Entry temperature

External Treated cooling water entry temperature 80°F (27°C), exit temperature 130-212°F (55-100°C)... 

B is the heat transfer from Z to the closed cycle within control surface Y, which occurs during the time interval that A/f, the mass of fuel, is supplied and [CV]q is its calorific value per unit mass of fuel for the ambient temperature (Tq) at which the reactants enter. F = A/f[CV]o is equal to the heat (0o) that would be transferred from Z if the products were to leave the control surface at the entry temperature of the reactants, taken as the temperature of the environment, Tq. Fig. 1.7 illustrates the definition of calorific value. 

Thus the cooled reversible cycle [CHT]rci with a first rotor inlet temperature, Tj, will have an internal thermal efficiency exactly the same as that of the uncooled cycle [CHTJru with a higher turbine entry temperature 3 = Tr, and the same pressure ratio. There is no penalty on efficiency in cooling the turbine gases at entry but note that the specific work output, w = (wj — wc)/CpT = [(0 /x) — 11(j — 1), is reduced, since 0 < 0. 

For two step cooling, now with irreversible compression and expansion, Fig. 4.7 shows that the turbine entry temperature is reduced from Ti. to by mixing with the cooling air i/ H taken from the compressor exit, at state 2, pressure p2, temperature T2 (Fig. 4.7a). After expansion to temperature Tg, the turbine gas flow (1 + lp ) is mixed with compressor air at state 7 (mass flow i/h.) at temperature Tg. This gas is then expanded to temperature T g. 

In a particular blade row, for a given gas entry temperature Tgj, a cooling air entry temperature and an assumed allowable blade metal temperature Tbi, the blade cooling effectiveness eq is obtained. With ep = 0.4 and Pcooi = 0-7, then follows from Eq. (5.10). With C = 0.045 the cooling air flow fraction ip is obtained from Eq. (5.13). 

If the compressor entry temperature T] is the same as the ambient temperature then Eq. (6.3) may be rewritten as... 

Even for this simplest CCGT plant, iterations on such a calculation are required, with various values of p, in order to meet the requirements set on T, the steam turbine entry temperature, and 7s (the calculated value of 7s has to be such that the dewpoint temperature of the gas (7jp) is below the economiser water entry temperature (7b) and that may not be achievable). But with the ratio /i satisfactorily determined, the work output from the lower cycle Wl can be estimated and the combined plant efficiency obtained from... 

For (b), Cerri assumed that the supplementary heat supplied was sufficient to give a maximum temperature equal to the assumed maximum steam entry temperature T. In general, it was shown that for the higher values of now used in CCGT plants there was little or no benefit on overall efficiency associated with supplementary heating. 

This approaeh was well illustrated by Brieseh et al. f 14], who showed separate plots of ( o)h. ( o)l and (t o)cp against pressure ratio for a given T ax and r ,in (Fig. 7.11), illustrating the validity of Eq. (7.35). But note that the limiting allowable steam turbine entry temperature also influences the ehoiee of pressure ratio in the gas turbine eyele. 

Heat, See also High temperature entries Hot entries Temperature entries Therm- entries effect on rubber aging, 27 785 in ethylene oxidation, 70 650 exponents of dimensions, 8 585t external resistance to, 25 312-316 in industrial hygiene, 74 221 wood reaction to, 26 348-351 Heat aging, of polychloroprene polymers, 79 844-845... 

Entry Temperature Conditions Yield 133(%) dr 133 (anli/syri) Yield 134(%) dr 134 (anli/syri)... 

For an entry temperature of 120°C and an adiabatic saturation temperature of 70°C, the expected outlet temperature would be... 

Pure crossflow is found in flat plate heat exchangers, as indicated by Fig. 1.22. The temperatures of both fluids also change perpendicular to the flow direction. This is schematically shown in Fig. 1.23. Each fluid element that flows in a crossflow heat exchanger experiences its own temperature change, from the entry temperature which is the same for all particles to its individual exit temperature. Crossflow is often applied in a shell-and-tube heat exchanger when one of the fluids is gaseous. The gas flows around the rows of tubes crosswise to the tube axis. The other fluid, normally a liquid, flows inside the tubes. The addition of... 

Fig. 1.26 is a scheme for a heat exchanger. The temperatures of the two fluids are denoted by S1 and t 2, 98 in section 1.3.1, and it will be assumed that q > t 2. Heat will therefore be transferred from fluid 1 to fluid 2. Entry temperatures are indicated by one dash, exit temperatures by two dashes. 

Fig. 1.26 Heat exchanger scheme, with the mass flow rate Mi, entry temperatures exit temperatures entry enthalpy h and exit enthalpy h" of both fluids (i = 1,2)...

Afterburner entry temperature of effluent = 738°F Afterburner heat loss= 10% in excess of calculated heat load Afterburner dimensions = 4.2 ft in diameter, 14 ft in length... 

Whichever method is selected, the calculations start at one end of the condenser, the vapor inlet presumably, where the vapor temperature, pressure, flow rate, and composition is known and proceed until either a specified area has been reached (a simulation problem) or until a specified amount of vapor has been condensed (a design problem). To simplify the calculations it is usual to specify the temperature of the coolant at the vapor inlet end of the condenser and determine the coolant entry temperature as part of the solution. Multiple pass condensers (where the coolant and/or gas vapor streams make more than one pass... 

A sketch of the steady-state problem that we will consider is shown in Fig. 3 13. The tube radius is denoted as a, and we utilize the standard cylindrical coordinates (r, (f>, z).18 We assume that the wall of the tube is insulated so that the heat flux is zero for positions z < 0. On the other hand, beginning at z = 0 and for all z > 0 there is a constant positive heat flux q through the wall of the tube. A reasonable approximation to this condition can be realized if the tube is uniformly wrapped with a heat tape or wire resistance heater beginning at z = 0. It may be noted that the problem would be identical from a mathematical point of view if there were a negative heat flux prescribed so that the temperature of the fluid in the tube decreased rather than increased for z > 0. We assume that the entry temperature of the fluid into the heated portion of the tube is Qo and that viscous dissipation can be neglected. 

Entry Temperature (°C) Yield (%) 3-fluorotoluene Yield (%) 3-chlorotoluene Yield (%) m-cresol Yield (%) carbonate... 

Entry Temperature rc) Reducing agent Yield of [3al (%) Recovery of [121 (%) Yield of other products (%)... 

In Figure 14.26, the instantaneous efficiency and the outlet temperature of a liquid-type collector (single-covering, steel finned tubes, black absorber) are illustrated as a function of liquid heat capacity flow rate [37]. The parameter is the irradiation. As the variations of I are accompanied by nonlinear heat transfer resistance variations, the curves for different I values deviate. The entry temperature of the medium is equal to the outside temperature (T j = TJ. 

---