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Static pressure conditions

Mammone, J. F., H, K. Mao, and P. M. Bell (1981). Equations of state of CaO under static pressure conditions. Geophys. Res. Letts. 8, 140-42. Manghnani, M. H., and S. Akimoto (1977) (eds.). High Pressure Research— Application to Geophysics. New York Academic Press. [Pg.485]

Once the boundary conditions are fixed (i.e., local decay heat generation rate, inlet coolant temperature, channel coolant flow rate, plenum pressure, assembly pressure drop and inlet air void fraction), FLOWTRAN-TF iterates between cells/nodes to obtain an axial temperature distribution for the fuel assembly subchannel surfaces as a function of time. In the calculation for power limits, the assembly power is progressively increased in increments until one of the subchannel surface nodes equals or exceeds the ECS T/H criterion (i. e., the fuel surface temperature exceeds the coolant saturation/boiling temperature for the static pressure conditions at that axial location (T... [Pg.553]

Axial fans are classified as propeller, tube-axial, and vane-axial (Fig. 9). The choice of fan requited is determined by the resistance (static pressure) the fan must work against as well as the volume flow requited. PtopeUet fans usually discharge iato a plenum or directly iato the atmosphere. Tube-axial fans are usually mounted ia ducts as ia an air conditioning system. Vane-axial fans are also mounted ia ducts but feature a stationary guide vane on the discharge side that straightens the air flow to improve efficiency. Tube-axial fans can work at static pressures up to 623 Pa (2.5 ia. H2O) vane-axial fans can work up to 2000 Pa (8 ia. H2O). [Pg.110]

Performance Curves. Pan manufacturers furnish fan performance curves for each type fan available. These are typically based on 61 m/s (12,000 ft/min) tip speed and 1.20 kg/m (0.075 lb /ft ) density. To select a fan for a specific duty requires knowledge of the flow, static pressure resistance, and density of the actual operating conditions. Usually the fan diameter is known as well as some idea of operating speed a 61 m/s tip speed can often be assumed. [Pg.112]

Gas flows are often determined by measuring the associated pressures. Figure 32-4 illustrates several different pressure measurements commonly made on systems carrying gases. Static pressure measurements are made to adjust the absolute pressure to standard conditions specified in the test procedure. [Pg.538]

In order to avoid the need to measure velocity head, the loop piping must be sized to have a velocity pressure less than 5% of the static pressure. Flow conditions at the required overload capacity should be checked for critical pressure drop to ensure that valves are adequately sized. For ease of control, the loop gas cooler is usually placed downstream of the discharge throttle valve. Care should be taken to check that choke flow will not occur in the cooler tubes. Another cause of concern is cooler heat capacity and/or cooling water approach temperature. A check of these items, especially with regard to expected ambient condi-... [Pg.422]

Adsorption for gas purification comes under the category of dynamic adsorption. Where a high separation efficiency is required, the adsorption would be stopped when the breakthrough point is reached. The relationship between adsorbate concentration in the gas stream and the solid may be determined experimentally and plotted in the form of isotherms. These are usually determined under static equilibrium conditions but dynamic adsorption conditions operating in gas purification bear little relationship to these results. Isotherms indicate the affinity of the adsorbent for the adsorbate but do not relate the contact time or the amount of adsorbent required to reduce the adsorbate from one concentration to another. Factors which influence the service time of an adsorbent bed include the grain size of the adsorbent depth of adsorbent bed gas velocity temperature of gas and adsorbent pressure of the gas stream concentration of the adsorbates concentration of other gas constituents which may be adsorbed at the same time moisture content of the gas and adsorbent concentration of substances which may polymerize or react with the adsorbent adsorptive capacity of the adsorbent for the adsorbate over the concentration range applicable over the filter or carbon bed efficiency of adsorbate removal required. [Pg.284]

Exhauster and Motor Air movers for LVHV systems are not conventional fans. The low static pressures needed to operate LVHV systems can be generated by multiple-stage centrifugal (turbine-type) exhausters. These utilize high-precision rotating blades that can be damaged by dust. Consequently, it is always necessary to have an air cleaner in an LVHV dust control system to protect the fan. The low static pressures also require air volume flow rates to be corrected to standard conditions for exhauster selection. [Pg.865]

Fig. 2.9. The measured stress-volume relation of shock-loaded sapphire reveals a substantial reduction in strength, but a small finite strength is retained. The reduction in strength is indicated by the small high pressure offset between the static and shock data, and from extrapolation of high pressure shock data to atmospheric pressure conditions (Graham and Brooks [71G01]). Fig. 2.9. The measured stress-volume relation of shock-loaded sapphire reveals a substantial reduction in strength, but a small finite strength is retained. The reduction in strength is indicated by the small high pressure offset between the static and shock data, and from extrapolation of high pressure shock data to atmospheric pressure conditions (Graham and Brooks [71G01]).
Safety-Relief Valve this is an automatic pressure-relieving device actuated by the static pressure upstream of the valve and characterized by an adjustment to allow reclosure, either a pop or a non-pop action, and a nozzle type entrance and it reseats as pressure drops. It is used on steam, gas, vapor and liquid (with adjustments), and is probably the most general tyqDe of valve in petrochemical and chemical plants (Figures 7-3, 7-3A, and 7-4). Rated capacity is reached at 3% or 10% overpressure, depending upon code and/or process conditions. It is suitable for use either as a safety or a relief valve [1,10]. It opens in proportion to increase in internal pressure. [Pg.400]

Figure 12-136A, B. Effects of fan dampers on airflow, static pressure, and brake horsepower. (A) Backwardiy inciined fan with outiet damper. (B) iniet damper appiied to condition of (A). (Used by permission Engineering Letter No.11, 1996. The New York Biower Co. For more information, contact the company at www.nyb.com.)... Figure 12-136A, B. Effects of fan dampers on airflow, static pressure, and brake horsepower. (A) Backwardiy inciined fan with outiet damper. (B) iniet damper appiied to condition of (A). (Used by permission Engineering Letter No.11, 1996. The New York Biower Co. For more information, contact the company at www.nyb.com.)...
Figure 12-138A, B, C, D. Centrifugal fan system control methods. Note the effect of air distribution zone control (A for VAV) terminal on sudden jump in system resistance to fan operating static pressure curve. (Used by permission Haines, R. W. Heating/Piping/Air Conditioning, p. 107, Aug. 1983. Penton Media, Inc. All rights reserved.)... Figure 12-138A, B, C, D. Centrifugal fan system control methods. Note the effect of air distribution zone control (A for VAV) terminal on sudden jump in system resistance to fan operating static pressure curve. (Used by permission Haines, R. W. Heating/Piping/Air Conditioning, p. 107, Aug. 1983. Penton Media, Inc. All rights reserved.)...
For the Ian existing in Example 12-15, what will he the conditions if the static pressure must he changed from 2 to 3.5 in. due to a change in the system pressure level into which the fan discharges The piping system, air density, and Ian size remain unchanged. What will he the new operating conditions for this fan ... [Pg.560]

From manufacturers rating tables for air or gas, at the required cfm at inlet operating conditions and the equivalent static pressure calculated in (2), read the rpm and bhp. Interpolate if necessary. [Pg.571]

Using actual cfm at intake conditions to fan and equivalent static pressure (2), read manufecturers rating tables for bhp and rpm. Note that if exact cfm or pressure value is not listed in tables, it may be reached by (a) interpolation as previously described for approximation or (b) by using fan laws to correct one set of table values. [Pg.571]


See other pages where Static pressure conditions is mentioned: [Pg.136]    [Pg.196]    [Pg.1224]    [Pg.527]    [Pg.111]    [Pg.112]    [Pg.119]    [Pg.444]    [Pg.756]    [Pg.961]    [Pg.136]    [Pg.196]    [Pg.1224]    [Pg.527]    [Pg.111]    [Pg.112]    [Pg.119]    [Pg.444]    [Pg.756]    [Pg.961]    [Pg.113]    [Pg.496]    [Pg.28]    [Pg.506]    [Pg.787]    [Pg.1169]    [Pg.1212]    [Pg.2200]    [Pg.2328]    [Pg.2526]    [Pg.75]    [Pg.542]    [Pg.543]    [Pg.518]    [Pg.169]    [Pg.48]    [Pg.650]    [Pg.550]    [Pg.551]    [Pg.551]    [Pg.554]    [Pg.564]    [Pg.571]    [Pg.572]    [Pg.576]   
See also in sourсe #XX -- [ Pg.111 ]




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