chemical physics of discharges - Argonne National Laboratory
chemical physics of discharges - Argonne National Laboratory chemical physics of discharges - Argonne National Laboratory
5 56 then t = to when e = 0 2) the final temperature of the briquette will be the temperature of the surroundings : I therefore t = t, when e = *go 3) there is no heat flow across the central plane because of symmetry: { I consequently -k (2;) - = 0 at x 0 The heat balance on the briquette surface is made by equating heattrans- ferred to the surface by conduction with heat transferred from the surfac by convect&,on.. In differential form, the heat balance is: ' -k dt = h (t - t,) at x = +a . (a4 % Newman') showed that the solution to Equations (1) through in terms of a dimensionless temperature ratio Yx is: ma (I+$ ma2 +ma) cospn where An= and pn are defined as the first, second, third, etc., roots of cendental equation: Pn TAN pn - I /ma = 0 The surface to solid thermal resistahce ratio, ma, ma = k/ha and Xa is defined as: xq = ae/a2 where the thermal diffusivity is: a = k/p Cp (5) (5) expressed the trans- Similarily , considering radial heat transfer , the .radial briquettl heat balance is The initial condition equation is: toto WHEN' 8=0 The final temperature equation is: t= 1, WHEN 8. - The boundary condition equations are: -k (g)=O AT r=O (7) (12) i
557 and -k (%)= h (t-ts) AT f =R Solving Equations (11) through (15) gives: and Pn ar,e the first, second, third, etc., roots of the equation: and . . PnJI(fin) - I/mr Jo(Pn) =.O The surface to solid thermal resistance ratio, mr is I x, = a8/R2 ~ and is : (18) frIr = k/hR (19 1 The complete differential equation for the case shown in Fig. 1 the solution to Equation (21) is: , eqn. 22 becomes: . . I If the center temperature defined at r = 0, x = 0 is tc, then tC’+S Yc= - = Yr to ’tS Y, where y, 1 and YX are evaluated at r = 0 and x = 0. i The preceding mathematical analysis shows that the rate of cooling, lor change in center temperature for a cyclindrical briquette is a function I of, time (8 ) , density ( e) , thermal conductivity (k) , the surface heat ) transfer coefficient (h) , specific heat (C,) and the briquette dimensions I as expressed by Equation (23). The experimental technique can now be described in terms of th; ~p~vious discussion. If the change in center temperature with time is Rsa- ,sued experimentally for a material of known thermal and physical prop- ‘erties (standard briquette) , the surface heat transfer coefficient can be calculated from Equation (23), since it is the only unknown. (20)
- Page 512 and 513: d 601 L P LL
- Page 516 and 517: I I I I I I I I m W N W N 0 (D ? 0
- Page 518 and 519: 514 was heated under nitrogen in a
- Page 520 and 521: The line broadening at 79OK of the
- Page 522 and 523: 13. 14. 15. 16. 17. 18. 19. 20. 21.
- Page 524 and 525: W L, Z 6 m (1: 0 6 d j o 2 ' 1 0.0
- Page 526 and 527: Coals 522 Studies of the 1600 cm-l
- Page 528 and 529: L in ole i c a c id - 0' Two sample
- Page 530 and 531: 526 Table 1.- Ultimate analyses of
- Page 532 and 533: 528 6. Friedel, R. A., and H. Retco
- Page 534 and 535: egeneration. The system can be seen
- Page 536 and 537: 532 and can be expressed in terms o
- Page 538 and 539: 534 in the vapor increases with inc
- Page 540 and 541: NH3 NH3 NH3 NH3 Pyridine Pyridine P
- Page 542 and 543: Mole Ratio of Test No. Quinoline to
- Page 544 and 545: IXPROFJCTION D; M. Mason Institute
- Page 546 and 547: -4:c~rciiny to recent studies o ;i4
- Page 548 and 549: 544 Table 1. LIGHT EMISSION OF Y"TR
- Page 550 and 551: emission in a few cases may be by d
- Page 552 and 553: LITERATUR2 CITED i. C. -. .' * il.
- Page 554 and 555: co, CH,,OR 1 - OTHER ADDITIVE FRITT
- Page 556 and 557: FRIT 'TED CO, CH,.OR 4 ___ OTHER AD
- Page 558 and 559: 340 350 300 400 4 50 500 600 700 80
- Page 560 and 561: 0 554 WITH COOLING (PLATE AT 40°C)
- Page 564 and 565: 5 58 The surface heat transfer coef
- Page 566 and 567: Discussion and Results 560 Three br
- Page 568 and 569: __- ._ 562 Table I THERMAL AND PHYS
- Page 570: ln 4 I 0 4J v \ 1.0 0.8 0.6 L - 0.4
5 56<br />
then t = to when e = 0<br />
2) the final temperature <strong>of</strong> the briquette will be the temperature <strong>of</strong><br />
the surroundings : I<br />
therefore t = t, when e = *go<br />
3) there is no heat flow across the central plane because <strong>of</strong> symmetry: {<br />
I<br />
consequently -k (2;) - = 0 at x 0<br />
The heat balance on the briquette surface is made by equating heattrans-<br />
ferred to the surface by conduction with heat transferred from the surfac<br />
by convect&,on.. In differential form, the heat balance is: '<br />
-k dt = h (t - t,) at x = +a<br />
. (a4 %<br />
Newman') showed that the solution to Equations (1) through<br />
in terms <strong>of</strong> a dimensionless temperature ratio Yx is:<br />
ma<br />
(I+$ ma2 +ma) cospn<br />
where An= and<br />
pn are defined as the first, second, third, etc., roots <strong>of</strong><br />
cendental equation:<br />
Pn TAN pn - I /ma = 0<br />
The surface to solid thermal resistahce ratio, ma,<br />
ma = k/ha<br />
and Xa is defined as: xq = ae/a2<br />
where the thermal diffusivity is: a = k/p Cp<br />
(5)<br />
(5) expressed<br />
the trans-<br />
Similarily , considering radial heat transfer , the .radial briquettl<br />
heat balance is<br />
The initial condition equation is:<br />
toto WHEN' 8=0<br />
The final temperature equation is:<br />
t= 1, WHEN 8. -<br />
The boundary condition equations are:<br />
-k (g)=O AT r=O<br />
(7)<br />
(12) i