#### Transcript Slide 1

**THE LOOP HEAT PIPE FOR AMS-02**

Stefano Zinna Marco Marengo LSRM, Faculty of Engineering, University of Bergamo, viale Marconi 5, 24044 Dalmine, Italy

**Inside ANTASME**

**OBTAINED RESULTS 8.1 The LHP for AMS is built and run for orbital conditions 8.2 The ground LHP for AMS is built and stationary results are compared with LHP model in microgravity 8.3 The construction of the **

*thermal chamber in China is delayed (cancelled)*

**8.4 A simplified model of the LHP is carried out in order to be implemented in multidisciplinary codes 9.3 The LHP model has been run by including the FEM results about valve**

## INDEX

**1.**

**2.**

**3.**

**Simulation of the LHP prototype in the thermal chamber (ground test) (deliverable 8.2) Definition of data input and output structures for future implementation in general multidisciplinary codes (deliverable 8.4) Implementation of the FEM data in the SINDA/FLUINT network scheme (deliverable 9.3)**

**Deliverable - 8.2**

**Simulation of the LHP prototype in the thermal chamber (ground test)**

**Ground LHP results**

The ground propylene LHP has been implemeted: The model has different correlation for pressure drop and condensation in the two phase part (condenser) The reservoir temperature (T CC ) and subcooling temperature (T model S ) are compared with microgravity Stationary mode is run with power from 30 W to 90 W The 1G results have temperature lower than m G while the power is increasing The temperature difference is about 2 ° for 90W 254 252 250 248 246 244 242 240 238 236 234 232 230 228 226 224 30 40 50 60 Q [W] 70 80 90 T CC T S CONDENSER T CC ( m G) T S ( m G) T CC ( G) T S ( G)

m

**-G/1G PRESSURE DROP**

m

**-G**

Bubbly/Slug flow **: ***McAdam* ’s formulation for homogeneous flow The annular regime **: ***Lockhart-Martinelli* correlation

**(Zhao L. Rezkallah K.S., 1995. Pressure drop in gas-liquid flow at microgravity conditions. Int. J. Multiphase Flow 21, 837-849) 1G**

The predicted pressure drops is based on the

*Muller-Steinhagen and Heck*

correlation (

*John R. Thome, Wolverine Engineering Data Book III, 2006*

) The factors A and B are the frictional pressure gradients for all the flow liquid and all the flow vapour

**1G Model SLIP FLOW**

The

*Tabular*

connector device allows users to specify flow rate versus head (or pressure drop) relationships in tabular (array) formats The gravitational forces are independent of the velocity while the friction and the acceleration forces are function of the square of the flow rate These coefficient are inserted in the equation for the fluid path while the vapour path is set in order to satisfy the slip flow model chosen

m

**-G/1G pressure drop differences**

The Clausius –Clapeyron correlation is used to calculate the temperature difference in the two-phase part of the condenser

**Q [W] 30 60 90**

MICROGRAVITY D T D P (Pa) 0.008

0.076

69.3

701.7

0.16

1815.7

NORMAL GRAVITY D T D P (Pa) 0.012

0.095

97.2

874 0.16

1791

*THE TEMPERATURE DIFFERENCE IS WEAKLY RELATED TO THE PRESSURE DROP*

m

**-G/1G CONDENSATION**

m

**-G**

The condensation heat transfer coefficient for two-phase flow is based on

*Shah*

’s correlation (

*Po-Ya Abel Chuang, An improved steady-state model of loop heat pipes on experimental and theoretical analyses. 2003, Phd Thesis*

)

**1G**

The correlation is based on

*Dobson and Chato method*

. (Soliman transition criterion) (

*John R. Thome, Wolverine Engineering Data Book III, 2006*

) The annular correlation: The stratified-wavy correlation:

**GRAVITY FLOW PATTERN**

The

*Soliman*

transition criterion for predicting the transition from annular flow to stratified-wavy flow was used The G is always lower than 500: G (30W)=9.3; G (60W)=18.7; G (90W)=28 The transition from stratified to annular is with quality between 0.6 and 0.8 depending on the temperature 150 100 50 0 350 300 250 200 ANNULAR 0,0 STRATIFIED 0,2 0,4 0,6 X 0,8 225 K 240 K 255 K 270 K 285 K 300 K 315 K 1,0 transition

m

**-G/1G condensation differences**

TRANSITION 3,5 3,0 2,5 2,0 1,5 8,0 7,5 7,0 6,5 6,0 5,5 5,0 4,5 4,0 0,0 0,2 0,4 0,6 0,8 1,0 X TRANSITION 9 8 7 6 5 4 3 2 1 0,1 0,2 0,3 225 K 285 K 315 K 0,4 0,5 X 0,6 0,7 0,8 0,9 1,0 225 K 285 K 315 K Q 90 W 30 W Stratified-wavy Dobson & Chato heat transfer compared with Shah heat transfer High quality The heat transfer coefficient difference is higher with higher power incoming the evaporator Annular Dobson & Chato heat transfer compared with Shah heat transfer Low quality The heat transfer for D&C is always higher

**CONCLUSIONS**

The gravity model temperatures are lower than the microgravity model and the difference is increasing while the power incoming in the evaporator is increasing The pressure drop has a negligible influence on the temperature drop in the two-phase condenser Wider two-phase lenght for high power Higher difference in the heat transfer for high power

**Deliverable - 8.4**

Definition of data input and uotput structures for future implementation in general multidisciplinary codes

**ANALYTICAL MODEL**

### (Evaporator balance)

•

*To test the SINDA/FLUINT results and to understand which are the most important parameters that influence the LHP in order to set the input/output structures*

•The heat absorbed from the cryoo cooler crosses from the evaporator wall to the solid wick and it is shared between Fluid wick and Reservoir: •The pressure in the end of the liquid line is close to the saturation pressure & the liquid flow rate depends on the power and the evaporation enthalpy at saturation temperature (Tsat): U W G back

**ANALYTICAL MODEL**

### (Radiator balance)

•The temperature changes depends only on the axial conductances with the evaporator wall and can be considered negligible while the pressure drop has a small influence on the enthalpy: •The power rejected from the radiator (Qout) is due to the radiation towards the external environmental

**ALGEBRAIC SYSTEM**

•The algebraic system has now 5 parameters:

*T sink*

:

*U WB*

,

*Q CRYO*

,

*Q flux*

,

*G rad*

, •The results are shown in the graphic for the steady state operating temperature: (a) Qflux=70 [W], Uwb=25/3 (b) Qflux=0 [W], Uwb =25/3 (c ) Qflux=70 [W], Uwb=25/6. For all the cases the radiative conductance Grad is 5.0

10-9 [W/T^4] and the Tsink is 170K.

300 280 260 240 220 200 180 Tsink 0 20 40 60 80 100 120 140 160 180 200 220 240 260 Q [W]

**CONDENSER TEMPERATURE**

The initial part of the pipe is near the end. The high temperature of the incoming two-phase fluid causes a important heat transfer to the outgoing fluid, the T S increases and consequently the T CC is higher. Another heat flux is exchanged between two parts of the same condenser in the middle of the radiator and leads to the first maximum in figure.

**Input/output structures**

Where L o is a system operator, t is time, x(t) is the state of the system, u(t) is its input, w(t) is some external or internal disturbance, and parameter that defines the system. Each one of these quantities belongs to a suitable set or vector space and there are a large number of possibilities l is a

**y**

: the steady state operating temperature and subcooling temperature; radiator); l

**u**

: the power coming in the evaporator;

**w**

: the boundary conditions (the external fluxes in the radiator, the radiative conductance and the sink temperature for the : the ratio between the conductance inside the wick and the conductance from the wick to the reservoir, and the radiator area.

INPUT OUTPUT SYSTEM BOUNDARY

**CONCLUSIONS**

An analytical model is carried out in order to achieve a simplified model: good approximation of the SINDA results for high power The input/output structures are defined: the solver L o could be by the analytical model (L o -> an algebraic operator ) or the sinda model SINDA ANALYTICAL MODEL

**Deliverable - 9.3**

Implementation of the FEM data in the SINDA/FLUINT network scheme

**LHP-VALVE**

Temperature requirements: Min. turn-on and operational temperature of the Cryo cooler Max. operational temperature of the Cryo-cooler 263K 313K Q VALVE WORST CONDITIONS (Coldest environment, nominal working (2LHP), minimum power (61W)) : 226K< T CRYO <230K CRYO COOLER T CRYO EVAPORATOR RADIATOR T RAD T CC L H P EXTERNAL AMBIENT

**Implementation of the FEM data**

VALVE The information about the valve come from FEM ANALYSIS (Speetjens M. & Rindt, C. 2006 Numerical analysis of the bypass valve in aloop heat pipe,

*INTERREG IIIC MATEO-ANTASME Deliverable 9.2.*

) The solver is only sinda (NO analytical model) The pressure drop : SINDA

**1 set point **

OPEN MODE: T CRYO <263 CLOSE MODE: T CRYO >263 The temperature in the cryo react quickly to the open mode The temperature in the cryo reachs 262.7 240 220 200 264 262 260 258 256 254 252 250 280 8000 260 8500 9000 time [s] 9500 10000 5000 10000 15000 time [s] 20000 25000 T CRYO T R T T CRYO R T RAD

**2 set point **

OPEN MODE: T CRYO <263 CLOSE MODE: T CRYO >265 Valve between the open and the close mode: 263

**CONCLUSIONS**

The FEM data are inserted in the sinda model and two cases are run depending on 1/2 set points There is a little inertia between the compensation chamber and the cryo a higher set point should be chosen 2 set point should be definied