IEA Solar Heating and Cooling Programm - NachhaltigWirtschaften.at
IEA Solar Heating and Cooling Programm - NachhaltigWirtschaften.at IEA Solar Heating and Cooling Programm - NachhaltigWirtschaften.at
IEA SHC Task 38 Solar Air Conditioning and Refrigeration Subtask C2-A, November 9, 2009 Internally, in addition to the tube bundles, the solution contributes by 50% of its mass in generator and absorber. In analogy, the refrigerant is assumed to have a 50% internal contribution in both evaporator and condenser. The mass of solution heat exchanger and solution pump has an internal effect on both generator and absorber heat transfer and is assumed to contribute by 50% of its weight on both. The vessel wall now contributes internally by 50% of its weight due to the larger surface area involved in heat transfer mainly in the sumps. Enthalpy balances Taking internal and external thermal storage as in Figures 3 and 4 into account, equations (6) to (9) can be refined and the external and internal enthalpy balances for the vessels can now be expressed. The external enthalpy balance of the vessels describes that the heat which is given off (generator) or taken on (absorber) by the heat carrier (left-hand side of equation (25) or (26)) partly crosses the heat exchanger (first term on the right-hand side, grey arrows in Figures 3 and 4) and reaches the mean vessel temperature, partly is used to heat up parts of the vessel which are more or less at external temperature (second term on right-hand side). For generator and evaporator, the external enthalpy balance reads ϑX , i −ϑX , i−1 m& X , w ⋅ c p, w ⋅ ( ϑX , in −ϑX , out ) = ( UA) ext, X ⋅ ( ϑ X , i − TX , i ) + ( M ⋅ c p ) ⋅ (25) ext, X ∆t In equation (25), index X denotes the different vessels of generator and evaporator (X = G, E). For absorber and condenser the external enthalpy balance reads ϑX , i −ϑX , i−1 m& X , w ⋅ c p, w ⋅( ϑX , in −ϑX , out ) = −( UA) ext, X ⋅ ( ϑX , i −TX , i ) − ( M ⋅c p ) ⋅ (26) ext, X ∆t Index X in equation (26) denotes absorber and condenser (X = A, C). The internal enthalpy balances for all vessels read as follows. T E, i − T E, i−1 ( r − c ⋅ ( T C, i − T E, i ) + ( M ⋅ c ) ⋅ = ( UA ⋅ ( T − T E i ) & (27) ∆t m v, A, i ⋅ ( pc) p, v p ) E E,int E, i , ,int m& = v, G, i ⋅ ( r( pc) + l( pc) + c p, w, i ⋅ ( T G, i − T A, i ) + Q& SHX , i + ( M ⋅ c p ) ( UA) ⋅ ( T − T G, i ) G,int G, i G,int T ⋅ G, i − T ∆t G, i−1 (28) page 72
IEA SHC Task 38 Solar Air Conditioning and Refrigeration Subtask C2-A, November 9, 2009 T C, i − T C, i−1 ( r + c ⋅ ( T G, i − T C, i ) + ( M ⋅ c ) ⋅ = ( UA) ⋅ ( T T ) & (29) ∆t m v, G, i ⋅ ( pc) p, v p C,int C,int C, i − C, i m& v, A, i ⋅ ( r + l − c ⋅ ( T G, i − T E, i ) + c ⋅ ( T G, i − T A, i ) ( pc) T A, i − T A, i−1 ( M ⋅ c ) ⋅ = ( UA) ⋅ ( T − T ) p A,int ( pc) ∆t p, v A,int p, w A, i A, i + Q& SHX , i + (30) Equations (27) and (28) describe the internal heat transfer in evaporator and generator, respectively. There, the heat which is given off by the heat exchanger (right-hand side) partly heats up the internal parts of the vessel (second term on left-hand side) and partly is used for the heating of solution and refrigerant (first term on left-hand side). In analogy, equations (29) and (30) describe condenser and absorber, respectively. There, the heat which is given off by the solution and refrigerant (first term on left-hand side) is used partly to heat the internal parts of the heat exchanger (second term on left-hand side) and partly to heat the cooling water (right-hand side). The equation system is being solved in MATLAB using a Newton-Raphson procedure with finite-difference Jacobian approximation [6]. Experimental Verification The agreement between simulated and experimental data has been tested using an experimentally measured hot water input step from 75 to 85 °C. The results of the simulation using these input data are shown in Figure 5. The hot water inlet and outlet temperatures in Figure 5 are taken from experimental measurements of the Phoenix absorption chiller. They show the transient behaviour of the chiller for a 10K step in hot water inlet temperature. Cooling and chilled water inlet temperatures as well as all external mass flow rates were kept constant during the step. It can be seen that it takes approx. 600s or 10 minutes to achieve a new steady-state in hot water inlet temperature after the step. This is shorter than the 15 minutes it takes for all parameters to achieve steady-state again. The simulation was performed using the measured data as inputs in the model and comparing simulated and measured hot water outlet temperatures. page 73
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<strong>IEA</strong> SHC Task 38 <strong>Solar</strong> Air Conditioning <strong>and</strong> Refriger<strong>at</strong>ion Subtask C2-A, November 9, 2009<br />
Internally, in addition to the tube bundles, the solution contributes by 50% of its mass in<br />
gener<strong>at</strong>or <strong>and</strong> absorber. In analogy, the refrigerant is assumed to have a 50% internal<br />
contribution in both evapor<strong>at</strong>or <strong>and</strong> condenser. The mass of solution he<strong>at</strong> exchanger <strong>and</strong><br />
solution pump has an internal effect on both gener<strong>at</strong>or <strong>and</strong> absorber he<strong>at</strong> transfer <strong>and</strong> is<br />
assumed to contribute by 50% of its weight on both. The vessel wall now contributes<br />
internally by 50% of its weight due to the larger surface area involved in he<strong>at</strong> transfer mainly<br />
in the sumps.<br />
Enthalpy balances<br />
Taking internal <strong>and</strong> external thermal storage as in Figures 3 <strong>and</strong> 4 into account, equ<strong>at</strong>ions<br />
(6) to (9) can be refined <strong>and</strong> the external <strong>and</strong> internal enthalpy balances for the vessels can<br />
now be expressed. The external enthalpy balance of the vessels describes th<strong>at</strong> the he<strong>at</strong><br />
which is given off (gener<strong>at</strong>or) or taken on (absorber) by the he<strong>at</strong> carrier (left-h<strong>and</strong> side of<br />
equ<strong>at</strong>ion (25) or (26)) partly crosses the he<strong>at</strong> exchanger (first term on the right-h<strong>and</strong> side,<br />
grey arrows in Figures 3 <strong>and</strong> 4) <strong>and</strong> reaches the mean vessel temper<strong>at</strong>ure, partly is used to<br />
he<strong>at</strong> up parts of the vessel which are more or less <strong>at</strong> external temper<strong>at</strong>ure (second term on<br />
right-h<strong>and</strong> side). For gener<strong>at</strong>or <strong>and</strong> evapor<strong>at</strong>or, the external enthalpy balance reads<br />
ϑX<br />
, i<br />
−ϑX<br />
, i−1<br />
m& X , w<br />
⋅ c<br />
p,<br />
w<br />
⋅ ( ϑX<br />
, in<br />
−ϑX<br />
, out<br />
) = ( UA) ext,<br />
X<br />
⋅ ( ϑ<br />
X , i<br />
− TX<br />
, i<br />
) + ( M ⋅ c<br />
p<br />
) ⋅<br />
(25)<br />
ext,<br />
X<br />
∆t<br />
In equ<strong>at</strong>ion (25), index X denotes the different vessels of gener<strong>at</strong>or <strong>and</strong> evapor<strong>at</strong>or (X = G,<br />
E). For absorber <strong>and</strong> condenser the external enthalpy balance reads<br />
ϑX<br />
, i<br />
−ϑX<br />
, i−1<br />
m& X , w<br />
⋅ c<br />
p,<br />
w<br />
⋅( ϑX<br />
, in<br />
−ϑX<br />
, out<br />
) = −( UA) ext,<br />
X<br />
⋅ ( ϑX<br />
, i<br />
−TX<br />
, i<br />
) − ( M ⋅c<br />
p<br />
) ⋅<br />
(26)<br />
ext,<br />
X<br />
∆t<br />
Index X in equ<strong>at</strong>ion (26) denotes absorber <strong>and</strong> condenser (X = A, C).<br />
The internal enthalpy balances for all vessels read as follows.<br />
T E,<br />
i − T E,<br />
i−1<br />
( r − c ⋅ ( T C,<br />
i − T E,<br />
i<br />
) + ( M ⋅ c ) ⋅<br />
= ( UA ⋅ ( T − T E i )<br />
& (27)<br />
∆t<br />
m<br />
v, A,<br />
i<br />
⋅<br />
( pc)<br />
p,<br />
v<br />
p<br />
)<br />
E<br />
E,int<br />
E,<br />
i ,<br />
,int<br />
m&<br />
=<br />
v,<br />
G,<br />
i<br />
⋅ ( r(<br />
pc)<br />
+ l(<br />
pc)<br />
+ c<br />
p,<br />
w,<br />
i<br />
⋅ ( T G,<br />
i − T A,<br />
i<br />
) + Q&<br />
SHX , i<br />
+ ( M ⋅ c<br />
p<br />
)<br />
( UA) ⋅ ( T − T G,<br />
i )<br />
G,int<br />
G,<br />
i<br />
G,int<br />
T<br />
⋅<br />
G,<br />
i<br />
− T<br />
∆t<br />
G,<br />
i−1<br />
(28)<br />
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