-sway system commissioned with an empty hook and then run with a tall fixture and no offset set for it, which leaves the controller working from the wrong pendulum (ABB 2020, 3AXD50000027678 Rev E, pp. 128–131; Siemens 2015, Sway Control V1.0 SP1, §2.4; ASME B30.20-2025; ASME BTH-1-2023; DOE-STD-1090-2020, §12.1–12.2).

How much fine-motion control does a precision lift need?​

Enough to move a load that is not yet free. NASA-STD-8719.9C sets conditions for using an overhead crane to load-test slings, platforms, or lifting fixtures, or to relieve part of the weight of a constrained load, among them:

  • the crane is specifically identified and documented for that use and approved by the Center's Lifting Devices and Equipment Manager;
  • a load measuring device is installed in the lifting assembly;
  • the total measured load stays at or below 50 percent of the crane's rated capacity when the crane load-tests an item above its periodic test value, pulls against an object heavier than the test load, or relieves part of a constrained load's weight;
  • when the crane pulls against an object heavier than the test load, or relieves part or all of a constrained load's weight, the crane or lifting assembly, for example a load positioning device, has enough fine-motion capability to control the load precisely and avoid overloading the crane or damaging the item.

NASA writes that fine-motion condition for a load test that pulls against a heavier object and for relieving a constrained load's weight. UTEC Industrial's engineering reading extends it to precision lifts of constrained loads generally: a part attached to a cart, pinned into a fixture, or entering a close-tolerance fit resists the hook, and extra hook travel becomes force in the load rather than motion. On the crane itself, fine motion comes from the drives. Rockwell Automation's reference manual for its 750-series drives describes a lifting and torque-proving feature of one drive model in the series and lists micro positioning among its functions both with and without an encoder, while float, holding full torque at zero speed, needs the encoder. How those functions hold and inch a suspended optic is described in Sub-Millimeter Positioning in Segmented-Mirror Handling Systems.

By engineering reasoning, fine motion belongs on every motion that closes the final gap: a crane with a fine hoist but coarse bridge and trolley drives leaves the final horizontal approach to riggers, the dependence the NIST paper describes for precise orientation. ASME HST-4-2021 has a section on hoist and trolley speeds; writing the slow end of each motion into the specification as well is engineering reasoning, not an HST-4 statement (NASA-STD-8719.9C, 2024, §5.5.2.1; Rockwell Automation 750-RM100D-EN-P, 2025, Ch. 5, pp. 151–152; ASME HST-4-2021; Albus et al. 1992, §4).

What should the hoist drive prove before it releases the brake?​

A precision hoist hands the load between brake and motor at every start and stop, and the drive can check each hand-off. ABB's crane control program describes these functions:

  • Torque proving. The drive applies a torque reference against the closed mechanical brake; if actual torque reaches that reference, the drive lets the brake open. Unsuccessful torque proving trips the drive. The function is mainly for hoists, but it can run on other motions that have encoder feedback.
  • Brake slip check. During torque proving, if motor speed exceeds a set limit for longer than a set delay, the brake is slipping and the drive trips.
  • Speed matching. The drive compares its speed reference with actual motor speed continuously, with one deviation level for acceleration and deceleration and another for constant speed, and checks that the brake does not slip at standstill.
  • Brake matching. Using the motor encoder, the drive detects brake slip and downward load movement after a stop command.
  • Smooth lifting. After each lowering operation, or on the first lift, the drive monitors the hoist load; if load is detected, it bypasses the speed reference and ramps the speed down. The manual's example is loose rope being tightened before the load is lifted, and it states that the sudden mechanical stress at the moment of lifting can be reduced.
  • Slowdown and fast stop. Slowdown limits the speed reference while the crane operates in a slowdown area, which the manual's figure places ahead of the end-limit zone. Fast stop stops the drive extremely fast from high speed, and the manual states that it is not an emergency stop function.

Rockwell Automation's manual states that the encoderless version of its torque-proving feature must be limited to lifting applications where personal safety is not a concern, and that encoders must be used where it is. NASA's critical-lift brake rule, which accepts one holding brake only in combination with a motor drive that automatically monitors brake function and motor torque, is covered with the other critical-lift crane rules in Handling Airframe, Engine, and Spacecraft Assemblies. In engineering terms, the failure mode is pickup shock, the sudden mechanical stress at the moment of lifting that ABB's smooth-lifting function addresses (ABB 2020, 3AXD50000027678 Rev E, pp. 84–86, 103–106, and 124–125; Rockwell Automation 750-RM100D-EN-P, 2025, Ch. 5, p. 160).

What do NASA's crane incident lessons show about single operator errors?​

Two Jet Propulsion Laboratory lessons from the Mars Science Laboratory program describe crane lifts of flight hardware that went wrong.

In the backshell incident of May 2011, a load-positioning device had lowered the hook until the slings went slack and the load cell read zero. The operator repeated the command "down slow" but drove the crane up, and lifted the flight backshell while it was still attached to its cart. The load cell peaked at 4,400 lb and two cart legs appeared to lift slightly off the floor; analysis and inspection found no damage. The lesson attributes it to the wrong button pressed on the crane controller, and standard crane operation, as specified in the JPL system-safety standard it cites, gave no clear mechanism for avoiding hardware damage from that type of operator error. Possible contributing causes, not found directly correlated with the event, were the lack of a physical separator between the up and down buttons and the operator's lesser experience on that crane. The lesson: lift operations can be vulnerable to single mistakes by crane operators.

In the mobility-assembly mishap of January 2010, an overhead-crane lift of the rover's aft rocker off its ground-support cart met an undetected interference between a latch-pin nut and the mechanical ground support equipment. The load cell rose to more than twice nominal, about 330 lb, before the nut sheared and the reading fell to 150 lb. The expected maximum reading had not been calculated or communicated beforehand. The lesson concludes that neither drawings nor earlier tests can be relied on to find interferences. It recommends a procedure step that records the expected load-cell reading, a pre-lift briefing that states that maximum and any close approaches, a fit or rotation check before engaging critical hardware, and someone assigned to watch the load cell and call out readings throughout the lift.

Both loads were constrained when the hook moved, the case that engineering reading covers. In both, the load cell registered the abnormal load, and the call to stop came from people on the lift team (NASA JPL 2011, LLIS Lesson No. 5796; NASA JPL 2011, LLIS Lesson No. 6216; NASA-STD-8719.9C, 2024, §5.5.2.1).

Where does a load-positioning device fit between the hook and the load?​

NASA-STD-8719.9C defines a load positioning device as an instrument installed between the hook and the load to allow precise control of lifting operations. The backshell lesson's recommendations, made by JPL Safety and JPL's assembly, test, and launch operations mechanical team, set a margin. When releasing a load, use the positioning device to establish enough slack for the rigging to be disconnected, or for 3 to 5 seconds of movement at the crane's highest speed in the wrong direction; when mating or raising a load, use it beyond the point where 3 to 5 seconds of movement is available at that speed. The lesson states that this gives enough time to execute an emergency stop. Where no positioning device is available or its function is lost, the lift lead should use limited movements or "bump" commands. A further recommendation is that an unencumbered person be available to monitor the load cell during lifts.

The 3-to-5-second option ties the device's stroke to the crane's top speed: by simple arithmetic, doubling the crane's highest speed doubles the travel required, so a fast production crane borrowed for a precision lift needs more stroke, not less.

NASA's standard proof-tests a load positioning device by holding a mock load of 1.20 to 1.25 times rated capacity, or as the designer recommends with the concurrence of the Center's Lifting Devices and Equipment Manager, and its periodic test uses 0.95 to 1.00 times rated capacity. DOE-STD-1090-2020 includes precision load positioners in its rigging-hardware section and calls for them to be inspected, operated, maintained, calibrated, and tested per the manufacturer's instructions. Fail-safe valves for pneumatic devices are covered in the aerospace assemblies article linked above. The device's length and weight also hang below the hook, so they add to both the hook load and the pendulum offset described earlier (NASA-STD-8719.9C, 2024, §3.2, §13.3.2.6, and §13.3.3.2; NASA JPL 2011, LLIS Lesson No. 5796; DOE-STD-1090-2020, §11.1 and §11.3).

How does critical-lift practice change what is asked of the crane?​

Critical-lift rules are written for people and paperwork, but several of them land on the crane. DOE-STD-1090-2020, which is not mandated for use at DOE sites and may be used as a contract document or a best-practice guide at the site's or program office's discretion, sets out the practice:

  • Planning basis. The standard's ordinary-lift section says lift planning should comply with ASME P30.1, and ASME's scope line for the 2024 edition divides that guidance into two categories, a Standard Lift Plan and a Critical Lift Plan.
  • Classification first. A management representative classifies the lift before it is planned. The DOE conditions that make a lift critical are set out with the turnover case in Rollover and Turnover Fixtures for Large, Heavy Assemblies; sites may add criteria such as loads needing exceptional care because of close-tolerance installation.
  • Rigging proof. All rigging used in critical lifts, including below-the-hook devices, is proof-load tested per the applicable ASME standards.
  • Approval and verification. Procedure and rigging sketches are reviewed and approved by the lift director, a qualified person, and the responsible manager before the lift; a pre-lift meeting reviews the plan; and a qualified person verifies the as-installed rigging against the approved plan.
  • Practice lift. Where the procedure requires one, a practice lift is done first. Its conditions should closely simulate weight, rigging, and load path, it should use the same crew and equipment, and the crane should be operated through its full range of motion before the lift.
  • Multi-use plans. Multi-use plans should be used for recurrent critical lifts, but the plan must be revised and approved if the lifting equipment or rigging must change.

Critical-lift criteria and plan contents for outage lifts are set out in Outage Handling in Thermal and Nuclear Power Plants. The next two points are engineering reasoning, not statements from these documents. The practice lift is where the crane's fine-motion and sway functions can be exercised under conditions that simulate the lift. Swapping the below-the-hook device on a multi-use plan changes both the approved rigging and the pendulum offset the drive was set up for, so the plan revision and the drive setting belong on one checklist (DOE-STD-1090-2020, §1.3.1, §2.1.1–2.1.3, §2.2.5, and §2.2.8–2.2.12; ASME P30.1-2024; ABB 2020, 3AXD50000027678 Rev E, p. 129).

What sensing and controls does a precision overhead crane need?​

The four functions depend on sensing that a basic pendant-controlled crane may not carry:

  • Hoist encoder. Sway control needs hoist position for the pendulum length. Siemens warns that a sudden change in that length, from a failed hoist encoder or loose wiring, can cause unpredictable crane-axis movements, to be answered with measures such as an emergency stop.
  • Motor and travel encoders. Brake matching works only with a motor encoder, and for sway control a travel-axis encoder is not necessary but is recommended to improve performance.
  • Load measuring device. NASA defines it as a below-the-hook device, such as a load cell or dynamometer, that indicates the weight being lifted. Tying a control threshold to the expected reading that the mobility-assembly lesson asks procedures to record is an engineering extension of that lesson, not its recommendation.
  • Slowdown areas. By engineering reasoning, slowdown areas ahead of the end limits need room for the longer stopping path that Siemens states for sway-controlled stops.
  • Fail-safe control. NASA recommends that no single failure drive a critical-lift crane faster than commanded or in the wrong direction; its note accepts a failure that stops the crane and sets the brakes, or slows it without disabling the stop.
  • Drive-integrated safe motion. Siemens' safety manual for its drive platform states that its drive-integrated safety functions conform to SIL 2, Category 3, and PL d, and that they correspond to the functions defined in EN 61800-5-2, where that standard defines them; this article cites the IEC edition, IEC 61800-5-2:2016. Safely limited speed caps motor speed, and safely limited position monitors two travel ranges, selected by a safe signal, with a stop response when the axis leaves its range.

UTEC Industrial is a Rockwell Automation Recognized System Integrator, and its controls work covers Allen-Bradley ControlLogix and CompactLogix PLCs, VFD and servo drives, EtherNet/IP networks, and UL 508A panel building (Siemens 2015, Sway Control V1.0 SP1, §2.4 and Ch. 6; ABB 2020, 3AXD50000027678 Rev E, pp. 86 and 103; NASA-STD-8719.9C, 2024, §3.2 and §5.2.3.9; Siemens 2020, 6SL3097-5AR00-0BP3, §3.1, §4.2.7, and §4.3.2; IEC 61800-5-2:2016; NASA JPL 2011, LLIS Lesson No. 6216).

How are sway control, drive functions, and load tests verified at commissioning?​

Pendulum length. The Siemens procedure measures the pendulum at two hook heights: the axis is moved to produce sway, more than five oscillations are timed, and the time divided by the count gives the period T. The effective length is L = g · T² / (4π²), and the two lengths with their hoist positions set the package's slope and offset. For example, if ten swings take 58.0 s at the low hook position, T = 5.80 s and L ≈ 8.36 m. If ten swings take 32.0 s at the high position, T = 3.20 s and L ≈ 2.54 m. Those times are illustrative, not measurements. ABB's instructions likewise measure the pendulum arm with an empty hook, then determine the load offset.

Damping. The Siemens damping factor has a setting range of 0.3 to 1.1. A higher value is recommended where low residual sway matters, and the factor is optimized during commissioning.

Drive functions. Rockwell Automation's configuration check for torque proving checks brake control, then runs the crane up and down without the load and then with it, adjusting acceleration and deceleration times if needed.

Load tests.

  • DOE-STD-1090-2020 calls for new, reinstalled, altered, repaired, and modified cranes to be load-tested before initial use.
  • NASA-STD-8719.9C proof-tests cranes with a mock load of 1.20 to 1.25 times rated capacity, after installation at the site, holding the load long enough to verify no drift occurs.
  • NAVFAC P-307 sets a nominal 125 percent test load for Navy cranes other than the mobile, boom-type, and other listed types it sets lower, within +0/−5 percent, using test weights, not dynamometers. It does not authorize test loads outside those limits except where it lists an exception, and a crane that OEM restrictions or its design keep from the specified overload test is down-rated to 80 percent of the OEM's allowable test load, 90 percent for third-party certified mobile, articulating-boom, and other telescoping-boom cranes, and then tested to P-307's requirements.
  • Reclamation's rules for powerhouse cranes are in Powerhouse Crane and Gate-Hoist Duty Cycle Requirements.

UTEC Industrial performs factory acceptance testing and on-site commissioning, so drive checks and interlocks can be demonstrated before the first critical lift (Siemens 2015, Sway Control V1.0 SP1, §4.6 and §6.1.3.4; ABB 2020, 3AXD50000027678 Rev E, pp. 136–139; Rockwell Automation 750-RM100D-EN-P, 2025, Ch. 5, p. 160; DOE-STD-1090-2020, §6.2; NASA-STD-8719.9C, 2024, §5.3.1.1–5.3.1.2.1; NAVFAC P-307, 2025, §4.7.1–4.7.1.1).

Where does a precision crane sit in the design-to-monitoring chain?​

Every link of the chain shapes how finely the hook can be controlled:

  • Design and engineering decide which motions need fine control and sway functions, and what offset each below-the-hook device brings.
  • Parts machining produces the drum, sheaves, wheels, and bearing seats. The reeving, the rope parts between drum and hook block, sets how drum rotation becomes hook motion, and its sheaves have to run true.
  • Fabrication and weld fatigue decide whether girders, trolley frames, and lifting beams survive a load cycle on every lift.
  • Stress relief keeps machined bearing seats and wheel bores where they were machined, as explained in Stress Relief for Machine Bases and Frames Before Final Machining.
  • Drives and controls deliver torque proving, brake-slip checks, smooth pickup, sway damping, and safe speed and position limits.
  • Tuning sets pendulum length, offset, and damping on the real crane with the real devices.
  • Monitoring keeps the record: DOE-STD-1090-2020 requires a preventive maintenance program based on the crane manufacturer's recommendations and the referenced ASME standards, and says the crane's maintenance history should be retained throughout its service life, and ABB's speed-matching and brake-slip functions raise faults, or a warning at standstill, when the motor does not follow its speed reference or the brake slips; keeping those events in the maintenance record is engineering reasoning.

UTEC Industrial stress-relieves welded structures, including by automated vibratory stress relief, and inspects with NDT and CMM. By engineering reasoning, the chain view also applies to an anti-sway retrofit. The Siemens requirements themselves settle the check: if the drive's actual speed does not follow its setpoint sufficiently well, or the hoist has no encoder, they are not met, and the manual names a growing speed deviation as a cause of poor sway-control quality (Siemens 2015, Sway Control V1.0 SP1, §2.4; ABB 2020, 3AXD50000027678 Rev E, pp. 84–86 and 105–106; DOE-STD-1090-2020, §6.3).

What should a precision-lift crane specification define?​

A specification written as a capacity, a span, and a lift leaves out every function above. A complete one defines:

  • Class and standards: crane type, hoist duty service class, lift, headroom and speeds, and the CMAA design basis.
  • Loads and devices: the heaviest and lightest loads, and for each below-the-hook device its weight, rated-load marking, and hook-to-center-of-gravity offset.
  • Fine motion: the slow end of hoist, trolley, and bridge travel as written requirements, and whether the crane will be used on constrained loads.
  • Sway control: manual-only damping or positioning mode, the required encoders, and the disturbances it will not cover, such as wind, indirect lifting, and oblique hoisting.
  • Drive functions: torque proving, brake-slip and speed-matching checks, smooth pickup, and fast stop kept separate from the emergency stop.
  • Critical-lift support: a load measuring device, logic built around the expected reading, and positioning-device stroke sized to the crane's top speed.
  • Safety: single-failure behavior, safe speed and position limits, and pendant layout.
  • Verification: pendulum calibration, damping tuning, loaded and unloaded runs, and the load test.

Each item should name its owner, the crane builder, the controls integrator, or the device designer, so nothing is left for the day of the lift (ASME B30.2-2022; ASME B30.17-2026; ASME B30.16-2022; ASME HST-4-2021; CMAA Specification No. 70-2025; CMAA Specification No. 74-2025; ASME B30.20-2025; ASME BTH-1-2023; ASME P30.1-2024; NASA-STD-8719.9C, 2024, §5.2.3.9 and §5.5.2.1).

Related Articles

References​

  • ASME B30.2-2022: Overhead and Gantry Cranes (Top Running Bridge, Single or Multiple Girder, Top Running Trolley Hoist). ASME, 2022.
  • ASME B30.17-2026: Cranes and Monorails (With Underhung Trolley or Bridge). ASME, 2026.
  • ASME B30.16-2022: Overhead Underhung and Stationary Hoists. ASME, 2022.
  • ASME HST-4-2021: Performance Standard for Overhead Electric Wire Rope Hoists. ASME, 2021.
  • CMAA Specification No. 70-2025: Specifications for Top Running Bridge and Gantry Type Multiple Girder Electric Overhead Traveling Cranes. CMAA, 2025.
  • CMAA Specification No. 74-2025: Specifications for Top Running and Under Running Single Girder Electric Traveling Cranes Utilizing Under Running Trolley Hoist. Crane Manufacturers Association of America/MHI, 2025.
  • AIST Technical Report No. 6-2018: Specification for Electric Overhead Traveling Cranes for Steel Mill Service. Association for Iron and Steel Technology, 2018.
  • ASME NOG-1-2025: Rules for Construction of Overhead and Gantry Cranes (Top Running Bridge, Multiple Girder). ASME, 2025.
  • OSHA 29 CFR 1910.179-2016: Overhead and Gantry Cranes. U.S. Department of Labor, 2016.
  • Siemens AG. SIMOCRANE Drive-Based Sway Control Operating Instructions, V1.0 SP1, edition 11/2015. Siemens AG, 2015.
  • Siemens AG. SIMOCRANE Drive-Based Sway Control V1.0 SP2. Siemens AG, 2018.
  • ABB. ACS880 Crane Control Program (Option +N5050) Firmware Manual, 3AXD50000027678 Rev E. ABB, 2020.
  • Albus, J., Bostelman, R., Dagalakis, N. (1992). "The NIST SPIDER, A Robot Crane." Journal of Research of the National Institute of Standards and Technology, 97(3), 373-385.
  • Abdel-Rahman, E.M., Nayfeh, A.H., Masoud, Z.N. (2003). "Dynamics and Control of Cranes: A Review." Journal of Vibration and Control, 9(7), 863-908.
  • Khalid, A., Huey, J., Singhose, W., Lawrence, J., Frakes, D. (2006). "Human Operator Performance Testing Using an Input-Shaped Bridge Crane." Journal of Dynamic Systems, Measurement, and Control, 128(4), 835-841.
  • ASME B30.20-2025: Below-the-Hook Lifting Devices. ASME, 2025.
  • ASME BTH-1-2023: Design of Below-the-Hook Lifting Devices. ASME, 2023.
  • DOE-STD-1090-2020: Hoisting and Rigging. U.S. Department of Energy, 2020.
  • NASA-STD-8719.9C: Lifting Standard. National Aeronautics and Space Administration, 2024.
  • Rockwell Automation. PowerFlex 750-Series Products with TotalFORCE Control Reference Manual, 750-RM100D-EN-P. Rockwell Automation, 2025.
  • NASA Jet Propulsion Laboratory. MSL Backshell Crane Incident, Lesson No. 5796. NASA Lessons Learned Information System, 2011.
  • NASA Jet Propulsion Laboratory. MSL Mobility Assembly Lift Mishap, Lesson No. 6216. NASA Lessons Learned Information System, 2011.
  • ASME P30.1-2024: Planning for Load Handling Activities. ASME, 2024.
  • NAVFAC P-307: Weight Handling Program Management. Naval Facilities Engineering Systems Command, 2025.
  • Siemens 6SL3097-5AR00-0BP3: SINAMICS S120 Safety Integrated Function Manual, Edition 06/2020. Siemens AG, 2020.
  • IEC 61800-5-2:2016: Adjustable speed electrical power drive systems — Part 5-2: Safety requirements — Functional. International Electrotechnical Commission, 2016.

Ready to Discuss a Material Handling System?​

UTEC Industrial designs, engineers, machines, fabricates, and installs custom material handling systems for heavy industry, from the stress-relieved structure and drives to the Allen-Bradley PLC controls, tuning, and monitoring that run them, at its Spokane Valley, WA facility. Send UTEC the application, loads, and duty cycle to start a system review.

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Questions? Call (509) 922-1832 or email sales@utec.co

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