How to Specify a 1,200-Ton Press Brake Production Cell
Last month, I walked into a heavy-fabrication facility where a newly delivered 1,200-ton press brake was already underperforming. The plant…
Walk into any heavy fabrication shop that has just secured a major defense or infrastructure contract, and you will see it: a monolithic, custom-painted press brake dominating the floor. The plant manager will pat the side of the 3,000-ton frame and say it can handle “whatever comes through the door.”
It sounds like smart capital planning. Buy the biggest hammer, and you never have to turn down a nail. But watch that same machine bend a standard half-inch plate, and you will see the operator fighting the crowning system just to maintain a three-degree tolerance across the part’s length.
That massive frame is not a safety net. It is an anchor.
A 10-foot piece of 1-inch Hardox 450 requires a vastly different force profile than a 20-foot piece of half-inch A36 mild steel. Yet when engineers assess risk, they tend to compress all of these variables—V-die opening, bend length, material thickness, and tensile strength—into one brute-force metric: maximum machine tonnage. The logic is tempting. If the worst-case scenario requires 1,500 tons, buying 2,000 tons gives you a 25% safety margin.
But press brake tonnage is not an independent buffer. A machine frame is essentially a giant spring. It is built to deflect under load, and its automated crowning system is calibrated to compensate for that particular deflection curve. When you put a 200-ton load on a 2,000-ton frame, the bed does not deflect enough to bring the crowning system into its sweet spot. You end up chasing angle variation along the length of the bend because the machine is too rigid to feel the work. You bought a safety margin for capacity, but you gave up your margin of error for precision.
Bidding on a bridge infrastructure project means reviewing blueprints with 2-inch-thick gussets and 30-foot spans. The procurement team looks at the current shop floor, sees a 750-ton brake, and panics. The fear of turning down a lucrative, multi-million-dollar contract because of equipment limitations is a powerful motivator. It is true that the opportunity cost of passing on a massive job can sometimes exceed the cost of idle steel. This real option value persuades smart people to write seven-figure purchase orders for capacity they may need only twice a year.
This fear overlooks the hidden math of heavy equipment installation. A massive press brake requires a massive foundation—often hundreds of thousands of dollars in pit excavation, soil stabilization, and reinforced concrete alone. It also requires higher-amperage electrical drops, specialized rigging, and custom heavy-duty tooling that costs three times as much as standard V-dies. The capital hemorrhage does not end with the invoice price. It seeps into your overhead, raising the hourly shop rate for every job that moves through the building and making you less competitive on the standard work that actually keeps the lights on.
Review a year’s worth of production logs from a typical heavy fabrication shop. You will usually see a harsh Pareto distribution: 95% of bends involve standard plate thicknesses under one inch, while only 5% move into extreme heavy-plate work.
When you buy one monolithic press brake to handle that top 5%, you make the other 95% subsidize it. Operators spend extra time using overhead cranes to set up massive tools for relatively simple jobs. Cycle times slow because the ram speeds on a 3,000-ton machine are inherently sluggish compared with a nimble 500-ton unit. The psychological comfort of knowing you could bend a battleship hull blinds you to the reality that you are actually bending tractor frames, and doing so less profitably than before. You have not future-proofed the business. You have built a monument to a theoretical order book while handicapping the real one.
The standard bending force formula—P = 1.42 × σ_b × S² × L / V—exposes a harsh mathematical reality that undermines the “bigger is better” equipment strategy. Because material thickness (S) is squared while tensile strength (σ_b) is linear, a mere 0.1 mm thickness fluctuation on a standard 2 mm plate can increase tonnage demand faster than moving from 60-ksi mild steel to 100-ksi high-strength steel.
Engineers often look at blueprints for heavy structural jobs and immediately specify a massive machine as a catch-all buffer. They treat tonnage as a raw commodity to stockpile rather than as a precise force to calculate. Run the numbers on a standard 10-foot bend of 0.5-inch plate over a 4-inch V-die: if you are bending standard A36 mild steel (60 ksi), the formula calls for roughly 153 tons of force. Replace that exact same 10-foot, half-inch plate with Advanced High-Strength Steel (AHSS) at 120 ksi, and the requirement immediately doubles to 306 tons. When you buy a 3,000-ton brake without mapping the exact multiplier effect of your specific material grades and die openings, you are not engineering a solution. You are guessing with a million-dollar budget. How do you calculate a machine’s true limit when the variables keep shifting beneath your tooling?
Peak tonnage in air bending does not occur when the punch first contacts the metal. It occurs at approximately 60 degrees into the external bend angle. Operators and procurement teams that size machine capacity based on initial penetration force systematically underestimate the true peak load of their daily work. To compensate for this blind spot, they oversize the machine, using excess capital to cover a hidden load profile instead of engineering around it.
Bending methods distort this math further. Coining, or full-depth forming, requires three to five times the tonnage of air bending for the exact same material and thickness. Yet many procurement specifications group all bending operations under a single inflated tonnage requirement. This creates massive oversizing for shops that primarily air bend, forcing them to pay for coining-level forces they will never use. If the bending method and angle dynamics quietly determine the peak load, what happens when the metal itself changes the rules?
Standard air-bending force charts posted on shop walls across the country assume a 60,000-psi tensile strength baseline for mild steel. Modern automotive and structural grades routinely range from 80,000 to 120,000 psi. These legacy charts do not scale linearly. Using a massive press brake rated for mild steel on advanced high-strength steels (AHSS) without recalculating the specific V-die ratio creates a false capacity ceiling.
You might assume your 2,500-ton machine gives you the freedom to bend thicker plate, but with 120-ksi steel, your effective working limit drops sharply. You are not truly increasing your thickness capacity; you are simply consuming your machine’s rated tonnage to overcome the yield strength of today’s steel mix. Buying more raw tonnage to solve a material-grade problem is an expensive stopgap that ignores the physics of the die opening. Once you account for the tensile strength of the material you are actually bending, what is the single biggest multiplier that drives up the rest of the capacity calculation?
Workpiece width (L in the formula) is a direct, linear multiplier. Doubling the bend length from 10 feet to 20 feet immediately doubles the force requirement. Buyers focus heavily on material thickness and V-die openings, treating width as a secondary variable that only determines the physical length of the machine bed. This leads to the most common and catastrophic capital mistake in heavy fabrication: buying a 40-foot, 4,000-ton monolithic brake simply because the shop occasionally bends 40-foot plates.
When an operator places a standard 10-foot part in the center of that 40-foot bed, they apply a massive, localized force to a frame designed to distribute load across its full span. The machine has the tonnage, but the physics of applying it over a short width causes the ram to bow. The automated crowning system, expecting a full-length load, overcorrects aggressively and ruins the bend angle. You paid millions for a machine that can bend a 40-foot plate, only to find that it cannot accurately bend a 10-foot one. If a monolithic frame physically cannot distribute force efficiently across different part widths, how do you handle extreme jobs without damaging your standard production?
If a single monolithic frame physically cannot distribute force efficiently across varying part widths, the only way to handle extreme jobs without ruining standard production is to abandon the monolith entirely. The mathematical solution is a tandem architecture: linking two or more properly sized machines that can synchronize for a 40-foot plate, then decouple to run standard 10-foot parts independently. But to understand why this fleet approach is mandatory, you first have to measure the exact mechanical penalty of relying on one massive anchor. Manufacturers treat maximum tonnage as a future-proofing safety net. On the shop floor, that safety net becomes a precision tax, systematically reducing the accuracy of every standard part you run through it.
When you center a 4-foot, 1/4-inch plate on a 20-foot, 2,000-ton press brake, the machine barely registers the hydraulic pressure needed to bend it. Yet the physical steel of the ram bows around that small tooling footprint like a bridge under a point load. Application data from manufacturers such as Trumpf confirms that accuracy failures on large presses are rarely force problems; they are geometry problems caused by load location and unsupported bed length.
A press brake is essentially a giant C-frame that behaves like a stiff spring under load. When a massive frame is subjected to a highly concentrated, low-tonnage load at its center, the unsupported ends of the ram and bed do not deflect in the smooth, predictable arc the machine was designed to produce. The heavy steel structure resists the localized pressure unevenly. Instead of a perfectly linear bend, you get microscopic twisting in the frame that transfers directly into the workpiece. You bought a massive anchor to guarantee capability, but its sheer physical size makes it too rigid where it should not be and too flexible exactly where you need it to hold a tight tolerance.
Across the industry, standard press brake accuracy is about +/-0.5 degrees for bend angles and +/-0.1 millimeters for linear positioning. Achieving those baselines on a mega-machine performing standard work is nearly impossible because of how hydraulic and mechanical compensation systems behave below 40% of their rated capacity.
Automated crowning systems are designed to push the center of the lower bed upward to offset the natural downward bowing of the upper ram. These systems calculate their counterforce using a proportional curve tied to the machine’s maximum tonnage. When a 2,000-ton brake runs at 15% capacity, the hydraulic proportional valves are barely opening. They operate outside their optimal resolution band, sending low-pressure data to a crowning system calibrated for major structural deflection. The machine overcompensates aggressively, pushing the center of the bed too high for the actual load being applied. This is the exact mechanical penalty: documented OEM accuracy specifications show that operating a massive frame below 20% capacity routinely introduces an angle variance of +/- 1.5 to 2.5 degrees over a standard 10-foot span—up to five times the acceptable industry tolerance. The result is a canoe-shaped bend: overbent in the middle and underbent at the ends. Brute force does not scale down cleanly; it creates a dynamic tolerance problem that operators have to fight with shims and manual overrides.
Modern light-gauge materials and advanced high-strength steels have substantial springback variability. Two sheets of 14-gauge steel from the same pallet can spring back differently depending on rolling direction and internal stress. Managing this requires finesse—specifically, straight ram alignment, high-resolution encoders, and closed-loop active angle measurement that adjusts punch depth in real time.
A monolithic 4,000-ton frame actively works against these precision controls. The sheer mass and inertia of a 60,000-pound steel ram moving downward cannot deliver the rapid, micro-millimeter responsiveness required for active springback compensation. When a laser sensor detects a 0.2-degree error mid-bend, the massive hydraulic cylinders cannot feather their adjustment precisely enough to correct it without overshooting the target. The machine is simply too heavy to be agile. You cannot force a piece of sheet metal into high-precision compliance through impact alone. If brute force inherently fails on the lighter, standard jobs that make up the bulk of your revenue, you are forced to rethink the architecture of your shop floor entirely.
The mechanical reality that a monolithic frame fails on lighter jobs leaves shop owners with a mathematical requirement: decouple heavy-plate outliers from daily production. Linking two right-sized machines in a synchronized tandem setup lets you combine forces for a 40-foot plate, then separate them to run standard 10-foot parts independently; for shops comparing this architecture in practical terms, ADH Machine Tool’s tandem press brake solution fits into a broader CNC-based bending and sheet metal automation portfolio. But evaluating this fleet approach still requires looking beyond glossy vendor brochures. Tandem machines do not magically eliminate bending physics; they simply trade the structural limitations of a giant steel frame for the digital complexity of software synchronization.
Guidance from bending specialists consistently notes that a single massive frame provides one uninterrupted working area and simpler part handling. If your facility rolls 40-foot, 2-inch-thick steel sections for shipbuilding 24 hours a day, a 5,000-ton monolith is the right tool. In a purely heavy-plate environment, flexibility is irrelevant. A monolithic frame has no center splice point and requires no software interpolation between two separate CNCs.
Tandem setups, by contrast, create a permanent mechanical seam. Application data from manufacturers such as Bystronic shows that running a part across two linked machines requires the workpiece to accommodate a second set of synchronization variables. Two separate hydraulic systems, two crowning profiles, and two sets of ram encoders must match perfectly. If your product mix consists entirely of heavy, long-span work and you never actually decouple the tandem machines for standard jobs, you have not purchased flexibility. You have simply bought a more complex single machine with a permanent weak point in the middle. The tandem calculation only produces a return on investment when your shop floor needs the agility to separate the fleet.
Consider the physical layout of a 12-meter monolithic press brake. The hydraulic cylinders that drive the ram are positioned at the far left and right ends of the machine. When you bend a long part, the ram bows upward in the center and the bed bows downward. The machine’s automatic crowning system must push a massive, continuous steel beam upward to compensate for one broad deflection curve. Product documentation from companies such as Trumpf confirms that large press brakes cannot guarantee straightness across these long spans without heavy active compensation, because controlling a single 40-foot deflection arc with only two push points is mechanically inefficient.
A tandem setup changes this geometry. Two linked 20-foot machines do not have two hydraulic cylinders; they have four. The massive 40-foot deflection curve is divided into two smaller, shallower arcs, each supported by its own set of cylinders and its own localized crowning system. Instead of fighting one large structural bow, the CNC manages two tightly controlled zones. The precision risk shifts from raw mechanical deflection to software synchronization. You are trading a physical impossibility—keeping a 40-foot unsupported beam perfectly straight—for a solvable software equation: synchronizing two Y-axes to within 0.01 millimeters at the splice point. For shops that combine long parts with high-precision requirements, cutting the deflection curve in half is the only way to maintain tight linear tolerances.
Changing a 40-foot run of heavy-duty multi-V dies requires a forklift, two operators, and hours of lost green-light time. On a monolithic machine, every time you switch from a 1-inch plate job to a 1/4-inch standard bracket, you must clear the entire bed. The sheer physical mass of the tooling becomes your main bottleneck. You are paying the capital expenditure for massive tonnage, but losing operating margin to setup time because the machine is constrained by its own tooling requirements.
Tandem architectures let you work around this logistical math. When the machines are decoupled, you can leave the heavy-duty, large-V dies permanently loaded in Machine A for thick plate, while equipping Machine B with precision gooseneck punches and narrow dies for lighter, complex work. You eliminate the constant teardown. The tandem setup isolates the heavy work, keeping the rest of your production moving without forcing operators to move tons of steel just to bend a 10-gauge bracket. But while splitting the machine solves the physics of bending and the logistics of tooling changeovers, it does not eliminate the equipment’s physical footprint. Whether you install one massive anchor or dock a fleet of smaller machines, you still have to alter the ground beneath them.
A 2024 NIST report on industrial maintenance economics highlights a harsh reality: facility managers consistently fail to forecast the true lifecycle and installation costs of massive machinery because they treat infrastructure as a predictable line item. When a vendor quotes a 3,000-ton press brake, that figure covers the steel, the hydraulics, and the CNC. It completely ignores the fact that you cannot simply bolt three million pounds of concentrated force to a standard six-inch concrete shop floor. To prevent the machine from cracking the slab and sinking into the earth under its own operating load, you have to alter the geology of your facility.
Consider the geometry of a mega-machine. To keep a 40-foot lower bed from deflecting under 3,000 tons of pressure, the machine needs a massive lower structural web. That web does not sit above ground; it extends 10 to 15 feet below the floor line. You are not merely pouring a reinforced pad. You are excavating a basement.
Excavating a 15-foot pit inside an existing, operating facility is a logistical nightmare. If your shop sits on a high water table, you are effectively building a waterproof submarine hull just to keep the lower hydraulics dry. If you encounter bedrock at eight feet, your installation timeline has just grown by three months of specialized blasting or core drilling. The machine’s footprint dictates the facility’s architecture, forcing you to permanently anchor your production layout around one immovable trench.
Once the machine is in the ground, the physics of running it create a new recurring penalty. Producing 3,000 tons of force requires moving enormous volumes of hydraulic fluid at high pressure, generating tremendous heat. A standard 200-ton brake might hold 150 gallons of oil and use a simple air-cooled heat exchanger. A 3,000-ton monolith operates on a completely different scale, often requiring reservoirs that hold more than 2,000 gallons.
Moving that much fluid through the manifold creates a thermal load that standard shop air cannot remove. You must install dedicated industrial chillers. In addition, hydraulic oil degrades under repeated high-heat cycles. When a standard machine needs an oil flush, it costs a few hundred dollars and takes an afternoon. When a 2,000-gallon mega-machine needs its scheduled fluid replacement, you are buying oil by the tanker truck and paying for specialized hazardous waste disposal. This is exactly the forecasting trap the NIST data warns about: baseline operating cost scales exponentially, not linearly, with tonnage.
The final hidden multiplier affects your utility infrastructure. A mega-machine requires high-voltage power drops that often exceed the existing capacity of a standard heavy fabrication bay, making new transformers and upgraded switchgear necessary. Add the electrical upgrades to the pit excavation, the custom poured-in-place concrete foundation, and the industrial chillers, and the facility preparation costs routinely equal or exceed the purchase price of the press brake itself.
For teams trying to price those site requirements before committing to a machine class, ADH Machine Tool’s CNC-focused portfolio across press brakes, laser cutting, shearing, grooving, and sheet metal automation makes its technical materials a useful next step: download the specification resources to compare equipment requirements against your available power, foundation, and production envelope.
This infrastructure shock fundamentally changes the machine’s required return on investment. Manufacturing Engineering data shows that Overall Equipment Effectiveness (OEE) collapses when a machine is used below its optimal capacity. If you spend two million dollars on a press brake and another two million dollars modifying your building to house it, that work cell must run heavy-plate, high-margin jobs continuously just to break even on its amortized footprint. When that massive, expensive anchor is forced to bend 1/4-inch brackets because the heavy jobs have dried up, it is not merely wasting tonnage—it is actively damaging your shop’s profitability. Size alone is not the villain, but committing to the permanent infrastructure of a 3,000-ton monolith forces you to calculate the capital delta: the millions spent on foundation and utility upgrades divided by the actual percentage of your order book that requires maximum tonnage.
When you run that capital-delta calculation against a realistic production schedule, the math consistently points away from owning the full capability spectrum and toward a right-sized fleet architecture, where the heavy-fabrication sweet spot falls between 1,500 and 2,500 tons. This range delivers enough brute force to handle serious industrial plate while keeping the physical footprint—and the capital expenditure—anchored in reality. For teams translating that sizing logic into an actual equipment shortlist, ADH Machine Tool’s CNC-based bending capability makes a large press brake a practical bridge between heavy-plate capacity and disciplined investment. But reaching this sweet spot requires giving up the “what if” procurement mindset.
Vendors like to sell you a machine sized for your absolute worst-case scenario. It is a mathematical trap rooted in shop-floor physics. Tonnage scales with the square of material thickness. Doubling your plate thickness from a quarter-inch to a half-inch does not double the required force. It quadruples it.
If 80% of your daily job mix is half-inch mild steel, a 1,500-ton machine can handle that work profitably all day. But if a customer occasionally asks for one-inch plate, the quadratic math suddenly calls for a behemoth. Buying that behemoth means spending twice the capital to capture a tiny fraction of your schedule. Worse, nameplate capacity is misleading. A 2,500-ton machine bending standard mild steel loses a large share of its effective power the moment you switch to stainless, which requires a formability multiplier of up to 1.7. If you size your machine to cover 100% of possible thicknesses and materials, you are buying a machine three tiers larger than your daily median job requires. The 80% coverage rule forces you to map your actual historical job mix and draw a firm line; for shops standardizing around repeatable bending rather than rare extremes, ADH Machine Tool’s CNC press brake solutions fit naturally into that capacity conversation because its portfolio is built around CNC-based bending and sheet metal automation.
You buy the machine that handles the 80% with maximum efficiency, and you let the rest go.
What happens when that 20% outlier job lands on your desk and you only have a 2,000-ton machine? You adjust your physics. Tonnage flexibility comes primarily from your tooling strategy, not from your hydraulic cylinders.
If that trade-off affects how you size your next press brake, it is worth discussing the job mix with a supplier that can support both equipment selection and implementation. ADH Machine Tool backs its press brake offering with international sales and service coverage, making a contact inquiry a practical next step before committing to excess capacity.
The force required to bend plate has a linear inverse relationship with die width. If you widen your V-die opening from four inches to eight inches, you cut the required tonnage exactly in half. Yes, this increases the inside radius of the bend. Yes, it leaves a larger unbent flat on the edge of the plate. But if the customer’s print allows it, a wider die lets a 1,500-ton press brake do the work of a 3,000-ton machine.
When the print is strict, you look at process flexibility. Bending a massive, complex profile in a single pass requires peak tonnage. Breaking that same profile into a multi-pass operation—bumping the material through in smaller increments—drastically lowers the force threshold. It takes more time. It requires more operator handling. But an extra thirty minutes of labor on a rare job is far cheaper than amortizing a multi-million-dollar mega-machine that sits idle waiting for that specific profile.
Eventually, you will encounter a job that tooling tricks cannot solve. A tight-radius channel in thick-gauge high-strength steel requires form tooling, which immediately multiplies the required air-bending force by three. Your 2,000-ton machine simply cannot do it.
This is where shop owners panic.
They hate turning down work. But look at the hard ROI math. If moving from a 2,000-ton sweet-spot machine to a 4,000-ton monolith adds two million dollars in capital and foundation costs, how many extreme-bending jobs would you need to win just to break even on the upgrade? Subcontracting those outlier jobs to a specialized heavy-plate shop cuts into the margin on that specific work. It hurts your pride. But paying a premium to a partner shop once a month is mathematically better than carrying a permanent, seven-figure debt burden for a capability you rarely use. Outsourcing the extremes protects your core profitability. It keeps your floor agile. Most importantly, it frees your capital to invest in the automation and software that make your 80% sweet spot radically more efficient.
You have just drawn a hard line at a 2,000-ton machine to handle the bulk of your heavy plate work. That decision leaves you with a multi-million-dollar pool of capital that was not buried in a foundation pit for a 4,000-ton monolith. The immediate question is where to deploy it. You put those funds directly into the software and automation that make your sweet-spot machine untouchable. A right-sized brake paired with offline programming software, automated tool changers, and laser angle measurement systems will out-produce a bare-bones mega-machine on every metric that matters. Maximum tonnage is a static defense against the unknown. Matched thinking is an active offense, pairing the exact hydraulic force required with the digital agility needed to keep the ram moving.
Vendors sell future-proofing by presenting maximum capacity as a fixed, dependable envelope. Shop-floor physics say otherwise. Look at a standard capacity chart from a manufacturer such as Cincinnati Incorporated. A machine rated to air-bend 21.7 feet of standard material can suddenly fall to a 12.8-foot usable envelope the moment you switch to a material with a higher formability factor. Maximum tonnage is a moving target shaped entirely by material yield strength and the bend method you choose. Buying excess capacity for an undefined future ignores how quickly that capacity disappears when alloy specifications change.
This blind pursuit of tonnage also changes the fundamental geometry of your floor. The standard V-die rule of thumb calls for an opening roughly eight times the material thickness. A 0.125-inch sheet needs a 1-inch die. But a vendor promoting a mega-machine will quickly point out that widening the die reduces the required tonnage, subtly encouraging you to use oversized tooling to justify the oversized ram. This hidden compromise increases your inside bend radius and changes minimum flange lengths. You are no longer just buying unused capacity; you are actively degrading the precision and geometry of your standard parts to accommodate a machine you never needed. Real growth projections map specific upcoming contracts. Vendor upselling maps fear.
There are rare cases where oversizing is prudent insurance rather than vanity. Running a brake at 100% of its rated capacity on every cycle will deform the ram, damage tooling, and create serious safety risks for the operator. You need a mechanical safety margin. But a deliberate 20% buffer to protect the hydraulics is entirely different from buying double the required tonnage just to feel secure.
Capacity planning fails when engineers treat it as a catalog-shopping exercise. It is a capital allocation problem. Every dollar spent on iron that sits idle is a dollar withheld from throughput-enhancing technology. If you match your machine to your median job mix, the capital saved can buy robotic part manipulators for heavy plate, reducing a three-person handling crew to a single operator. It can buy dynamic crowning systems that ensure first-pass accuracy on long bends. You stop paying for theoretical force and start paying for actual velocity.
Vendors like to sell to the top 5% of your order book, presenting massive tonnage as a status symbol of a capable shop. But sound engineering looks past the nameplate and aligns capital expenditure with your actual bending curve. To reach a firm ROI verdict on your next press brake, pause the purchase order and run this three-step capital allocation test:
First, map your 80th-percentile job. Pull your actual production data from the last 36 months, excluding the sales team’s fantasy pipeline. If 80% of your heavy plate work requires 1,500 tons or less over a standard bed, that is your baseline machine requirement.
Second, calculate the infrastructure delta. Price the 15-foot foundation pit, specialized rigging, high-voltage electrical upgrades, and crane capacity required for a 4,000-ton monolith. Compare that with the standard flat-floor installation of a right-sized machine or a tandem setup. That delta is the hidden penalty for overbuying.
Third, run the outsourcing break-even. Take the capital saved from the machine price difference and the infrastructure delta. Calculate how many years of outsourcing the extreme top 20% of your jobs it would take to use up those exact savings. In almost every shop floor audit I conduct, the break-even point extends well beyond the equipment’s depreciation lifecycle.
You do not buy a mega-machine to protect yourself from unknown variables. You buy right-sized or tandem architectures because the math proves they are the only profitable choice. Run the test, protect your margin, and let the numbers make the decision.
