 Open Access
 Total Downloads : 21
 Authors : Amarjeet Kumar Prasad , Ravi Pratap
 Paper ID : IJERTV7IS040433
 Volume & Issue : Volume 07, Issue 04 (April 2018)
 Published (First Online): 30042018
 ISSN (Online) : 22780181
 Publisher Name : IJERT
 License: This work is licensed under a Creative Commons Attribution 4.0 International License
Inclusion of Purge Sector in Rotary Desiccant Wheel: A Review
Amarjeet Kumar Prasad 1
Department of Mechanical Engineering Madan Mohan Malaviya Institute of Technology
Gorakhpur, India
Ravi Pratap 2
Department of Mechanical Engineering Madan Mohan Malaviya Institute of Technology
Gorakhpur, India
Abstract Purge sector is introduced by modifying two sector into three sector or by introducing purge in four sector to make it six sector. Few researchers have found that by adding purge in desiccant wheel increases the moisture removal capacity (MRC) and effectiveness of the wheel compared to two and four sector desiccant wheel. The direction of rotation of wheel i.e. clockwise or anticlockwise rotation has a significant effect on the MRC, temperature difference of process velocity and effectiveness of the wheel. In this paper, a minor review is done to justify the why the introduction of purge is important in the desiccant wheel.
Keywords Desiccant wheel, purge moisture removal capacity, effectiveness.

INTRODUCTION
A traditional air conditioning is primarily based on vapour compression system in which water vapour is eliminated by means of cooling the air beneath dew point temperature. This method consumes more energy and additionally impacts the surroundings through liberating hydrocarbons. Desiccant based cooling system are green and eco friendly. According to one estimate desiccant dehumidification could lessen overall residential or commercial electricity demand by 25% or greater in hot and humid climatic region, providing drier, purifier and greater comfortable indoor surrounding with a decrease energy invoice. Desiccant cooling system displaces chlorofluro carbon based cooling system, the emission from which it contributes to the depletion of earth ozone layer.
Munters [1] investigated that by adding an extra sector on the process inlet and outlet side, an external duct is used to recirculate air into the regeneration cycle after the heater. Depending on airflows application etc. the savings on energy needed for regeneration reaches up to 25%. Y. M. Harshe et al. (2005) [2] developed 2dimension study state model of a rotary desiccant wheel. This model developed was capable of predicating steadystate behaviour of desiccant wheel having at the most three section (process, purge and regeneration). The temperature and humidity profile in the wheel during both the dehumidification and the regeneration process curve analysed M.Golubovic, M.Hettiorocchi, M.Worek (2007) [3] evaluated the rotary dehumidifier with and without heated purge sector. The performance parameter of both were compared and it was found that the heated purge angle had an overall positive effect on the performance of a rotary dehumidifier.. J.Jeonget et al. (2009) [4] carried out evaluation by means of doing 4 partition of desiccant wheel and hybrid dehumidification air conditioning device. It was determined that the exist an optimum rotational velocity to maximize the dehumidification overall performance and that the hybrid air
conditioning device improves COP by 94% in comparison to traditional VC system refrigerator. R.Narayan et al (2011) [5] advanced 1D heat and mass transfer model for desiccant wheel one considering simplest the gas aspect resistance and different considering most effective the both solid and gas side resistance. The model is used to examine the overall performance of various wheel layout. The examine must be that the advent of an axial cooling segment on enhance the overall performance of desiccant wheel substantially. W.Ruan et al. (2012) [6] advanced one dimensional transient heat and mass transfer model to examine the overall performance of enthalpy restoration wheel each with and with out purge air. It was concluded that the an enthalpy restoration wheel with purge air are offered and indicated that there is an most efficient wheel depth and rotation velocity to obtain most overall performance for enthalpy restoration wheel with purge air. A.Yadav (2014) evolved a mathematical model for predicting the overall performance of a desiccant wheel with purge zone, which has been used for both heat, and mass transfer of wet air and desiccant material. It was observed that for all of the cases on this model like rotation of wheel, regeneration temperature velocity and atmospheric moisture, result is higher in an anticlockwise in comparison to clockwise course of the rotation direction of desiccant wheel. A Yadav and L. Yadav (2014) [8] evaluated a comparative overall performance of desiccant wheel with effective and regular regeneration area. furthermore, it was determined that for all of the instances like velocity and ambient moisture, the desiccant wheel with affective regeneration zone offers higher end result in comparison to regular regeneration sector. Yadav and Yadav (2015) [9] developed a mathematical model to investigate the purge sector angle of the desiccant wheel for different operating condition and found that the anticlockwise rotation gives purge angle at any operating condition, the performance increase in lower purge sector angle as compared to higher purge angle. Yadav and Yadav (2017) [10] divided desiccant wheel in to three parts process regeneration and third small sector(TSS). This wheel is numerically investigated by installing TSS in wheel in four different arrangement. A comparative study amongst those arrangement reveals that the for low exit humidity TSS need to be established inside the regeneration side of the desiccant wheel, and DCOP should be excessive and the growth in temperature of system air.

MATHEMATICAL MODEL
The desiccant wheel is divided into more than two section, which includes process sector, regeneration sector, and Purge sector. Where process section is kept at 180Â°, purge section varies from 10Â° to 40Â°, and remaining portion is given to the regeneration section. Purge in to come in to effect when wasteful heat is used to regenerate the absorbent material or purge sector comes into effect because as the wheel is
Flow channel Crosssectional area =
Channel with the desiccant layer Crosssectional area:
Desiccant channel Wall thickness
Flow channel perimeter of given by Zhang et al. (2003)] (11)
continuously rotating at very low speed. When this heated
ab 2
region entered in to process air section, it absorbs very less
a
a
moisture. This decreases the absorbing capacity of the wheel. Thus decreases the efficiency of the wheel. Different purge
Pf b 2
b 2 a 2
2 2
3
2
4 2b
angle can be analyzed based on process velocity and other
a a
parameters to determine the moisture removal capacity and temperature difference effect. The desiccant wheel consists of numerous flow channel from which airflow.
The flow channel hydraulic diameter given by Narayan et al [2011] (12)
4A
D f a 1.0542 0.466
f
2
0.1180
0.1794
a 3
0.043
a 4
b b b b
Pf
Porosity in desiccant,
Volume of pores (Vpores ) Total volume of layer (Vtotal )
(b)
(a)
Volume ratio, Volume of desiccant (Vdesiccant )
Total volume of layer (Vtotal )
Cross sectional area of desiccant layer of a channel,
Mathematical model of desiccant wheel has been derived through making use of fundamental mass and energy conservationequations within the control volume of air and desiccant.

Mass conservation in control volume of air
Applying mass conservation in control volume of air as shown in Figure 2
Rate of change of mass in control volume = inflow outflow
Convective mass
Figure 1: (a) Three sector desiccant wheel, (b) Differential control volume (c) Crosssectional of matrix channel showing desiccant material with substrate.
Flow channel height Flow channel pitch
Upper boundary of sine curve expressed as,
CV of air
Figure 2: Control volume of air for mass conservation
The mass conservation in air can be expressed as:
Convective mass
Applying energy conservation in control volume of air as shown in Figure
Rate of change of stored energy in control volume = inflow outflow

Mass conservation in control volume of desiccant
(1)
Figure 4: Control volume of air for energy conservation
D. Energy conservation in control volume of desiccant
(3)
Applying energy conservation in control volume of desiccant as shown in figure
Figure 3: Control volume of desiccant for mass conservation
Applying mass conservation in control volume of desiccant as shown in Figure 3
Rate of change of mass in control volume = inflow outflow
(2)

Energy conservation in control volume of air
The rate of change of stored energy in control volume = inflowoutflow
Figure 5: Control volume of desiccant for energy conservation
The energy conservation in the desiccant is given by:
(4)
The governing equations (1) to (4) have five unknown variables in order to solve this set of equations; boundary conditions and some auxiliary equations are required.
E. Auxiliary equations
Humidity ratio and relative humidity are given as
0.62188P 0.62188RH
M.N. Golubovic et al. (3) suggested a new purge sector by dividing the process section and named it as effective purge angle. Effective purge angle is defined as the ratio of an amount of moisture removed from the inlet air per unit time to the amount of heat required to regenerate the desiccant wheel in per unit time. Effective purge angle is hot and humid in comparison to the process section. Process section will have less temperature and less humidity than the effective purge angle. M.N. Golubovic et al. concluded that introducing purge in the process air section decreases the area of the process section. Effective purge angle for the rotary desiccant wheel when hot regeneration is considered, the temperature range should be between 140Â° to 170Â°C with effective purge angle to be around 29.4Â°. Introduction of the purge in the process section decreases the humidity ratio and temperature of the process section, if purge section air is mixed with outside air in the regeneration section it also saves the energy.
Y v d
d P P P
a v a RHd
Pvs
Where is the saturation pressure of water vapour, which can be related as [Zhang et al. (2003)] (11):
Relative humidity and Water content in the desiccant is related by a general sorption isotherm as:
Where is the maximum water content, R is the separation factor that determines the shape of isotherm, RH is the relative humidity.


DIFFERENT RESEARCHERS WORK ON INCLUSION OF
PURGE SECTOR IN DESICCANT WHEEL
Figure 6: Desiccant wheel with purge sector (3)
Figure 7: Desiccant wheel with purge sector for clockwise direction (13)
A.Yadav et. al. (13) investigated that at any rotational speed moisture removal capacity of the desiccant wheel is higher for the anticlockwise rotation of the wheel than the clockwise rotation. In the second case, it was found that at any regeneration temperature moisture removal capacity in the anticlockwise rotational of the wheel was better than that of clockwise rotation. In third case process velocity ranging from
1 m/s to 5 m/sec, it was found that the moisture removal capacity was better in an anticlockwise rotation than the clockwise rotation of the desiccant wheel. In the fourth case with ambient moisture,, the desiccant wheel with anticlockwise rotation shows higher moisture removal than the clockwise rotation.
Figure 8. Variation of moisture elimination with rotation of desiccant wheel for distinctive layout
The above graph indicates that the MRC increases with increase in the rotational speed. However, at low rotational speed there is no significant effect on the MRC at any given purge angle but with an increase in rotational speed purge angle at 5Â° shows higher moisture removal than the other purge angle. Greater the purge angle will affect the regeneration section because there will be the decrease in regeneration area so moisture removal would be less. So in high rotational speed, MRC is high for low purge angle because residence area of hot air is more, whereas for purge
angle 10,15,20 there is less MRC due to the decrease in residence area of the regeneration air.
Figure 9. Graph for moisture removal with process velocity of desiccant wheel for different design
The MRC of all the purge angle decreases with increase in process air velocity because the increase in inlet velocity of air decreases the residence time of air that with the channel matrix or the desiccant surface. Although at process velocity of 1.5 m /s purge angle of 5Â°, shows the higher MRC
compared to the other purge angle. Whereas at higher process velocity does not affect the any purge angle due to reduce in the residence time of inlet air.
Figure 10. Graph for moisture elimination with regeneration temperature of desiccant wheel for distinct layout
The above graph indicates that the MRC increases with an increase of the regeneration temperature for every purge angle. At the temperature range of 60Â° 73Â°c MRC of purge with 5Â° is always high than the other purge angle whereas for 20Â°
Effectiveness , %
purge sector MRC is found to be lowest. The reason behind the drop of MRC with the increase in purge sector is purge sector reduces the area of the regeneration air. Therefore, reduction in the area of regeneration decreases the MRC when we compared with four different purge angle.
100 without purge air
with purge air (same volume flow rate)
90
with purge air (same face velocity)
80
70
60
50
40
30
20
10
0
sensible latent total
Figure 11: variation of effectiveness of purge and without purge in desiccant wheel

COCLUSION
For the rotational speed of the 39 m/sec, it is found that the purge sector with 5Â° has the highest MRC compared to the other sector.
At the process velocity of 1.5 m/sec, purge sector with 5Â° angle produces higher MRC
At regeneration temperature of 60 – 73Â°c again purge sector with 5Â° angle shows better MRC compared to other sector discussed above.
Purge section with same face velocity shows higher effectiveness
REFERENCE
[1]. C. Munters, Munters energy efficient technique – your guarantee, p.8.
[2]. Y. M. Harshe, R. P. Utikar, V. V. Ranade, and D. Pahwa, Modeling of Rotary Desiccant Wheels, Chem. Eng. Technol., vol. 28, no. 12, pp. 14731479, Dec. 2005. [3]. M. N. Golubovic, H. D. M. Hettiarachchi, and W. M. Worek, Evaluation of rotary dehumidifier performance with and without heated purge, Int. Commun. Heat Mass Transf., vol. 7, no. 34, pp. 785795, 2007. [4]. J. Jeong, S. Yamaguchi, K. Saito, and S. Kawai, Performance analysis of fourpartition desiccant wheel and hybrid dehumidification airconditioning system, Int. J. Refrig., vol. 33, no. 3, pp. 496509, May 2010. [5]. R.Narayna Comparative study of different desiccant wheel designs – ScienceDirect. [Online]. Available: https://www.sciencedirect.com/science/article/pii/S135943111100067 6. 2011. [6]. W. Ruan, M. Qu, and W. T. Horton, Mdeling analysis of an enthalpy recovery wheel with purge air, Int. J. Heat Mass Transf., vol. 55, no. 17, pp. 46654672, Aug. 2012. [7]. Yadav, ANALYSIS OF DESICCANT WHEEL WITH PURGE SECTOR FOR IMPROVING THE PERFORMANCE USING AMATHEMATICAL MODEL, Int. J. AirCond. Refrig., vol. 22, no. 01, p. 1450004, Mar. 2014.
[8]. Yadav and L. Yadav, Comparative performance of desiccant wheel with effective and ordinary regeneration sector using mathematical model, Heat Mass Transf., vol. 50, no. 10, pp. 14651478, Oct. 2014 [9]. L.yadav and A.yadav Mathematical investigation of purge sector angle for clockwise and anticlockwise rotation of desiccant wheel – ScienceDirect. [Online]Availablehttps://www.sciencedirect.com/science/article/pii/S135943111501109 6. [Accessed: 24Mar2018].
[10]. L. Yadav and A. Yadav, Effect of different arrangements of sector on the performance of desiccant wheel, Heat Mass Transf., vol. 54, no. 1, pp. 723, Jan. 2018. [11]. Zhang, X.J., Dai, Y.J. and Wang, R.Z., 2003, A simulation study of heat and mass transfer in a honeycombed rotary desiccant dehumidifier, Applied Thermal Engineering, Vol. 23, pp. 9891003 [12]. Narayanan, R., Saman, W.Y., White, S.D. and Goldsworthy, M., 2011, Comparative study of different desiccant wheel designs, Applied Thermal Engineering, Vol. 31, pp. 16131620. [13]. A.YADAV "ANALYSIS OF DESICCANT WHEEL WITH PURGE SECTOR FOR IMPROVING THE PERFORMANCE USING AMATHEMATICAL MODEL" , International Journal of Air
Conditioning and Refrigeration Vol. 22, No. 1 (2014) 145000
[14]. Wei Ruan , Ming Qu , W. TravisHorton "Modelling analysis of an enthalpy recovery wheel with purge air", International Journal of Heat and Mass Transfer, Volume 55, Issues 1718, August 2012, Pages 46654672NOMENCLATURE
SYMBOLS USED
[] Total cross sectional area of a channel
[] Cross sectional area of desiccant layer
[] Cross sectional area of flow passage of one channel

(J/kg K) Specific heat at constant pressure

(J/kg K) Specific heat of liquid water

(J/kg K) Specific heat of water vapour

(J/kg K) Specific heat of dry air

(J/kg K) Specic heat of substrate (matrix material)

D [m] Diameter of desiccant wheel
[] Hydraulic diameter of flow passage of one channel
 [] Surface diffusion coefficient
 [J/kg] Latent heat of vaporization
 [kg/m2s] Mass transfer coefficient
 [W/m2K] Convective heat transfer coefficient
 [W/m K] Thermal conductivity
 [m] Wheel Length
 [rph] Rotational speed
 [Pa] Pressure
 [m] Perimeter of flow passage of one channel
 [ ] Temperature difference of process air
 [J/kg] Heat of adsorption
 [Sec] Time
 [ ] Temperature
 [m/s] Velocity
 [kg kgadsorbent1] Water content in desiccant

[kg kg1] Humidity ratio of the air
Greek symbols
 [kg/m3] Density

Thermal diffusivity

Porosity

Fraction Angle
 [m] Channel Wall Thickness

Volume Ratio
Subscripts
Air

ad Adsorbent

Desiccant

Dry Air

Flow Passage

m Matrix Material

Process Air

Regeneration Air

Vapour