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F二 mrω2 (4-7)
Since the force must not exceed 10% of the static journalload，
mr二 0.ω12 W (4-8)
d
Taking the correction constants， the equation can be written
56， 347 x Journal static weightload
Max. unbalanced force二(rpm)2 (4-9)
The double amplitude of unfiltered vibration in any plane measured on the shaft adjacent to each radial bearing is not to exceed 2.0 mils (0.05 mm) or the value given by
 
12，000
Amplitude二 rpm(4-10)
where rpm is the maximum continuous speed. It is more meaningful for gearsto be instrumented using accelerometers. Design specifications for bearings，seals， and lubrication are also given.
Accessories such as couplings， couplingguards， mountingplates，piping，instrumentation， and controls are described. Inspection and testing pro-cedures are detailed. The purchaser is allowed to inspect the equipment during manufacture after notifying the vendor. All welds in rotating partsmust receive 100% inspection. To conduct a mechanical run test， the unit must be operated at maximum continuous speed until bearing and lube oil temperatures have stabilized. Then the speed is increased to 110% of max-imum continuous speed and run for four hours.
Lubrication Systems
This API Standard 614 standard covers the minimum requirements forlubricationsystems， oil shaft sealingsystems， and related control systems forspecial purpose applications. The terms are fully defined， references are well documented and basic design is described. Details of the lubrication system are presented in chapter 15.
Lubrication systems should be designed to meet continuously all condi-tions for a nonstop operation of three years. Typical lubricants should be hydrocarbon oils with approximate viscosities of 150 SUS at 100 oF (37.8 oc). Oil reservoirs should be sealed to prevent the entrance of dirt and water and sloped at the bottom to facilitate drainage. The reservoir working capacity should be sufficient for at least a five minute flow. A typical reservoir is shown in Figure 4-8. The oil system should include a main oil pump and a standby oil pump. Each pump must have its own driver sized according to API Standard 610. Pump capacities should be based on thesystems. maximum usage plus a minimum of 15%. For seal oil systems， thepump capacity should be maximum capacity plus 20% or 10 gpm， whichever is greater. The standby oil pump should have an automatic startup control to maintain safe operation if the main pump fails. Twin oil coolers should beprovided， and each should be sized to accommodate the total cooling load. Full-flow twin oil filters should be furnished downstream of the coolers. Filtration should be 10 microns nominal. The pressure drop for clean filters should not exceed 5 psi (0.34 Bar) at 100 oF (37.8 oc) operating temperature during normal flow.

Overheadtanks， purifiers， and degasing drums are covered. All pipewelding is to be done according to Section I. of the ASME code， and all piping must be seamlesscarbon steel， minimum schedule 80 for sizes 112inches (38.1 mm) and smaller， and a minimum of schedule 40 for pipe sizes 2 inches (50.8 mm) or greater.
The lubrication control system should enable orderlystartup， stableoperation， warning of abnormal conditions， and shutdown of main equip-ment in the event of impending damage. A list of required alarm and shut-down devices is provided. Figure 4-9 is a schematic of a seal lube and control oil system. The purchaser has the right to inspect the work and testing of subcomponents if he informs the vendor in advance.Eachcooler，filter，accumulator， and other pressure vessels should be hydrostatically tested at one and one-half times design pressure. cooling water jackets and other water-handling components should be tested at one and one-half times design pressure. The test pressure should not be less than 115 psig (7.9 Bar). Tests should be maintained for durations of at least 30 minutes.
Operational tests should:
　
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