1. Projects
Projects
Intended for
Northumbria University Newcastle
Student no.
W12001941
Date
18th
May 2016
Word Count
18512
REPORT 3 – MECHANICAL
SPECIALIST ZONE –
SWIMMING POOL SPACE

2. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
CONTENTS
1. Executive summary 1
2. Introduction 2
3. Case Study 4
3.1 Ventilation and Air Conditioning Analysis 4
3.2 Heating Analysis 5
3.3 Conclusion 5
4. Calculation of Winter Design Load 6
4.1 Infiltration 6
4.2 Heat Loss 7
4.3 Summary of Winter Design Loads 9
5. Calculation of Summer Design Loads 10
5.1 Solar Gain Calculation 10
5.2 Internal Gain Calculation 10
5.3 Fabric Heat Loss 11
5.4 Infilttation Loss 11
5.5 Summary of Summer Design Loads 12
6. Calculation of POOL DESIGN Loads 13
6.1 Latent Gain Calculation 13
6.2 Condensation Gain Calculation 17
6.3 Summary of Pool Design Loads 19
7. Ventilation and Air Conditioning Design 20
7.1 Fresh Air Requirement 21
7.2 Winter Design 21
7.3 Summer Design 23
7.4 Air Handling Unit Selection 31
8. Domestic Water Services Design 34
8.1 Pool Water Quality 34
8.2 Disinfection 34
8.3 Ph Value 34
8.4 Pool Water requirements calculation 35
8.5 Fresh Water Requirement Calculation 36
8.6 Balance Tank Sizing 37
8.7 Plate Heat Exchanger Sizing 38
8.8 Shower Water Requirements Calculation 40
8.9 Hot Water Calorfier Sizing 41
9. Heating Design 43
9.1 Trench Heating Design 43
9.2 Underfloor Heating Design 46
9.3 Boiler Sizing 47
10. Drawings 48
10.1 Heating and Domestic Water Services Schematic 48
10.2 Heating and Domestic Water Services Distribution Layout 49
10.3 Ventilation and Air Conditioning Services Distribution Layout 50
11. Futher Design Considerations 51
12. Bibliography 52
13. Appendicies 53
13.1 Air Handling Unit Manufactuers Data 53
13.2 Trench Heating Manufactuers Data 55
13.3 Hot Water Calorfier Manufactuers Data 57

3. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
TABLES
Table 1 - Design Conditions for Swimming Pool Space agreed upon with Client............................................3
Table 2 - Finalised Fabric Performance Values..........................................................................................7
Table 3 - Calculation of Total Fabric Surface ............................................................................................8
Table 4 - Total Fabric Surface with Corresponding Thermal Resistance........................................................8
Table 5 - Total Winter Fabric Heat Loss...................................................................................................9
Table 6 - Total Internal Sensible Gain Calculation................................................................................... 10
Table 7 - Total Summer Fabric Heat Loss .............................................................................................. 11
Table 8 - Pool Space Design Requirements............................................................................................ 20
Table 9 - Initial Winter Design Requirements for Swimming Pool Space .................................................... 21
Table 10 - Initial Summer Design Requirements for Swimming Pool Space................................................ 23
Table 11 - Existing quanitites of Metals present in incoming water supply from Southern Waters ................. 35
Table 12 - Pool Design Requirements based on Client request ................................................................. 35
Table 13 - Pool Design Requirements from BSI guide to management of public swimming pools .................. 35
Table 14 - Comparison of calculated Turnover Rate with the recomended Turnover Rate from BS Design of
Swimming Pools Guide ....................................................................................................................... 36
Table 15 - Peak Flow Requirements calculation for Showers within Swimming Pool Space (Standards, 2006) 40
Table 16 - Trench Heating System Output comparison with Glass Facade Heat Loss ................................... 45
Table 17 - Boiler Selection for Swimming Pool Space.............................................................................. 47

4. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
FIGURES
Figure 1 - South East Rendition of Swimming Pool Space ..........................................................................2
Figure 2 - Internal Rendition of Swimming Pool Space ..............................................................................2
Figure 3 - Graph illustrating the Percentage Occupancy during the day within the Swimming Pool Space ........3
Figure 4 - London Aquatics Pool Area......................................................................................................4
Figure 5 - Mechanical Services to London Aquatics Centre.........................................................................4
Figure 6 - Illustration of Heat loss through Swimming Pool Space Construction............................................6
Figure 7 - Swimming Pool Space diemensions..........................................................................................7
Figure 8 - Normalised activity factor for evaporation from indoor swimming pools acquired from W.P.Jones
(1997).............................................................................................................................................. 15
Figure 9 - Reistance Values and Design Conditions for Glass Facade in Pool Space ..................................... 18
Figure 10 - Illustration of Psychometric Chart showing Condensation occurance......................................... 19
Figure 11 - Distribution of Ventilation and Air Conditioning Design within Swimming Pool Space .................. 20
Figure 12 - Air Handling Unit Diagram to be used for Supplying Swimming Pool Space ............................... 21
Figure 13 – Illustration of the Psychometric Process during the Winter Conditions ..................................... 23
Figure 14 - Determing Off coil condition from use of SPC Coils software.................................................... 24
Figure 15 - Illustration of the Psychometric Process during Summer Conditions ......................................... 25
Figure 16 - Revised Off coil condition confirmed with the use SPC Coils software........................................ 26
Figure 17 - Revised Ilustraiition of the Psychometric Process during Summer Conditions............................. 27
Figure 18 - Example of Sized Air Handling Unit System for Swimming Pool Space ...................................... 31
Figure 19 - Illustration of Daytime Operation during Winter Months.......................................................... 32
Figure 20 - Illustration of Daytime Operation during Cooler Summer Months ............................................. 32
Figure 21 - Illustration of Daytime Operation during Warmer Summer Months........................................... 32
Figure 22 - Illustration of Night Time (Pool Unoccupied) Operation........................................................... 33
Figure 23 - A simple schematic of the proposed design of the pool water provision..................................... 37
Figure 24 - Nomogram for determing the size of the required Balance Tank aquired from CIBSE Guide G ..... 38
Figure 25 - First Heat Exchanger Design Requirement ............................................................................ 38
Figure 26 - Second Heat ExchangerDesign Requirement ......................................................................... 39
Figure 27 - Shower Location within Swimming Pool Space....................................................................... 40
Figure 28 - Indicative Heating Pipework distribution for Swimming Pool Space........................................... 41
Figure 29 - Example of Hot Water Calorfier to be used to supply Hot Water to Showers
(Hamworthheating.co.uk) ................................................................................................................... 41
Figure 30 - Example of Electric Hot Water Calofier to be used to supply hot Water to showers
(Hamworthyheating.co.uk).................................................................................................................. 42
Figure 31 - Evaporation occurrence within the Pool Space ....................................................................... 43
Figure 32 - Illustration of how Trench Heating System offsets Glass Facade Heat Loss................................ 43
Figure 33 - Trench Heating System Diemension and Location within Swimming Pool Space ......................... 45
Figure 34 - Rendition of Trench Heating location in Swimming Pool Space................................................. 46
Figure 35 - Underfloor Heating Construction.......................................................................................... 46
Figure 36 - Swimming Pool space indicative underfloor heating area ........................................................ 47

5. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
1
1. EXECUTIVE SUMMARY
This report will analyse the requirements of a specialist zone to be selected within the Hotel project. The
selection of the specialist zone will depend on the complexity involved in providing the system provision
for this space. The complexity will involve how the systems will be provided to the designated space as
well as the condition of the space in question for example high latent gain or abnormal design conditions
and so on.
The specialist zone has been selected to be the swimming pool space within the Hotel project. The
reasons behind the selection of this zone is to provide a simple system provision with good control to
achieve its design conditions despite the abnormal design conditions and high latent gain present within
the space.
The system provision within the Swimming pool space will include the ventilation and air conditioning
design, heating and domestic water services to the space. The controls involved with the systems will also
be analysed to ensure that maximum control is available on demand for the systems designed for this
space. An analysis of the swimming pool loads will be analysed carefully to ensure that the systems
provided will be able to handle the loads with the swimming pool space to provide the best possible design
conditions.
The calculation procedures to determine the required plant equipment to provide the systems designed
within the space will be compared to different calculation procedures such as BSRIA Guides and
manufactures data to ensure the accuracy and reliability of the results obtained can be justified
accordingly. After completion of the system provision to the swimming pool space, a further design
consideration will be analysed to ensure that no stones have been left unturned about providing the best
design approaches available for the swimming pool space.

6. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
2
2. INTRODUCTION
This report will propose various mechanical services to the Swimming Pool space to provide the relevant
heating, cooling, ventilation, domestic services as well as drainage systems. Through a report the
provision of these systems will go under thorough analysis by comparing the acquired results with the
manual calculations provided with other calculations carried out such as BSRIA Rule of Thumb, IES VE and
other sources and guides.
The Swimming Pool space has been decided to act upon its own as supposed to work with the rest of the
Hotel building. The benefits of making this decision is it lets the Swimming Pool Space have its own
working hours and requirements compared to sharing the loads with the other spaces in the buildings.
This will also mean the Swimming Pool Space plant requirements will be only supplying to the Pool space,
which gives the design of the systems the flexibility it requires to provide the various system
requirements needed in the most efficient and cost saving method.
Figure 1 - South East Rendition of Swimming Pool Space
Figure 2 - Internal Rendition of Swimming Pool Space
Figures 1 & 2 give an illustrated picture of the space where the mechanical services will be applied. The
Space as shown. If there is a large section of glazing on the two external walls of the space where it is
predicted that there will be a rather large amount of heat loss passing through the glazing construction.
This will be analysed further as well as the heat loss experienced through the other fabric of the Pool
Space later on within this report.
The mechanical systems that will be sized for the Swimming Pool space will need to be able to modulate
constantly through the day due to the requirements of the Swimming Pool space varying as the day
progresses. Figure 3 provides an illustrative idea of how the Swimming Pool Space will vary its mechanical
requirements based on the occupancy of the Space during a typical day as shown.

7. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
3
Figure 3 - Graph illustrating the Percentage Occupancy during the day within the Swimming Pool Space
From the graph produced in figure … this illustrates how the occupancy within the pool space will
indicatively be during the day. The occupancy profile demonstrates that there will be two predicted peak
points during the day whilst maintaining base loads of 20% during operation hours of the pool between
04:00am and 22:00pm. It should be also noted that the mechanical systems sizing will need to take into
account heat up periods and turn down periods as shown in the graph above the hours where there is not
occupancy present is from 22:00pm to 04:00am, which results in a 6 hour periods where no requirements
are needed.
The swimming pool space is intended to be designed to tight design conditions to be able to maintain the
internal environment of the pool as controllable as possible for the client as well as efficiently. In table …
can be found the design conditions and occupancy details as set out by the client, which needs to be
designed to through this report as follows below.
Table 1 - Design Conditions for Swimming Pool Space agreed upon with Client
Air Temperature
(°C)
Water
Temperature
(°C)
Occupancy (P)
Fresh Air
Requirement
(l/s/m2
)
Swimming Pool
Space
29 27 10 10
The above table showing the clients set design conditions for the Swimming Pool space will be used as a
baseline of data for sizing the relevant mechanical services accordingly aiming to achieve these design
conditions at all time whilst maintain efficiency and control throughout. The values obtained within the
table have been acquired from CIBSE Guides and British Standards for Swimming Pool design. The
conditions set out within the table are to be maintained during the summer and winter periods for
ultimate thermal comfort.
The relevant systems that will need to be designed for the swimming pool space are as follows:
 Heating Design
 Cooling Design
 Domestic Water Services Design
 Above Ground Drainage Design
 Filtration Design
The relevant systems as outlined above will require additional calculations to determine the correct loads
that will be based upon when finalising the relevant system selection. The manual calculations undertaken
will go through comparison of other calculation processes such as BSRIA Guides and results obtained from
IES VE software to discuss the differences or similarities between results.
0%
10%
20%
30%
40%
50%
60%
70%
80%
90%
100%
00:00
01:00
02:00
03:00
04:00
05:00
06:00
07:00
08:00
09:00
10:00
11:00
12:00
13:00
14:00
15:00
16:00
17:00
18:00
19:00
20:00
21:00
22:00
23:00
PercemtageOccupancy(%)
Time (hr:mm)

8. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
4
3. CASE STUDY
A case study will be analysed with regards to the swimming pool design to provide a general knowledge of
the type of systems and design approach that can be made to the final swimming pool design within this
project. The case study that will be analysed is the London Aquatics Centre built for the Olympics during
the 2012 games. The centre accommodates 2500 spectators making it one of the largest swimming
venues in the UK. The London Aquatics Centre will be chosen as a case study to analyse the swimming
pool design as the centre’s innovative, eco-friendly building services design also provides a lasting energy-
efficient facility for the nation as stated by (M.Stych & H.But 2012).
Figure 4 - London Aquatics Pool Area
The London Aquatics Centre will be analysed for the Ventilation, Heating and Domestic Water Services
supply to this application as the knowledge gained can be transferred into applying towards the hotel
project’s swimming pool design.
3.1 Ventilation and Air Conditioning Analysis
The London Aquatics centre provided various initial methods of providing ventilation and air conditioning
systems to the pool space however many design risks arose whilst applying these systems to the space.
To reach the required design conditions within the pool space there was an inherent instability in the air
flow patterns, which gave rise to draughts and ultimately discomfort as stated by (M.Stych & H.But 2012).
This design risk will be analysed thoroughly within the hotel design of the swimming pool space as the
inherent instability in the airflow patterns may be extensive for when being applied to a relatively smaller
space in comparison with the London Aquatics Centre.
The London Aquatics Centre however found a solution where a provision of low velocity supplies system at
poolside level relying on natural convection within the hall. As the pool water surface absorbs heat, it
draws supply air down, which is then extracted via the pool drainage channels along the pool edge as
stated by (M.Stych & H.But 2012). This also helps keep contaminated air at the pool surface and limits
migration to other areas This design approach will be considered with the Hotel where it seems imperative
to provide a ventilation and air conditioning design which will not only provide design comfort for the
occupants within the pool space but also provide a healthy environment with the provision of minimising
the risk of developing contaminants and other health related risks.
Figure 5 - Mechanical Services to London Aquatics Centre
To provide such design conditions to the hotel pool space, specialised air handling units will be required as
used in the London Aquatics Centre, which will include liaising with Specialists Swimming Pool Design
manufactures. Within the air handling units plate heat exchangers will be required to maximise the energy
efficiency of the system by extracting the heat energy from the return air from the Hotel Pool Space and
supplying it to the Hotel Pool Space with heat recovered fresh air. The Plate Heat exchanger used in the
London Aquatics Centre was able to achieve a heat recovery efficiency of up to 84%. The AHU control
adjusts the fresh air ratio into the air system to control the space humidity level as stated by (M.Stych &
H.But 2012).

9. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
5
The supply and extract ductwork in the London Aquatics Centre was designed in such a way that the low-
velocity warm air supply louvres provide comfortable conditions in the pool surrounds, while the self-
balanced, low-level air extraction service limits the build-up and spread of moisture and pollutants as
stated by (M.Stych & H.But 2012). Within the Hotel Pool space, the supply ductwork will be initially
located above the external ductwork at High level to promote a similar air flow pattern as that achieved
within the London Aquatics Centre as it was proved to be affective.
The supply condition into the Hotel Pool space will be based on Swimming Pool Regulations for design
comfort however taking into consideration the temperature allowed for by the London Aquatics Centre to
be 30°C which is so that buoyancy is reduced which provides a stable atmospheric condition within the
pool space.
3.2 Heating Analysis
During the pool operation hours the occupants, using the Hotel Pool space will be creating additional
amounts of moisture onto the poolside areas as expected from the transition from showers to pool space
as well as the procedure of leaving the pool space to the dry changing rooms. The expected moisture on
the poolside areas can results in a health and safety hazard due to slippery surfaces as well as provides
discomfort to the occupants when using the poolside area.
The London Aquatics Centre has a similar situation to that created in the Hotel Pool space therefore the
solution was to provide an underfloor heating system to the poolside area. This provides comfort for the
swimmers and radiant heat to offset the radiant losses to surrounding surfaces as stated by (M.Stych &
H.But 2012). Therefore, the underfloor heating system will be applied to the Hotel space following the
design benefits outlined by the use in the London Aquatics Centre. Another benefit is that by warming the
low velocity supply air, encourages upwards air flow, thereby reducing the risk of air recirculation by the
pool surround air extraction which was also experienced within the London Aquatics Centre as stated by
(M.Stych & H.But 2012).
The Hotel Pool Space consists of a large glazed façade which is similar to the London Aquatics Centre
where large amounts of heat loss was experienced and condensation build up through the operation of the
pool space. Therefore to offset these design issues it was treated separately by the use of natural
convectors fed from the heating hot water system. Along the perimeter there was a trench heater system
to offset heat losses, and limit condensation build up. On the taller façade elements, the mullions and
transoms have integrated hot water pipes embedded to reduce the risk of condensation and limit down
draughts. Each curtain wall is fed by a dedicated variable temperature circuit that is weather
compensation control as stated by (M.Stych & H.But 2012).
With regards to the Hotel Pool Space utilising a similar trench heating system design will be analysed
further within this report as appose to if condensation actually occurs on the glazing façade of the space
and whether the heat loss experienced through the glazing is worth designing for.
3.3 Conclusion
From the analyzed case study based on the London Aquatics Centre’s building services provision to the
pool space many design considerations have been acquired. The acquired design consideration will need
to be analyzed further to see if they fit well the Hotel Pool Space as many differences between the Pool
Space applications can vary the design outcome. Factors such as location, design conditions and volume
of the Pool Space can play a limiting factor to the final design.
However if the design considerations are applicable the Hotel Pool Space will be considered a well-
designed space as recognized by BREEAM for the London Aquatics Centre which provided a 16.5% savings
in carbon using efficiency measures alone, before applying renewable energy sources. Therefore applying
the design considerations outlined within this section of the report is expected to improve the Hotel Pool
Space’s energy efficiency.

10. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
6
4. CALCULATION OF WINTER DESIGN LOAD
The heat loss through the swimming pool space will need to be determined, as it will need to be offset by
additional heating provided to keep the space in design conditions. The following calculations will be
undertaken to determine the total heat loss variables for the Swimming Pool Space.
Indicative illustrations of the possible surfaces where heat will be lost through the fabric of the Swimming
Pool Space are as shown in Figure 6.
As shown in Figure 6 Heat loss is experienced in all facades of swimming pool space therefore a heat loss
calculation process will be required to determine the total heat loss load is to size the required heating
strategy to offset the heat loss experienced in this space. The calculation procedures carried out is based
on the calculation procedure recommended by BSRIA Guide to HVAC Calculations, (BSRIA, 2007).
4.1 Infiltration
Infiltration is a key area where we have to accurately measure the rate of outside air entering the space
and the rate of internal air dissipating from the internal space to the outside. Air can enter the space
through the buildings cracks and imperfections of when being built which can depend on the quality of the
build. The main cause to this is usually due to the air pressure difference, which is caused by wind
pressure or temperature differences. Compensating the design against natural infiltration at this early
stage of the design is key as it can cause additional heat loss through winter conditions as air enters the
space at outdoor conditions, and in summer, it can cause additional heat gain.
Initial Calculations:
𝐼𝑛𝑡𝑒𝑟𝑛𝑎𝑙 𝑆𝑢𝑟𝑓𝑎𝑐𝑒 𝐴𝑟𝑒𝑎 (𝑆)(𝑚2) = 671.406 𝑚2
𝑉𝑜𝑙𝑢𝑚𝑒 𝑜𝑓 𝑆𝑝𝑎𝑐𝑒 (𝑚3) = 1057.68 𝑚3
𝐴𝑖𝑟 𝐿𝑒𝑎𝑘𝑎𝑔𝑒 𝐼𝑛𝑑𝑒𝑥 𝑄50/𝑆 (𝑚3
/(ℎ. 𝑚2)) = 5.0 (𝑚3
/ℎ)/𝑚2
𝑡𝑖𝑛𝑠𝑖𝑑𝑒 = 29 ℃
𝑡 𝑜𝑢𝑡𝑠𝑖𝑑𝑒 = −2.7 ℃
The main output is to determine the infiltration rate in air changes per hour from design purposes which
will be defined as ‘I’ as well as the heat loss due to infiltration which will be shown as Qv (kW). Therefore
using the following equation, we can determine the infiltration rate using the initial calculated values as
follows:
𝑰 =
𝟏
𝟐𝟎
×
𝑺
𝑽
×
𝑸 𝟓𝟎
𝑺
Where:
1
20
= 𝑡ℎ𝑒 𝑎𝑝𝑝𝑙𝑖𝑒𝑑 𝑎𝑖𝑟 𝑙𝑒𝑎𝑘𝑎𝑔𝑒 𝑖𝑛𝑑𝑒𝑥 𝑡𝑜 𝑎𝑝𝑝𝑟𝑜𝑥𝑖𝑚𝑎𝑡𝑒 𝑡ℎ𝑒 𝑎𝑖𝑟 𝑖𝑛𝑓𝑖𝑙𝑡𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑖𝑛 𝑎𝑖𝑟 𝑐ℎ𝑎𝑛𝑔𝑒𝑠 𝑝𝑒𝑟 ℎ𝑜𝑢𝑟
𝑆
𝑉
= 𝑇ℎ𝑒 𝑠𝑢𝑟𝑓𝑎𝑐𝑒 𝑡𝑜 𝑣𝑜𝑙𝑢𝑚𝑒 𝑟𝑎𝑡𝑖𝑜 𝑡𝑜 𝑏𝑒 𝑎𝑝𝑝𝑙𝑖𝑒𝑑 𝑡𝑜 𝑔𝑖𝑣𝑒 𝑎𝑛 𝑎𝑝𝑝𝑟𝑜𝑥𝑖𝑚𝑎𝑡𝑒 𝑎𝑖𝑟 𝑖𝑛𝑓𝑖𝑙𝑡𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑖𝑛 𝑎𝑖𝑟 𝑐ℎ𝑎𝑛𝑔𝑒𝑠 𝑝𝑒𝑟 ℎ𝑜𝑢𝑟
𝑄50
𝑆
= 𝑇ℎ𝑒 𝑎𝑖𝑟 𝑙𝑒𝑎𝑘𝑎𝑔𝑒 𝑖𝑛𝑑𝑒𝑥
Figure 6 - Illustration of Heat loss through Swimming Pool Space Construction
Internal Temperature
29°C
Difference in
Temperature to be
31.7°C
Difference in
Temperature to be
10°C

11. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
7
Therefore:
𝐼 =
1
20
×
671.406
1057.68
× 5.0
𝑰 = 𝟎. 𝟏𝟓𝟗 𝒂𝒄𝒉
Now that the infiltration rate has been determined through, the fabric construction of the Swimming Pool
Space the fabric heat loss needs to be determined to determine the final heating load required for this
space.
4.2 Heat Loss
To fully size a heating system that will compensate for the total heat loss of the space, the heat loss
through the fabric needs to be also calculated alongside the infiltration loss. The heat loss calculation is
dependent upon the following factors:
 Infiltration rate to the space
 Dimensions of the surfaces of the space
 Thermal transmittance of the space’s building elements
 External temperature
 Internal temperature of the space
The obtained design information is as follows:
 Infiltration Rate – This has been calculated earlier in this report which is 0.159 ach
 The inside dry resultant design temperature is to be 29 °C
 The outside dry resultant temperature is -2.7 °C
To determine the fabric heat loss through the constructions the fabric performances of the constructions
used within the Swimming Pool space are as shown in Table 2.
Table 2 - Finalised Fabric Performance Values
Ground
Floor
Roof Door Partition
External
Wall
Glazing
Finalised
Fabric
Performance
0.19 0.19 2.63 1.31 0.26 1.65
To determine the fabric heat loss the dimensions of each of the facades constructions are needed which
can be found in Figure 7. Which have the dimensions of the constructions facades of the pool space, which
the calculation of each of the constructions surface area will be determined.
Figure 7 - Swimming Pool Space dimensions

12. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
8
Following the produced dimensions for each of the façade within the pool space, the calculation of the
internal surface area for each construction within the Pool Space can be found in Table 3.
Table 3 - Calculation of Total Fabric Surface
Ground
Floor
Roof Door Partition
External
Wall
Glazing
North Face - - - -
(13.663m ×
6.0m) –
55.59m2
=
26.388m2
(10.9m ×
5.1m) =
55.59m2
East Face - - - -
(12.902m ×
6.0m) –
55.59m2
=
21.882m2
(10.9m ×
5.1m) =
55.59m2
South Face - -
(1.5m ×
2.1m) +
(0.91m ×
2.1m) =
5.082m2
(6.613 ×
6.0) – 1.911
m2
) + (3.0 ×
6.0) – 3.171
m2
) =
52.596 m2
(4.05m ×
6.0m) =
24.3m2
-
West Face - - -
(7.753m ×
6.0m) +
(5.15m ×
6.0m) =
77.418m2
- -
Ceiling Face -
(13.663m ×
12.902m) =
176.28m2
- - - -
Ground Face
(13.663m ×
12.902m) =
176.28m2
- - - - -
Total 176.28m2
176.28m2
5.082m2
130.014m2
72.57m2
111.18m2
Σ(A) = 671.406m2
From the produced table the total surface area of the constructions have been calculated which will be
used later on within this section to dtermine the total heating load for the Pool space. The corresponding
thermal resistance values for each of the constructions within the Pool space now needs to be calculated
which is shown as follows in Table 4.
Table 4 - Total Fabric Surface with Corresponding Thermal Resistance
Ground
Floor
Roof Door Partition External Wall Glazing
North Face - - - -
(0.26W/m²K
× 26.39m²)
= 6.86W/K
(1.65W/m²K
× 55.59m²) =
91.72W/K
East Face - - - -
(0.26W/m²K
× 21.88m²)
= 5.69W/K
(1.65W/m²K
× 55.59m²) =
91.72W/K
South Face - -
(2.63W/m²K
× 5.08m²)
=
13.36W/K
(1.31W/m²K
× 52.60m²)
=
68.91W/K
(0.26W/m²K
× 24.30m²)
= 6.32W/K
-
West Face - - -
(1.31W/m²K
× 77.42m²)
=
101.42W/K
- -
Ceiling Face -
(0.19W/m²K
×
176.28m²)
=
33.49W/K
- - - -
Ground
Face
(0.19W/m²K
×
176.28m²)
=
33.49W/K
- - - - -
Σ(AU) = 6204.03 W/K
The final total surface area with correspnding thermal resistance values for each construction has now
been calculated as well as the total surface area corresponding thermal reisstance figure for all
constructions which will be used later on in the fabric heat loss calculation as follows.
To determine the final heat loss value for each of the constructions outlined, the following table uses the
calculated corresponding thermal resistances value and multiplies it by the difference in temperature
between the adjacent spaces to come to the final heat loss value for each of the constructions used within
the Pool space

13. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
9
Table 5 - Total Winter Fabric Heat Loss
Ground
Floor
Roof Door Partition External Wall Glazing
North Face - - - -
(6.86 W/K ×
ΔT 31.7°C) =
217.462W
(91.72 W/K ×
ΔT 31.7°C) =
2907.524W
East Face - - - -
(5.69 W/K ×
ΔT 31.7°C) =
180.373W
(91.72 W/K ×
ΔT 31.7°C) =
2907.524W
South Face - -
(13.36 W/K
× ΔT 10°C)
= 133.60W
(68.91 W/K
× ΔT 10°C)
= 689.10W
(6.32 W/K ×
ΔT 31.7°C) =
200.344W
-
West Face - - -
(101.42 W/K
× ΔT 10°C)=
1014.20W
- -
Ceiling Face -
(33.49 W/K
× ΔT 10°C)
= 334.90W
- - - -
Ground
Face
(33.49 W/K
× ΔT °C) =
334.90W
- - - - -
Σ(Fabric Heat Loss) = 8919.927 W
From the produced table above the final fabric heat loss has been calculated to be 8.92 kW. During winter
conditions, the other heat loss that will be experienced would be the infiltration heat loss. Using the
calculated air change rate of the Swimming Pool space the infiltration heat loss during winter conditions
can be confirmed as follows.
𝑄 𝑠𝑖 =
𝑛 × 𝑉 × (𝑡 𝑜 − 𝑡 𝑟)
3
Where:
𝑄 𝑠𝑖 𝑖𝑠 𝑡ℎ𝑒 𝑖𝑛𝑓𝑖𝑙𝑡𝑟𝑎𝑡𝑖𝑜𝑛 𝑔𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑛 𝑖𝑠 𝑡ℎ𝑒 𝑛𝑢𝑚𝑏𝑒𝑟 𝑜𝑓 𝑎𝑖𝑟 𝑐ℎ𝑎𝑛𝑔𝑒𝑠 𝑝𝑒𝑟 ℎ𝑜𝑢𝑟 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑 𝑡𝑜 𝑏𝑒 0.159 𝑎𝑐ℎ
𝑉 𝑖𝑠 𝑡ℎ𝑒 𝑣𝑜𝑙𝑢𝑚𝑒 𝑜𝑓 𝑡ℎ𝑒 𝑠𝑝𝑎𝑐𝑒 𝑡𝑜 𝑏𝑒 1057.68 𝑚3
𝑡 𝑜 𝑖𝑠 𝑡ℎ𝑒 𝑜𝑢𝑡𝑠𝑖𝑑𝑒 𝑎𝑖𝑟 𝑐𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛 𝑑𝑢𝑟𝑖𝑛𝑔 𝑤𝑖𝑛𝑡𝑒𝑟 𝑡𝑜 𝑏𝑒 − 2.7°𝐶
𝑡 𝑟 𝑖𝑠 𝑡ℎ𝑒 𝑟𝑜𝑜𝑚 𝑎𝑖𝑟 𝑐𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛 𝑡𝑜 𝑏𝑒 29 °𝐶
Therefore:
𝑄 𝑠𝑖 =
0.159 × 1057.68 × (−2.7 − 29)
3
𝑄 𝑠𝑖 = −1833.07 𝑊𝑎𝑡𝑡𝑠
Therefore, to summarise from the provided infiltration loss associated with the swimming pool space,
there is a total heat loss from the fabric heat loss and calculated infiltration loss of 1.83 kW the total
winter design load can be calculated as follows.
4.3 Summary of Winter Design Loads
Following the calculation processes as shown above within this section of the report, the final winter
Design loads associated with the pool space have been calculated. The loads calculated will be used as
part of the winter design for the Air handling unit design later on in this report. A final summary of the
calculated Winter design loads are shown as follows below.
𝑻𝒐𝒕𝒂𝒍 𝑾𝒊𝒏𝒕𝒆𝒓 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 𝑳𝒐𝒂𝒅 = 𝑭𝒂𝒃𝒓𝒊𝒄 𝑯𝒆𝒂𝒕 𝑳𝒐𝒔𝒔 + 𝑰𝒏𝒇𝒊𝒍𝒕𝒓𝒂𝒕𝒊𝒐𝒏 𝑳𝒐𝒔𝒔
Where:
𝑇𝑜𝑡𝑎𝑙 𝑊𝑖𝑛𝑡𝑒𝑟 𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝐿𝑜𝑎𝑑 𝐿𝑜𝑠𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝐹𝑎𝑏𝑟𝑖𝑐 𝐻𝑒𝑎𝑡 𝐿𝑜𝑠𝑠 𝑙𝑜𝑎𝑑 𝑡𝑜 𝑏𝑒 8.92 𝑘𝑊
𝐼𝑛𝑓𝑖𝑙𝑡𝑟𝑎𝑡𝑖𝑜𝑛 𝐿𝑜𝑠𝑠 𝐿𝑜𝑎𝑑 𝑡𝑜 𝑏𝑒 1.83 𝑘𝑊
Therefore:
𝑇𝑜𝑡𝑎𝑙 𝑊𝑖𝑛𝑡𝑒𝑟 𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝐿𝑜𝑎𝑑 = 8.92 + 1.83
𝑻𝒐𝒕𝒂𝒍 𝑾𝒊𝒏𝒕𝒆𝒓 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 𝑳𝒐𝒂𝒅 = 𝟏𝟎. 𝟕𝟓 𝒌𝑾
From the calculated total winter sensible load the winter design of the air handling unit for pool space can
be calculated and designed.

14. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
10
5. CALCULATION OF SUMMER DESIGN LOADS
The cooling load calculation is necessary to size the relevant cooling systems needed within the Swimming
Pool Space. To determine the final cooling load, the internal gains experienced within the Swimming pool
space will need to be calculated. The heat gains experienced within the pool space are as follows.
 Solar Gain
 Internal Gains
 Fabric Heat Loss
 Infiltration Loss
To determine the various gains as outlined above, manual calculation processes will be undertaken to
determine these various gains and to ultimately finalise the total heat gain so to size an adequate cooling
system to offset the gains experienced within the Pool Space.
5.1 Solar Gain Calculation
To determine the solar gain within the Bedroom Space, the CIBSE Guide document Design for improved
solar shading control, provides indicative solar gain on the outside of a window values for each orientation
for various locations in table 5.2. The location chosen will be London as it is the closest location to
Southampton where the project is based. The chosen Bedroom space is orientated facing the South
façade so therefore the solar gain value for the South facing orientation will be chosen. The total solar
gain calculation is shown as follows.
𝑸 𝑺𝒐𝒍𝒂𝒓 𝑮𝒂𝒊𝒏 = (𝑺𝒐𝒍𝒂𝒓 𝑮𝒂𝒊𝒏 𝒐𝒏 𝑶𝒖𝒕𝒔𝒊𝒅𝒆 𝒐𝒇 𝑾𝒊𝒏𝒅𝒐𝒘 × 𝑨𝒓𝒆𝒂 𝒐𝒇 𝑮𝒍𝒛𝒊𝒏𝒈) × 𝑮 𝑽𝒂𝒍𝒖𝒆
Where:
𝑄 𝑆𝑜𝑙𝑎𝑟 𝐺𝑎𝑖𝑛 = 𝑇𝑜𝑡𝑎𝑙 𝑆𝑜𝑙𝑎𝑟 𝑔𝑎𝑖𝑛 𝑣𝑎𝑙𝑢𝑒 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑆𝑜𝑙𝑎𝑟 𝐺𝑎𝑖𝑛 𝑜𝑛 𝑂𝑢𝑡𝑠𝑖𝑑𝑒 𝑜𝑓 𝑊𝑖𝑛𝑑𝑜𝑤 𝑡𝑜 𝑏𝑒 355 𝜃𝑆/(𝑊/𝑚2
)
𝐴𝑟𝑒𝑎 𝑜𝑓 𝑔𝑙𝑎𝑧𝑖𝑛𝑔 𝑡𝑜 𝑏𝑒 111.18 𝑚2
𝐺 𝑉𝑎𝑙𝑢𝑒 𝑜𝑓 𝑔𝑙𝑎𝑧𝑖𝑛𝑔 𝑡𝑜 𝑏𝑒 0.3 𝜃𝑆
Therefore:
𝑄 𝑆𝑜𝑙𝑎𝑟 𝐺𝑎𝑖𝑛 = (355 × 111.18) × 0.3
𝑸 𝑺𝒐𝒍𝒂𝒓 𝑮𝒂𝒊𝒏 = 𝟏𝟏𝟖𝟒𝟎. 𝟔𝟕 𝑾
The G Value used in this calculation has been determined from the stage 2 report where an analysis of the
required G Value needed for the glazing to improve the cooling and heating requirements for the space
which resulted in having a lower G Value. Now that the solar gain value has been determined to be 11.84
kW.
5.2 Internal Gain Calculation
The calculation of internal gain can be determined by analysing the heat gains within the pool space that
do not respire or produce moisture. These types of gains tend to fall under the following categories.
 Lighting Loads
 Small Power Loads
 Occupant Loads
To determine these loads the electrical requirements of the space need be analysed. The electrical
requirements will be based on BSRIA Rule of Thumb 5th
Edition, which outlines the lighting, and small
power loads, which can be found as Watts per meters squared values as, outlined as follows.
 Swimming Pool Lighting Loads – 12 W/m2
 Swimming Pool Small Power Loads – 5 W/m2
From the produced watts per meters squared values for the lighting and small power loads within the
Swimming Pool space by BSRIA Rule of Thumb 5th
Edition the table below outlines the final internal loads
within the pool space.
Table 6 - Total Internal Sensible Gain Calculation
Lighting Loads Small Power Loads
CIBSE Guide A (W/m2
) 12 5
Area (m2
) 176.28 176.28
Internal Load (W) 2115.36 881.40
Total Internal Sensible Gain = 2996.76 Watts

15. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
11
From the produced table above the calculated total sensible gain based on CIBSE Guide A Section 6 loads
are shown. Therefore, the additional occupant gain can be added to the total sensible gain load as follows.
The occupant sensible load is based on data provided by CIBSE Guide A table 6.3 where it states that
occupants performing athletic activities produce a sensible gain of 210 Watts. Therefore based on the
Swimming Pool Space having 10 occupants within the space, the occupant’s sensible gain will be
calculated as shown below.
𝑶𝒄𝒄𝒖𝒑𝒂𝒏𝒕𝒔 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 𝑮𝒂𝒊𝒏 (𝑾) = 𝑶𝒄𝒄𝒖𝒑𝒂𝒏𝒕𝒔 (𝑷) × 𝑶𝒄𝒄𝒖𝒑𝒂𝒏𝒕𝒔 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 𝑮𝒂𝒊𝒏 (𝑾/𝒑)
Therefore:
𝑂𝑐𝑐𝑢𝑝𝑎𝑛𝑡𝑠 𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝐺𝑎𝑖𝑛 (𝑊) = 10 × 210
𝑂𝑐𝑐𝑢𝑝𝑎𝑛𝑡𝑠 𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝐺𝑎𝑖𝑛 (𝑊) = 2100𝑊
From the produced occupant sensible gains, the total internal gains experienced within the pool space
during the summer external conditions can be determined.
Furthermore to determining the summer design loads that would be experience with regards to the
swimming pool space, as well as gains experienced losses will also be experience through the fabric and
infiltration through the constructions due to the swimming pool space being conditioned to design
condition s warmer than that outside during the summer periods.
5.3 Fabric Heat Loss
During the summer conditions, externally the swimming pool space will experience heat loss through the
fabric construction due to the swimming pool space being conditioned warmer than the outside conditions.
Therefore, the following calculation process will determine the heat loss experienced through the fabric
construction.
Table … which is acquired from the fabric heat loss calculation process for determining the winter design
loads can be used in determining the fabric heat loss value during the summer external conditions. By
altering, the difference in temperature between the internal space and the external dry bulb temperature
the final fabric heat loss value can be determined as shown.
Table 7 - Total Summer Fabric Heat Loss
Ground
Floor
Roof Door Partition External Wall Glazing
North Face - - - -
(6.86 W/K ×
ΔT 8.4°C) =
57.624W
(91.72 W/K ×
ΔT 8.4°C) =
770.448W
East Face - - - -
(5.69 W/K ×
ΔT 8.4°C) =
47.796W
(91.72 W/K ×
ΔT 8.4°C) =
770.448W
South Face - -
(13.36 W/K
× ΔT 10°C)
= 133.60W
(68.91 W/K
× ΔT 10°C)
= 689.10W
(6.32 W/K ×
ΔT 8.4°C) =
53.088W
-
West Face - - -
(101.42 W/K
× ΔT 10°C)=
1014.20W
- -
Ceiling Face -
(33.49 W/K
× ΔT 10°C)
= 334.90W
- - - -
Ground
Face
(33.49 W/K
× ΔT 10°C)
= 334.90W
- - - - -
Σ(Fabric Heat Loss) = 4206.104 W
The fabric heat loss value determined from the produced table above will not be the only heat loss value
from the pool space. Infiltration will also be experienced during the summer external conditions, which is
calculated as follows.
5.4 Infilttation Loss
The infiltration gain within the pool space will be based upon the infiltration rate calculated earlier on in
this report. Air passes through the fabric in such gaps as cracks or not as well formed laid brick walls into
the internal space at this rate. Therefore, this transition from outside warm air during the summer periods
entering the internal space can be measured by the following calculation to determine the infiltration gain.
𝑸 𝒔𝒊 =
𝒏 × 𝑽 × (𝒕 𝒐 − 𝒕 𝒓)
𝟑

16. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
12
Where:
𝑄 𝑠𝑖 𝑖𝑠 𝑡ℎ𝑒 𝑖𝑛𝑓𝑖𝑙𝑡𝑟𝑎𝑡𝑖𝑜𝑛 𝑔𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑛 𝑖𝑠 𝑡ℎ𝑒 𝑛𝑢𝑚𝑏𝑒𝑟 𝑜𝑓 𝑎𝑖𝑟 𝑐ℎ𝑎𝑛𝑔𝑒𝑠 𝑝𝑒𝑟 ℎ𝑜𝑢𝑟 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑 𝑡𝑜 𝑏𝑒 0.159 𝑎𝑐ℎ
𝑉 𝑖𝑠 𝑡ℎ𝑒 𝑣𝑜𝑙𝑢𝑚𝑒 𝑜𝑓 𝑡ℎ𝑒 𝑠𝑝𝑎𝑐𝑒 𝑡𝑜 𝑏𝑒 1057.68 𝑚3
𝑡 𝑜 𝑖𝑠 𝑡ℎ𝑒 𝑜𝑢𝑡𝑠𝑖𝑑𝑒 𝑎𝑖𝑟 𝑐𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛 𝑑𝑢𝑟𝑖𝑛𝑔 𝑠𝑢𝑚𝑚𝑒𝑟 𝑡𝑜 𝑏𝑒 26.1°𝐶
𝑡 𝑟 𝑖𝑠 𝑡ℎ𝑒 𝑟𝑜𝑜𝑚 𝑎𝑖𝑟 𝑐𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛 𝑡𝑜 𝑏𝑒 30 °𝐶
Therefore:
𝑄 𝑠𝑖 =
0.159 × 1057.68 × (26.1 − 30)
3
𝑸 𝒔𝒊 = −𝟐𝟏𝟖. 𝟔𝟐𝟐 𝑾𝒂𝒕𝒕𝒔
From the produced Infiltration gain calculation it has been determined that during peak conditions during
the summer periods there is an inverse reaction where the swimming pool space experience heat loss
during the summer. This is a result of the internal condition of the space to have a higher dry bulb
temperature than that of the external summer dry bulb temperature.
5.5 Summary of Summer Design Loads
To summarise the total summer design loads to base the summer design of the air-handling unit for the
swimming pool space, a summary of the calculated values have been provided. From the calculated
summer design loads, there is a mixture of gains and losses for the swimming pool space. Therefore, to
determine the final Total Summer design load the calculation process as shown below will determine the
final load to proceed with the design of the Air Handling Unit.
𝑻𝒐𝒕𝒂𝒍 𝑺𝒖𝒎𝒎𝒆𝒓 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 𝑳𝒐𝒂𝒅 = (𝑺𝒐𝒍𝒂𝒓 𝑮𝒂𝒊𝒏 + 𝑰𝒏𝒕𝒆𝒓𝒏𝒂𝒍 𝑮𝒂𝒊𝒏) − (𝑭𝒂𝒃𝒓𝒊𝒄 𝑯𝒆𝒂𝒕 𝑳𝒐𝒔𝒔 + 𝑰𝒏𝒇𝒊𝒍𝒕𝒓𝒂𝒕𝒊𝒐𝒏 𝑳𝒐𝒔𝒔)
Where:
𝑇𝑜𝑡𝑎𝑙 𝑆𝑢𝑚𝑚𝑒𝑟 𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝐿𝑜𝑎𝑑 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑆𝑜𝑙𝑎𝑟 𝐺𝑎𝑖𝑛 ℎ𝑎𝑠 𝑏𝑒𝑒𝑛 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑 𝑡𝑜 𝑏𝑒 11.84 𝑘𝑊
𝐼𝑛𝑡𝑒𝑟𝑛𝑎𝑙 𝐺𝑎𝑖𝑛 ℎ𝑎𝑠 𝑏𝑒𝑒𝑛 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑 𝑡𝑜 𝑏𝑒 5.10 𝑘𝑊
𝐹𝑎𝑏𝑟𝑖𝑐 𝐻𝑒𝑎𝑡 𝐿𝑜𝑠𝑠 ℎ𝑎𝑠 𝑏𝑒𝑒𝑛 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑 𝑡𝑜 𝑏𝑒 4.21 𝑘𝑊
𝐼𝑛𝑓𝑖𝑙𝑡𝑟𝑎𝑡𝑖𝑜𝑛 𝐿𝑜𝑠𝑠 ℎ𝑎𝑠 𝑏𝑒𝑒𝑛 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑 𝑡𝑜 𝑏𝑒 0.22 𝑘𝑊
Therefore:
𝑇𝑜𝑡𝑎𝑙 𝑆𝑢𝑚𝑚𝑒𝑟 𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝐿𝑜𝑎𝑑 = (11.84 + 5.10) − (4.21 + 0.22)
𝑻𝒐𝒕𝒂𝒍 𝑺𝒖𝒎𝒎𝒆𝒓 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 𝑳𝒐𝒂𝒅 = 𝟏𝟐. 𝟓𝟏 𝒌𝑾
From the calculated summer design load, the latent load within the Swimming Pool space needs to be
determined as the pool latent loads will be constant through the year disregarding the conditions outside.

17. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
13
6. CALCULATION OF POOL DESIGN LOADS
A separate calculation process for the pool gains is required, as the loads associated with the pool will
remain constant throughout the year regardless of the external conditions. The only load associated with
the Pool gains will be the latent gains produced which will be analysed as follows. The following pool
design load calculations have been acquired from W.P.Jones Air Conditioning Engineering 5th
Edition,
(Jones, 1973).
6.1 Latent Gain Calculation
The latent gain calculation is particularly important to the Swimming Pool space as the space contains a
lot of water, which is expected to evaporate and produce moisture into the atmosphere within the Pool
space. Other latent gains from the occupants within the pool space as well as the evaporation of the wet
surfaces surrounding the pool space will also be experienced due to the relatively warm air condition of
the space causing evaporation to occur. Therefore, the total latent gain experienced within the pool space
will be determined using the following calculation processes.
6.1.1 Occupant Latent Gain Calculation
The occupant latent gain can be determined by refereeing to CIBSE Guide A table 6.3 where it states the
occupant latent gain when performing Athletic activities produced a latent gain value of 315 Watts.
Therefore using the following calculation the total occupant latent gain can be confirmed as shown below.
𝑶𝒄𝒄𝒖𝒑𝒂𝒏𝒕𝒔 𝑳𝒂𝒕𝒆𝒏𝒕 𝑮𝒂𝒊𝒏 (𝑾) = 𝑶𝒄𝒄𝒖𝒑𝒂𝒏𝒕𝒔 (𝑷) × 𝑶𝒄𝒄𝒖𝒑𝒂𝒏𝒕𝒔 𝑳𝒂𝒕𝒆𝒏𝒕 𝑮𝒂𝒊𝒏 (𝑾/𝒑)
𝑂𝑐𝑐𝑢𝑝𝑎𝑛𝑡𝑠 𝐿𝑎𝑡𝑒𝑛𝑡 𝐺𝑎𝑖𝑛 (𝑊) = 10 × 315
𝑶𝒄𝒄𝒖𝒑𝒂𝒏𝒕𝒔 𝑳𝒂𝒕𝒆𝒏𝒕 𝑮𝒂𝒊𝒏 (𝑾) = 𝟑𝟏𝟓𝟎𝑾
From the determined total occupant latent gain load calculated the other latent gains could be calculated.
The latent gains experienced within the swimming pool area need specific calculation procedures to
determine the final load. Therefore, with the aid of W.P Jones (1997) Air Conditioning Application and
Design 2nd
Edition the following calculation processes can determine the total latent gain produced by the
Pool and the surrounding floor air area due to evaporation.
6.1.2 Pool Water Latent Gain Calculation
Firstly to determine the evaporation rate the following initial design information are outlined as follows
 Pool Space Air Temperature – 29 °C
 Pool Space Humidity – 50%
 Pool water Temperature – 27 °C
 Occupants – 10 Bathers
 Pool Area – 117 m2
Following the produced initial design information as outlined above, the Vapour pressure value
experienced within the Pool space at the Pool space air temperature and Humidity condition need to
acquire with the aid of CIBSE Guide C Section 1-46 where the vapour pressure figures are extracted
below.
 Vapour Pressure @ 29 °C 54% Saturation – 2.203 kPa
 Vapour Pressure @ 29 °C 56% Saturation – 2.283 kPa
As shown above the acquired vapour pressure figures at 29 °C are for 54% and 56% Saturation levels.
Therefore, interpolation will be required to determine the Vapour Pressure value for 55% Saturation levels
as shown below.
𝑉𝑎𝑝𝑜𝑢𝑟 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 @ 29 °𝐶 55% 𝑆𝑎𝑡 = 2.203 𝑘𝑃𝑎 + (
55 − 54
56 − 54
) × (0.08)
𝑽𝒂𝒑𝒐𝒖𝒓 𝑷𝒓𝒆𝒔𝒔𝒖𝒓𝒆 @ 𝟐𝟗 °𝑪 𝟓𝟓% 𝑺𝒂𝒕 = 𝟐. 𝟐𝟒𝟑 𝒌𝑷𝒂
From the acquired Vapour pressure, value at 29 °C 55% Saturation levels the Latent heat of evaporation
value and the Vapour Pressure of the water within the pool at 27 °C needs to be acquired which can be
found within CIBSE Guide C (CIBSE, 2010), which is extracted below.
 Vapour Pressure of Water within Pool @ 27 °C – 3.779 kPa
 Latent Heat of evaporation @ 29 °C – 2434.7 kJkg-1
From acquiring the above values to proceed with the calculation process, the evaporation rate can be
confirmed using the following equation.

18. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
14
𝒒 𝒆 = (𝟎. 𝟎𝟖𝟖𝟓 + (𝟎. 𝟎𝟕𝟕𝟗 × 𝒗)) × (𝒑 𝒘 − 𝒑 𝒔)
Where:
𝑞 𝑒 𝑖𝑠 𝑡ℎ𝑒 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑣 𝑖𝑠 𝑡ℎ𝑒 𝑎𝑖𝑟 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑜𝑣𝑒𝑟 𝑡ℎ𝑒 𝑠𝑢𝑟𝑓𝑎𝑐𝑒 𝑜𝑓 𝑡ℎ𝑒 𝑝𝑜𝑜𝑙 𝑤ℎ𝑖𝑐ℎ 𝑖𝑠 𝑎𝑠𝑠𝑢𝑚𝑒𝑑 𝑡𝑜 𝑏𝑒 0.15𝑚𝑠−1
𝑝 𝑤 𝑖𝑠 𝑡ℎ𝑒 𝑠𝑎𝑡𝑢𝑟𝑎𝑡𝑒𝑑 𝑣𝑎𝑝𝑜𝑢𝑟 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑒𝑥𝑒𝑟𝑡𝑒𝑑 𝑏𝑦 𝑡ℎ𝑒 𝑃𝑜𝑜𝑙 𝑎𝑡 27°𝐶 𝑡𝑜 𝑏𝑒 3780 𝑃𝑎
𝑝𝑠 𝑖𝑠 𝑡ℎ𝑒 𝑝𝑎𝑟𝑡𝑖𝑎𝑙 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑜𝑓 𝑡ℎ𝑒 𝑤𝑎𝑡𝑒𝑟 𝑣𝑎𝑝𝑜𝑢𝑟 𝑖𝑛 𝑡ℎ𝑒 𝑎𝑖𝑟 𝑎𝑡 29°𝐶 𝑡𝑜 𝑏𝑒 2243 𝑃𝑎
Therefore:
𝑞 𝑒 = (0.0885 + (0.0779 × 0.15)) × (3780 − 2243)
𝒒 𝒆 = 𝟏𝟓𝟑. 𝟗𝟖 𝑾𝒎−𝟐
Following the calculated evaporation rate above the latent heat gain can be calculated as follows
𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝑮𝒂𝒊𝒏 =
𝑬𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝑹𝒂𝒕𝒆 × 𝑨𝒓𝒆𝒂 𝒐𝒇 𝑷𝒐𝒐𝒍 × 𝟏. 𝟐
𝟏𝟎𝟎𝟎
Where:
𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝐺𝑎𝑖𝑛 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝐸𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑅𝑎𝑡𝑒 𝑡𝑜 𝑏𝑒 153.98 𝑊𝑚−2
𝐴𝑟𝑒𝑎 𝑜𝑓 𝑃𝑜𝑜𝑙 𝑡𝑜 𝑏𝑒 117𝑚2
Therefore:
𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝐺𝑎𝑖𝑛 =
153.98 × 117 × 1.2
1000
𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝑮𝒂𝒊𝒏 = 𝟐𝟏. 𝟔𝟏𝟗 𝒌𝑾
From the Latent Heat gain value, being calculated the total evaporation rate about the rate of evaporation
with the surrounding atmosphere inside the Pool space could be calculated as follows.
𝑻𝒐𝒕𝒂𝒍 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 =
𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝑮𝒂𝒊𝒏
𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝒐𝒇 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 @ 𝟐𝟗℃
Where:
𝑇𝑜𝑡𝑎𝑙 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝐺𝑎𝑖𝑛 𝑖𝑠 𝑡𝑜 𝑏𝑒 21.619 𝑘𝑊
𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝑜𝑓 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 @ 29℃ 𝑡𝑜 𝑏𝑒 2434.7 kJ𝑘𝑔−1
Therefore:
𝑇𝑜𝑡𝑎𝑙 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 =
21.619
2434.7
𝑻𝒐𝒕𝒂𝒍 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 = 𝟎. 𝟎𝟎𝟖𝟗 𝒌𝒈𝒔−𝟏
From the total evaporation rate being calculated, the total evaporation rate is to be disregarded from the
area of the pool to proceed with the calculation process. Therefore using the following calculation the
specific evaporation rate can be calculated as follows.
𝑺𝒑𝒆𝒄𝒊𝒇𝒊𝒄 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 =
𝑻𝒐𝒕𝒂𝒍 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆
𝑨𝒓𝒆𝒂 𝒐𝒇 𝑷𝒐𝒐𝒍
Where:
𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑇𝑜𝑡𝑎𝑙 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑡𝑜 𝑏𝑒 0.0089 𝑘𝑔𝑠−1
𝐴𝑟𝑒𝑎 𝑜𝑓 𝑃𝑜𝑜𝑙 𝑡𝑜 𝑏𝑒 117𝑚2
Therefore:
𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 =
0.0089
117
𝑺𝒑𝒆𝒄𝒊𝒇𝒊𝒄 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 = 𝟎. 𝟎𝟎𝟎𝟎𝟕𝟔 𝒌𝒈𝒔−𝟏
𝒎−𝟐
Following the specific evaporation rate value being calculated as shown above. To proceed with the
calculation process the type of activity within the pool needs to be outlined as the activity factor needs to
be determined.

19. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
15
Figure 8 - Normalised activity factor for evaporation from indoor swimming pools acquired from W.P.Jones (1997)
From the plotted graph aquired from W.P.Jones (1997) which illustrates the normalised activity factor for
evaporation for an indpool, the activity factor was determined to be 0.5 based on the Area of the Pool and
the amount of bathers using the pool.
Following the aquired normalised activity factor the flow rate with account of the presenece of th
occupants needs to be calculated with the following calulation process.
𝒘 𝒐 = (𝟑. 𝟐𝟕𝟖 + ((𝟒. 𝟏𝟓𝟕 ×∈) × (𝒑 𝒘 − 𝒑 𝒔)) × 𝑨 𝒑 × 𝟏𝟎−𝟓
Where:
𝑤𝑜 𝑖𝑠 𝑡ℎ𝑒 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 𝑤𝑖𝑡ℎ 𝑎𝑐𝑐𝑜𝑢𝑛𝑡 𝑜𝑓 𝑡ℎ𝑒 𝑝𝑟𝑒𝑠𝑒𝑛𝑐𝑒 𝑜𝑓 𝑡ℎ𝑒 𝑜𝑐𝑐𝑢𝑝𝑎𝑛𝑡𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
∈ 𝑖𝑠 𝑡ℎ𝑒 𝑛𝑜𝑟𝑚𝑎𝑙𝑖𝑠𝑒𝑑 𝑎𝑐𝑡𝑖𝑣𝑖𝑡𝑦 𝑓𝑎𝑐𝑡𝑜𝑟 𝑡𝑜 𝑏𝑒 0.5
𝑝 𝑤 𝑖𝑠 𝑡ℎ𝑒 𝑠𝑎𝑡𝑢𝑟𝑎𝑡𝑒𝑑 𝑣𝑎𝑝𝑜𝑢𝑟 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑒𝑥𝑒𝑟𝑡𝑒𝑑 𝑏𝑦 𝑡ℎ𝑒 𝑃𝑜𝑜𝑙 𝑎𝑡 27°𝐶 𝑡𝑜 𝑏𝑒 3780 𝑃𝑎
𝑝𝑠 𝑖𝑠 𝑡ℎ𝑒 𝑝𝑎𝑟𝑡𝑖𝑎𝑙 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑜𝑓 𝑡ℎ𝑒 𝑤𝑎𝑡𝑒𝑟 𝑣𝑎𝑝𝑜𝑢𝑟 𝑖𝑛 𝑡ℎ𝑒 𝑎𝑖𝑟 𝑎𝑡 29°𝐶 𝑡𝑜 𝑏𝑒 2243 𝑃𝑎
𝐴 𝑝 𝑖𝑠 𝑡ℎ𝑒 𝐴𝑟𝑒𝑎 𝑜𝑓 𝑃𝑜𝑜𝑙 𝑡𝑜 𝑏𝑒 117𝑚2
Therefore:
𝑤𝑜 = (3.278 + ((4.157 × 0.5) × (3.780 − 2.243)) × 117 × 10−5
𝒘 𝒐 = 𝟎. 𝟎𝟎𝟕𝟓𝟕 𝒌𝒈𝒔−𝟏
From the acquired flow rate with account of the presence of the occupants within the pool space being
calculated as shown above, the specific evaporation rate needs to be re-calculated as shown below.
𝑺𝒑𝒆𝒄𝒊𝒇𝒊𝒄 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 =
𝑬𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 𝒘𝒊𝒕𝒉 𝒂𝒄𝒄𝒐𝒖𝒏𝒕 𝒐𝒇 𝒐𝒄𝒄𝒖𝒑𝒂𝒏𝒕𝒔
𝑨𝒓𝒆𝒂 𝒐𝒇 𝑷𝒐𝒐𝒍
Where:
𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑇𝑜𝑡𝑎𝑙 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑤𝑖𝑡ℎ 𝑎𝑐𝑐𝑜𝑢𝑛𝑡 𝑜𝑓 𝑜𝑐𝑐𝑢𝑝𝑎𝑛𝑡𝑠 𝑡𝑜 𝑏𝑒 0.00757 𝑘𝑔𝑠−1
𝐴𝑟𝑒𝑎 𝑜𝑓 𝑃𝑜𝑜𝑙 𝑡𝑜 𝑏𝑒 117𝑚2
Therefore:
𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 =
0.00757
117
𝑺𝒑𝒆𝒄𝒊𝒇𝒊𝒄 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 = 𝟎. 𝟎𝟎𝟎𝟎𝟔𝟒𝟕 𝒌𝒈𝒔−𝟏
𝒎−𝟐
From the finalised specific evaporation rate, being calculated as shown above, the total latent heat gain
produced by the Pool while occupied can be confirmed using the following calculation process.
𝑻𝒐𝒕𝒂𝒍 𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝑮𝒂𝒊𝒏 = 𝑻𝒐𝒕𝒂𝒍 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐 𝒓𝒂𝒕𝒆 𝒐𝒇 𝒐𝒄𝒄𝒖𝒑𝒂𝒏𝒕𝒔 × 𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝒐𝒇 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 @ 𝟐𝟗℃
Where:
𝑇𝑜𝑡𝑎𝑙 𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝐺𝑎𝑖𝑛 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑇𝑜𝑡𝑎𝑙 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜 𝑟𝑎𝑡𝑒 𝑤𝑖𝑡ℎ 𝑎𝑐𝑐𝑜𝑢𝑛𝑡 𝑜𝑓 𝑜𝑐𝑐𝑢𝑝𝑎𝑛𝑡𝑠 𝑡𝑜 𝑏𝑒 0.00757 𝑘𝑔𝑠−1
𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝑜𝑓 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 @ 29 °𝐶 𝑡𝑜 𝑏𝑒 2434.7 𝑘𝐽𝑘𝑔−1
Therefore:
𝑇𝑜𝑡𝑎𝑙 𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝐺𝑎𝑖𝑛 = 0.00757 × 2434.7
𝑻𝒐𝒕𝒂𝒍 𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝑮𝒂𝒊𝒏 = 𝟏𝟖. 𝟒𝟑 𝒌𝑾

20. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
16
The total latent heat gain has been calculated to be 18.43 kW for the pool space. This latent heat gain
load calculated is only calculated about the evaporation of heat from the pool water surface. Therefore,
the wet surfaces surrounding the pool space need to go through a similar calculation process to determine
the latent heat gain being evaporated from the wet surfaces.
6.1.3 Wet Surface Latent Gain Calculation
To determine the latent heat gain produced from the surrounding wet surfaces of the pool space the
following initial design information requirements have been outlined as follows.
 Pool Space Air Temperature – 30 °C
 Pool Space Humidity – 60%
 Water Temperature on surface – 29 °C
 Wet Surface Area – 59.28 m2
 Vapour Pressure of Air @ 30 °C 60% Sat -2.243 kPa
 Vapour Pressure of Water on the surface @ 29 °C – 3.779 kPa
 Latent Heat of evaporation @ 30 °C – 2434.7 kJkg-1
The outlined initial design information have been acquired with the use of CIBSE Guide C Data and initially
calculated details when calculating the latent heat gain from the pool within the pool space.
From acquiring the above values to proceed with the calculation process, the evaporation rate can be
confirmed using the following equation.
𝒒 𝒆 = (𝟎. 𝟎𝟖𝟖𝟓 + (𝟎. 𝟎𝟕𝟕𝟗 × 𝒗)) × (𝒑 𝒘 − 𝒑 𝒔)
Where:
𝑞 𝑒 𝑖𝑠 𝑡ℎ𝑒 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑣 𝑖𝑠 𝑡ℎ𝑒 𝑎𝑖𝑟 𝑣𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑜𝑣𝑒𝑟 𝑡ℎ𝑒 𝑠𝑢𝑟𝑓𝑎𝑐𝑒 𝑜𝑓 𝑡ℎ𝑒 𝑓𝑙𝑜𝑜𝑟 𝑤ℎ𝑖𝑐ℎ 𝑖𝑠 𝑎𝑠𝑠𝑢𝑚𝑒𝑑 𝑡𝑜 𝑏𝑒 0.15𝑚𝑠−1
𝑝 𝑤 𝑖𝑠 𝑡ℎ𝑒 𝑠𝑎𝑡𝑢𝑟𝑎𝑡𝑒𝑑 𝑣𝑎𝑝𝑜𝑢𝑟 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑒𝑥𝑒𝑟𝑡𝑒𝑑 𝑏𝑦 𝑡ℎ𝑒 𝑃𝑜𝑜𝑙 𝑎𝑡 27°𝐶 𝑡𝑜 𝑏𝑒 3780 𝑃𝑎
𝑝𝑠 𝑖𝑠 𝑡ℎ𝑒 𝑝𝑎𝑟𝑡𝑖𝑎𝑙 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑜𝑓 𝑡ℎ𝑒 𝑤𝑎𝑡𝑒𝑟 𝑣𝑎𝑝𝑜𝑢𝑟 𝑖𝑛 𝑡ℎ𝑒 𝑎𝑖𝑟 𝑎𝑡 29°𝐶 𝑡𝑜 𝑏𝑒 2243 𝑃𝑎
Therefore:
𝑞 𝑒 = (0.0885 + (0.0779 × 0.15)) × (3780 − 2243)
𝒒 𝒆 = 𝟏𝟓𝟑. 𝟗𝟖 𝑾𝒎−𝟐
Following the calculated evaporation rate above the latent heat gain can be calculated as follows
𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝑮𝒂𝒊𝒏 =
𝑬𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝑹𝒂𝒕𝒆 × 𝑨𝒓𝒆𝒂 𝒐𝒇 𝑾𝒆𝒕 𝑺𝒖𝒓𝒇𝒂𝒄𝒆 × 𝟏. 𝟐
𝟏𝟎𝟎𝟎
Where:
𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝐺𝑎𝑖𝑛 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝐸𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑅𝑎𝑡𝑒 𝑡𝑜 𝑏𝑒 153.98 𝑊𝑚−2
𝐴𝑟𝑒𝑎 𝑜𝑓 𝑊𝑒𝑡 𝑆𝑢𝑟𝑓𝑎𝑐𝑒 𝑡𝑜 𝑏𝑒 59.28 𝑚2
Therefore:
𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝐺𝑎𝑖𝑛 =
153.98 × 59.28 × 1.2
1000
𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝑮𝒂𝒊𝒏 = 𝟏𝟎. 𝟗𝟓𝟒 𝒌𝑾
From the Latent Heat gain value, being calculated the total evaporation rate about the rate of evaporation
with the surrounding atmosphere inside the Pool space could be calculated as follows.
𝑻𝒐𝒕𝒂𝒍 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 =
𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝑮𝒂𝒊𝒏
𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝒐𝒇 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 @ 𝟐𝟗℃
Where:
𝑇𝑜𝑡𝑎𝑙 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝐺𝑎𝑖𝑛 𝑖𝑠 𝑡𝑜 𝑏𝑒 10.954 𝑘𝑊
𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝑜𝑓 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 @ 29℃ 𝑡𝑜 𝑏𝑒 2434.7 kJ𝑘𝑔−1
Therefore:
𝑇𝑜𝑡𝑎𝑙 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 =
10.954
2434.7
𝑻𝒐𝒕𝒂𝒍 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 = 𝟎. 𝟎𝟎𝟒𝟓 𝒌𝒈𝒔−𝟏
From the total evaporation rate being calculated, the total evaporation rate is to be disregarded from the
area of the wet surface area to proceed with the calculation process. Therefore using the following
calculation the specific evaporation rate can be calculated as follows.

21. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
17
𝑺𝒑𝒆𝒄𝒊𝒇𝒊𝒄 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 =
𝑻𝒐𝒕𝒂𝒍 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆
𝑨𝒓𝒆𝒂 𝒐𝒇 𝑾𝒆𝒕 𝑺𝒖𝒓𝒇𝒂𝒄𝒆
Where:
𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑇𝑜𝑡𝑎𝑙 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑡𝑜 𝑏𝑒 0.0045 𝑘𝑔𝑠−1
𝐴𝑟𝑒𝑎 𝑜𝑓 𝑊𝑒𝑡 𝑆𝑢𝑟𝑓𝑎𝑐𝑒 𝑡𝑜 𝑏𝑒 59.28 𝑚2
Therefore:
𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 =
0.0045
59.28
𝑺𝒑𝒆𝒄𝒊𝒇𝒊𝒄 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 = 𝟎. 𝟎𝟎𝟎𝟎𝟕𝟓𝟗 𝒌𝒈𝒔−𝟏
𝒎−𝟐
Following the specific evaporation rate value being calculated as shown above the evaporation rate for a
wet surface within the pool space needs to be calculated. This is acquired by using the following
calculation process.
𝒘 𝒘𝒔 = (𝟐. 𝟏𝟖𝟖 × (𝒑 𝒘 − 𝒑 𝒔) − 𝟏. 𝟔𝟑𝟗) × 𝑾 𝒑 × 𝟏𝟎−𝟓
Where:
𝑤 𝑤𝑠 𝑖𝑠 𝑡ℎ𝑒 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 𝑤𝑖𝑡ℎ 𝑟𝑒𝑔𝑎𝑟𝑑𝑠 𝑡𝑜 𝑎 𝑤𝑒𝑡 𝑠𝑢𝑟𝑓𝑎𝑐𝑒 𝑤𝑖𝑡ℎ𝑖𝑛 𝑎𝑛 𝑖𝑛𝑡𝑒𝑟𝑛𝑎𝑙 𝑠𝑝𝑎𝑐𝑒
𝑝 𝑤 𝑖𝑠 𝑡ℎ𝑒 𝑠𝑎𝑡𝑢𝑟𝑎𝑡𝑒𝑑 𝑣𝑎𝑝𝑜𝑢𝑟 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑒𝑥𝑒𝑟𝑡𝑒𝑑 𝑏𝑦 𝑡ℎ𝑒 𝑃𝑜𝑜𝑙 𝑎𝑡 27°𝐶 𝑡𝑜 𝑏𝑒 3780 𝑃𝑎
𝑝𝑠 𝑖𝑠 𝑡ℎ𝑒 𝑝𝑎𝑟𝑡𝑖𝑎𝑙 𝑝𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑜𝑓 𝑡ℎ𝑒 𝑤𝑎𝑡𝑒𝑟 𝑣𝑎𝑝𝑜𝑢𝑟 𝑖𝑛 𝑡ℎ𝑒 𝑎𝑖𝑟 𝑎𝑡 29°𝐶 𝑡𝑜 𝑏𝑒 2243 𝑃𝑎
𝑊𝑝 𝑖𝑠 𝑡ℎ𝑒 𝐴𝑟𝑒𝑎 𝑜𝑓 𝑊𝑒𝑡 𝑆𝑢𝑟𝑓𝑎𝑐𝑒 𝑡𝑜 𝑏𝑒 59.28 𝑚2
Therefore:
𝑤 𝑤𝑠 = (2.188 × (3.780 − 2.243) − 1.639) × 59.28 × 10−5
𝒘 𝒘𝒔 = 𝟎. 𝟎𝟎𝟏𝟎𝟐𝟐 𝒌𝒈𝒔−𝟏
From the finalised evaporation flow rate for a wet surface within the pool space, being calculated as
shown above, the total latent heat gain produced by the Wet surfaces surrounding the Pool can be
confirmed using the following calculation process.
𝑻𝒐𝒕𝒂𝒍 𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝑮𝒂𝒊𝒏 = 𝑻𝒐𝒕𝒂𝒍 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 𝒓𝒂𝒕𝒆 𝒐𝒇 𝑾𝒆𝒕 𝑺𝒖𝒓𝒇𝒂𝒄𝒆𝒔 × 𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝒐𝒇 𝒆𝒗𝒂𝒑𝒐𝒓𝒂𝒕𝒊𝒐𝒏 @ 𝟐𝟗℃
Where:
𝑇𝑜𝑡𝑎𝑙 𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝐺𝑎𝑖𝑛 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑇𝑜𝑡𝑎𝑙 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 𝑟𝑎𝑡𝑒 𝑤𝑖𝑡ℎ 𝑎𝑐𝑐𝑜𝑢𝑛𝑡 𝑜𝑓 𝑊𝑒𝑡 𝑆𝑢𝑟𝑓𝑎𝑐𝑒𝑠 𝑡𝑜 𝑏𝑒 0.001022 𝑘𝑔𝑠−1
𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝑜𝑓 𝑒𝑣𝑎𝑝𝑜𝑟𝑎𝑡𝑖𝑜𝑛 @ 29 °𝐶 𝑡𝑜 𝑏𝑒 2434.7 𝑘𝐽𝑘𝑔−1
Therefore:
𝑇𝑜𝑡𝑎𝑙 𝐿𝑎𝑡𝑒𝑛𝑡 𝐻𝑒𝑎𝑡 𝐺𝑎𝑖𝑛 = 0.001022 × 2434.7
𝑻𝒐𝒕𝒂𝒍 𝑳𝒂𝒕𝒆𝒏𝒕 𝑯𝒆𝒂𝒕 𝑮𝒂𝒊𝒏 = 𝟐. 𝟒𝟗 𝒌𝑾
The finalised latent heat gain values for the Occupants, Pool and the Surface area surrounding the Pool
have been finalised which will be used further o within this report to determine the various systems to be
provided for the Pool space.
6.2 Condensation Gain Calculation
An analysis of the condensation gain on the face of the glass façade needs to be analysed due to the
possibility of dampness occurrence and build-up of moisture on the sills of the glass facades walls.
Therefore the following calculation process will determine the temperature of the inside face of the glass
façade as shown below.

22. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
18
Figure 9 - Resistance Values and Design Conditions for Glass Facade in Pool Space
From the produced illustration of the construction of glass façade and the corresponding resistance values
and design conditions of the internal space and the external condition to the glass façade, the following
calculation process can determine the temperature of the glass façade on the inside surface as follows.
When analysing the condensation occurrence on the glazing façade of the pool space, it should be noted
that it could occur during summer and winter periods therefore both external design conditions needs to
be analysed.
Using the following equation to determine what the surface temperature would be on the Glass façade can
be then used to provide a confirmation of whether condensation occurs on the glass façade. Firstly, the
winter external design consideration will be analysed as follows.
𝑡𝑖 − 𝑡 𝑠 =
(𝑡𝑖 − 𝑡 𝑜)
(𝑅𝑖𝑠 + 𝑅 𝑜𝑠)
Where:
𝑡𝑖 𝑖𝑠 𝑡ℎ𝑒 𝑆𝑤𝑖𝑚𝑚𝑖𝑛𝑔 𝑃𝑜𝑜𝑙 𝑆𝑝𝑎𝑐𝑒 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 30℃
𝑡 𝑠 𝑖𝑠 𝑡ℎ𝑒 𝑆𝑢𝑟𝑓𝑎𝑐𝑒 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑜𝑓 𝑡ℎ𝑒 𝐺𝑙𝑎𝑠𝑠 𝐹𝑎𝑐𝑎𝑑𝑒 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑡 𝑜 𝑖𝑠 𝑡ℎ𝑒 𝑂𝑢𝑡𝑠𝑖𝑑𝑒 𝑊𝑖𝑛𝑡𝑒𝑟 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 − 2.7℃
𝑅𝑖𝑠 𝑖𝑠 𝑡ℎ𝑒 𝐼𝑛𝑠𝑖𝑑𝑒 𝑆𝑢𝑟𝑓𝑎𝑐𝑒 𝑟𝑒𝑠𝑖𝑠𝑡𝑎𝑛𝑐𝑒 𝑡𝑜 𝑏𝑒 0.13 𝑚2
℃/𝑊
𝑅 𝑜𝑠 𝑖𝑠 𝑡ℎ𝑒 𝐼𝑛𝑠𝑖𝑑𝑒 𝑆𝑢𝑟𝑓𝑎𝑐𝑒 𝑟𝑒𝑠𝑖𝑠𝑡𝑎𝑛𝑐𝑒 𝑡𝑜 𝑏𝑒 0.04 𝑚2℃/𝑊
Therefore:
30 − 𝑡 𝑠 =
(30 − (−2.7))
(0.13 + 0.04)
30 − 𝑡 𝑠 = 192.35
𝑡 𝑠 = −162.35℃
As the calculation process illustrates immediately that condensation would occur on the inside of the glass
façade of the pool space due to the adverse value produced which will not be able to be analysed further
due to the extremeity of the produced value.
Therefore the summer external condition will now be analsyed to see whether condensation occurs on the
inside glass façade of the pool space as follows.
𝑡𝑖 − 𝑡 𝑠 =
(𝑡𝑖 − 𝑡 𝑜)
(𝑅𝑖𝑠 + 𝑅 𝑜𝑠)
Where:
𝑡𝑖 𝑖𝑠 𝑡ℎ𝑒 𝑆𝑤𝑖𝑚𝑚𝑖𝑛𝑔 𝑃𝑜𝑜𝑙 𝑆𝑝𝑎𝑐𝑒 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 30℃
𝑡 𝑠 𝑖𝑠 𝑡ℎ𝑒 𝑆𝑢𝑟𝑓𝑎𝑐𝑒 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑜𝑓 𝑡ℎ𝑒 𝐺𝑙𝑎𝑠𝑠 𝐹𝑎𝑐𝑎𝑑𝑒 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑡 𝑜 𝑖𝑠 𝑡ℎ𝑒 𝑂𝑢𝑡𝑠𝑖𝑑𝑒 𝑆𝑢𝑚𝑚𝑒𝑟 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 26.1℃
𝑅𝑖𝑠 𝑖𝑠 𝑡ℎ𝑒 𝐼𝑛𝑠𝑖𝑑𝑒 𝑆𝑢𝑟𝑓𝑎𝑐𝑒 𝑟𝑒𝑠𝑖𝑠𝑡𝑎𝑛𝑐𝑒 𝑡𝑜 𝑏𝑒 0.13 𝑚2
℃/𝑊
𝑅 𝑜𝑠 𝑖𝑠 𝑡ℎ𝑒 𝐼𝑛𝑠𝑖𝑑𝑒 𝑆𝑢𝑟𝑓𝑎𝑐𝑒 𝑟𝑒𝑠𝑖𝑠𝑡𝑎𝑛𝑐𝑒 𝑡𝑜 𝑏𝑒 0.04 𝑚2
℃/𝑊
Swimming Pool
Temperature = 30°C
Summer Outside
Temperature =
26.1°C
Inside Surface Resistance
= 0.13 m2
℃/W
Outside Surface
Resistance = 0.04 m2
℃/W
Winter Outside
Temperature = -2.7°C

23. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
19
Therefore:
30 − 𝑡 𝑠 =
(30 − 26.1)
(0.13 + 0.04)
30 − 𝑡 𝑠 = 22.94
𝑡 𝑠 = 7.06
From the aquired internal surface temperature from the calculation process as shown above, it can be
plotted on the psychometric chart as shown in Figure 10.
As illustrated in Figure 10 when plotting the internal dry bulb temperature condition of the iside of the
glass façade surface then a a horizontal line is drawn to the 100% saturation curve where the wet bulb
temperature is deteermined. If the inside temperature of the glass façade is below the deteermined wet
bulb temperature of the dew point from the plotted pschometric chart then condensation will occur on the
inside of the glass façade to the Pool Space.
6.3 Summary of Pool Design Loads
Following the calculated Latent Gain loads for the pool space, a summary of the acquired values is shown
below as follows.
 Occupant Latent Heat Gain = 3.15 kW
 Pool Space Latent Heat Gain = 18.43 kW
 Wet Surface Area Latent Heat Gain = 2.49 kW
The latent heat gain values calculated as shown above are calculated based on the initial design
information gained from within the Pool space and take no consideration to the external conditions.
Therefore, the following System will be designed to produce the required design conditions with
consideration to the Winter, Summer and Pool design loads calculated previously.
Figure 10 - Illustration of Psychometric Chart showing Condensation occurrence

24. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
20
7. VENTILATION AND AIR CONDITIONING DESIGN
The provision of the ventilation and air conditioning to the Swimming Pool space is to design to the
calculated Sensible and Latent Loads as calculated previously within this report. Due to the Swimming
Pool space containing large amounts of water within the space which has been predicated to evaporate
and therefore result in a rather large amount of moisture to be found within the atmosphere of the
internal air space, precautions must be made in order to prevent mould and other forms of build-up of
moisture and condensation within the space but to be extracted out the space at a regulated period of
time.
The swimming pool space needs to be maintained at comfortable design conditions for the occupants that
use the pool space through the day. Therefore, the design conditions set out for the Swimming Pool space
will remain the same throughout the year for optimum thermal comfort when using the space. The design
of the ventilation and air conditioning system is to provide sufficient control over the air temperature and
humidity levels within the space all through the year regardless of peak summer or winter conditions. To
achieve this certain preliminary design conditions have been set out to achieve optimum control, which
are set out below in Table 8.
Table 8 - Pool Space Design Requirements
Occupants 10 Bathers
Pool Water Design Temperature 29°C
Pool Space Air Condition 30°C 60% Saturation
From the produced table above the initial design requirements have been outlined for the pool space. The
Swimming Pool space will consist of a central air-handling unit, which will be responsible of removing
contaminants from the pool as it pool water, evaporates. It will also provide a generally well-distributed
flow of fresh air that will overcome the high internal sensible and latent gains experienced within the
space as well as extract the same gains to be recovered for maximum efficiency for the whole system.
Figure 11 illustrates how the system will be indicatively designed within the Pool space. This shows that
the supply of the fresh conditioned air will be situated at the top of the space and the extraction of the air
within the space will be located at the bottom of the space within the walls. The proposed design has its
benefits as the supply of the fresh conditioned air is primarily used to offset the high internal sensible and
latent gains, which inevitably increase the internal design temperature. Looking into the mechanics of air
flow the hot air will rise to the top due to its density therefore the supply fresh air will cool the hot air at
the top of the space and force the movement of air in a circle motion as illustrated in Figure 11 the other
benefit of using this system is for the extraction of the contaminants and warm moist air being forced
down to the extraction points by the supply flow of fresh air.
Figure 11 - Distribution of Ventilation and Air Conditioning Design within Swimming Pool Space
Following the illustration of an indicative system layout within the Swimming Pool Space to be design to,
the sizing of the central air-handling unit can begin. It has been already been decided that the design
conditions within the pool space will not change during the winter and summer conditions. Therefore the
system plant is expected to be larger than conventional plant used in other types of spaces due to the
demand of keeping the same design conditions throughout the year regardless of how warm or how cold it
gets outside.

25. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
21
The swimming pool space will require the same design conditions consistently throughout the year
regardless of the winter and summer condition outside. The air-handling unit will require a frost coil for
the incoming fresh air supply to be heated up to acceptable requirements during the winter periods. A
heat exchanger will also be required to recover any rejected heat from the pool space to be recirculated
back into the pool space with the fresh air requirement being delivered. A reheat coil will also be required
to heat the recirculated air into the pool space to the design conditions specified and finally a humidifier is
required to de-humidify the supply air into the pool space to offset the pool latent load.
An illustration of the Air Handling Unit’s components is shown above in Figure 12 Following the produced
illustration a system selection process will be required to determine the system process during winter and
summer conditions for the swimming pool space, which will be carried out as follows below.
7.1 Fresh Air Requirement
Before the Air Handling Unit can be sized for the pool space, the fresh air requirement for the pool space
needs to be determined which will be analysed as follows.
The fresh air requirement for the pool space has been acquired from CIBSE Guide A Section 6 where it
outlines the requirement for the Pool Space to have a ventilation rate of 15 l/s/m2
. Therefore the required
ventilation rate for the pool space throughout the year will now be calculated as follows.
𝐹𝑟𝑒𝑠ℎ 𝐴𝑖𝑟 𝑅𝑒𝑞𝑢𝑖𝑟𝑒𝑚𝑒𝑛𝑡 = 𝐹𝑟𝑒𝑠ℎ 𝐴𝑖𝑟 𝑅𝑎𝑡𝑒 × 𝐴𝑟𝑒𝑎 𝑜𝑓 𝑃𝑜𝑜𝑙 𝑆𝑝𝑎𝑐𝑒
Where:
𝐹𝑟𝑒𝑠ℎ 𝐴𝑖𝑟 𝑅𝑒𝑞𝑢𝑖𝑟𝑒𝑚𝑒𝑛𝑡 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝐹𝑟𝑒𝑠ℎ 𝐴𝑖𝑟 𝑅𝑎𝑡𝑒 𝑎𝑞𝑢𝑖𝑟𝑒𝑑 𝑓𝑟𝑜𝑚 𝐶𝐼𝐵𝑆𝐸 𝐺𝑢𝑖𝑑𝑒 𝐴 𝑆𝑒𝑐𝑡𝑖𝑜𝑛 6 𝑡𝑜 𝑏𝑒 15 𝑙/𝑠/𝑚2
𝐴𝑟𝑒𝑎 𝑜𝑓 𝑃𝑜𝑜𝑙 𝑆𝑝𝑎𝑐𝑒 𝑡𝑜 𝑏𝑒 176.28 𝑚2
Therefore:
𝐹𝑟𝑒𝑠ℎ 𝐴𝑖𝑟 𝑅𝑒𝑞𝑢𝑖𝑟𝑒𝑚𝑒𝑛𝑡 = 15 × 176.28
𝐹𝑟𝑒𝑠ℎ 𝐴𝑖𝑟 𝑅𝑒𝑞𝑢𝑖𝑟𝑒𝑚𝑒𝑛𝑡 = 2644.20 𝑙/𝑠
From the calculated fresh air requirement, the pool space systems can be designed as follows.
7.2 Winter Design
The winter design process for the swimming pool space will require the same design requirements for the
pool such as latent gain provided by the Pool water and the Wet surfaces around the Pool although heat
loss through fabric and infiltration loss will be experienced additionally. To outline the total design loads
that will be experienced Table 9 provides a total of all the final loads as follows which have been acquired
from ASHRAE Weather Data (ASHRAE Weather Data Southampton), and Client requirements based on
CIBSE Guide C, (CIBSE, 2010).
Table 9 - Initial Winter Design Requirements for Swimming Pool Space
Pool Hall Design Condition 30°C DB, 60% RH
Outdoor Design Condition -2.7°C DB, 90% RH
Pool Hall Sensible Load 10.75 kW
Pool Hall Latent Load 24.07 kW
Pool Hall Fresh Air Requirement 2.644 m3
/s
From the produced table above, which outlines the required loads for winter, the system can be designed.
During the winter, conditions as outlined in Table 9 the incoming supply fresh air is deemed too cold to
handle for the internal air handling unit’s components, as there is a possibility of frost build up. Therefore
the incoming fresh air supply will be heated up to 5°C at the first heating coil before entering the air-
handling unit. The calculation process of determining the required size of the frost coil is shown as follows
below.
Air Handling Situated in the Plant Room supplying fresh air to Swimming Pool Space
Figure 12 - Air Handling Unit Diagram to be used for Supplying Swimming Pool Space

26. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
22
𝑸 𝑭𝑪 = 𝒎 𝒐 × 𝑪𝒑 × ∆𝑻
Where:
𝑄 𝐹𝐶 = 𝐹𝑟𝑜𝑠𝑡 𝐶𝑜𝑖𝑙 𝑠𝑖𝑧𝑒 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑚 𝑜 = 𝐹𝑟𝑒𝑠ℎ 𝑎𝑖𝑟 𝑟𝑒𝑞𝑢𝑖𝑟𝑚𝑒𝑛𝑡 𝑡𝑜 𝑏𝑒 2.644 𝑚3
/𝑠
𝐶𝑝 = 𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝐻𝑒𝑎𝑡 𝑐𝑎𝑝𝑎𝑐𝑖𝑡𝑦 𝑜𝑓𝑎𝑖𝑟 𝑡𝑜 𝑏𝑒 𝑎𝑠𝑠𝑢𝑚𝑒𝑑 𝑎𝑠 1.02 𝑘𝐽/𝑘𝑔. 𝐾
𝐷𝑒𝑛𝑠𝑖𝑡𝑦 𝑜𝑓 𝑎𝑖𝑟 𝑡𝑜 𝑏𝑒 𝑎𝑠𝑠𝑢𝑚𝑒𝑑 𝑎𝑠 1.2 𝑘𝑔/𝑚3
∆𝑇 = 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑑𝑖𝑓𝑓𝑒𝑟𝑒𝑛𝑐𝑒 𝑏𝑒𝑡𝑤𝑒𝑒𝑛 𝐹𝑜𝑟𝑠𝑡 𝐶𝑜𝑖𝑙 𝑐𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛 𝑎𝑛𝑑 𝑜𝑢𝑡𝑠𝑖𝑑𝑒 𝑐𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛
Therefore:
𝑄 𝐹𝐶 = (2.644 × 1.2) × 1.02 × (5 − −2.7)
𝑸 𝑭𝑪 = 𝟐𝟒. 𝟗𝟐 𝒌𝑾
Following the determined size of the required frost coil within the Air handling unit, the condition of the air
after the heat recovery process needs to be determined. From the manufactures data produced by
Dantherm (Dantherm.co.uk), who will manufacture the required Air handling unit, the heat exchangers
efficiency has been stated to be up to 80% efficient. The condition of the air after the heat recovery
process within the air-handling unit can be determined using the following calculation process.
𝒕 𝑯𝑹 = ɳ × (𝒕 𝒓 − 𝒕 𝑭𝑪) + 𝒕 𝒐
Where:
𝑡 𝐻𝑅 = 𝐻𝑒𝑎𝑡 𝑟𝑒𝑐𝑜𝑣𝑒𝑟𝑦 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑡 𝑟 = 𝑅𝑜𝑜𝑚 𝑎𝑖𝑟 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 30°𝐶
𝑡 𝐹𝐶 = 𝐹𝑟𝑜𝑠𝑡 𝐶𝑜𝑖𝑙 𝑎𝑖𝑟 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 5°𝐶
Therefore:
𝑡 𝐻𝑅 = 0.8 × (30 − 5) + 5
𝒕 𝑯𝑹 = 𝟐𝟓°𝑪
As determined from the calculation process as shown above, the heat recovery process between the
outside fresh air and the return air from the pool space is able to recover up to 80% of the air condition to
supply at a temperature of 25°C. This temperature condition for the supply of the pool space is not
sufficient therefore, additional heating requirement is needed.
Firstly the Room Ratio Line (RRL) needs to be determined with the use of the calculated sensible and
latent gain loads during the winter condition of the pool space. Therefore, the following calculation process
determines the RRL as follows.
𝑹𝑹𝑳 =
𝑸 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆
𝑸 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 + 𝑸 𝑳𝒂𝒕𝒆𝒏𝒕
Where:
𝑅𝑅𝐿 = 𝑅𝑜𝑜𝑚 𝑟𝑎𝑡𝑖𝑜 𝑙𝑖𝑛𝑒 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑄 𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 = 𝑊𝑖𝑛𝑡𝑒𝑟 𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝑔𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 10.75 𝑘𝑊
𝑄 𝐿𝑎𝑡𝑒𝑛𝑡 = 𝑃𝑜𝑜𝑙 𝑙𝑎𝑡𝑒𝑛𝑡 𝑔𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 24.07 𝑘𝑊
Therefore:
𝑅𝑅𝐿 =
10.75
10.75 + 24.07
𝑹𝑹𝑳 = 𝟎. 𝟑𝟏
From the calculated RRL the supply condition can be determined for which to supply the pool space at
during winter external conditions to achieve the required pool design conditions. The supply condition has
been determined to be 25°C which is the recovered Heat Recovery condition although the supply condition
is expected to be slightly humidified to be supplied into the pool space. Therefore the following calculation
process will determine the required humidifier load for the air handling unit.
𝑸 𝑯𝒖𝒎 = 𝒎 𝒐 × 𝒉𝒇𝒈 × (𝒈 𝒔 − 𝒈 𝒔′)
Where:
𝑄 𝐻𝑢𝑚 = 𝐻𝑢𝑚𝑖𝑑𝑖𝑓𝑖𝑒𝑟 𝑙𝑜𝑎𝑑 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑚 𝑜 = 𝐹𝑟𝑒𝑠ℎ 𝑎𝑖𝑟 𝑟𝑒𝑞𝑢𝑖𝑟𝑚𝑒𝑛𝑡 𝑡𝑜 𝑏𝑒 2.644 𝑚3
/𝑠
ℎ𝑓𝑔 = 𝐶𝑜𝑛𝑠𝑡𝑎𝑛𝑡 𝑓𝑖𝑔𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 2500 𝑘𝑔/𝑘𝑔
𝐷𝑒𝑛𝑠𝑖𝑡𝑦 𝑜𝑓 𝑎𝑖𝑟 𝑡𝑜 𝑏𝑒 𝑎𝑠𝑠𝑢𝑚𝑒𝑑 𝑎𝑠 1.2 𝑘𝑔/𝑚3
𝑔𝑠′ = 𝐻𝑒𝑎𝑡 𝑅𝑒𝑐𝑜𝑣𝑒𝑟𝑒𝑑 ℎ𝑢𝑚𝑖𝑑𝑖𝑡𝑦 𝑟𝑎𝑡𝑖𝑜 𝑡𝑜 𝑏𝑒 0.0028 𝑘𝑔/𝑘𝑔
𝑔𝑠 = 𝑆𝑢𝑝𝑝𝑙𝑦 ℎ𝑢𝑚𝑖𝑑𝑖𝑡𝑦 𝑟𝑎𝑡𝑖𝑜 𝑡𝑜 𝑏𝑒 0.0050 𝑘𝑔/𝑘𝑔
Therefore:
𝑄 𝐻𝑢𝑚 = (2.644 × 1.2) × 2500 × (0.0050 − 0.0028)
𝑸 𝑯𝒖𝒎 = 𝟏𝟕. 𝟒𝟓 𝒌𝑾
The calculated humidifier load will be utilised as part of the air handling unit plant design for the pool
space in providing the required supply condition for the pool space.

27. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
23
The winter psychometric process has now been confirmed during the winter conditions from the
calculation processes as carried out above. To illustrate the determined winter process that would be seen
on the produced winter psychometric chart, Figure 13 is an indicative illustration of the winter process for
the pool space.
Frost Coil Load Humidifier Load
Heat Recovery Process RRL Supply
Following the produced illustration of the winter psychometric process, the summer process needs to be
determined as follows bellows to determine the summer psychometric process for the swimming pool
space.
7.3 Summer Design
The summer design process for the swimming pool space will require the same design requirements for
the pool such as latent gain provided by the Pool water and the Wet surfaces around the Pool although
heat loss through fabric and infiltration loss will be experienced additionally. To outline the total design
loads that will be experienced Table 10 provides a total of all the final loads as follows.
Table 10 - Initial Summer Design Requirements for Swimming Pool Space
Pool Hall Design Condition 30°C DB, 60% RH
Outdoor Design Condition 26.1°C DB, 18.4°C DB
Pool Hall Sensible Load 12.51 kW
Pool Hall Latent Load 24.07 kW
Pool Hall Fresh Air Requirement 2.644 m3
/s
From the produced table above, which outlines the required loads for summer, the system can be
designed. The air-handling unit used to supply the ventilation and air conditioning requirements into the
pool space will be incorporating a heat recovery component. Therefore the heat recovery process needs to
be determined so that the supply condition after the heat recovery process can be calculated which is
shown as follows.
𝒕 𝑯𝑹 = ɳ × (𝒕 𝑹 − 𝒕 𝑶) + 𝒕 𝑶
Where:
𝑡 𝐻𝑅 = 𝐻𝑒𝑎𝑡 𝑟𝑒𝑐𝑜𝑣𝑒𝑟𝑒𝑑 𝑠𝑢𝑝𝑝𝑙𝑦 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑡 𝑅 = 𝑅𝑜𝑜𝑚 𝑎𝑖𝑟 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 30°𝐶
𝑡 𝑂 = 𝑆𝑢𝑚𝑚𝑒𝑟 𝑜𝑢𝑡𝑠𝑖𝑑𝑒 𝑎𝑖𝑟 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 26.1°𝐶
Therefore:
𝑡 𝐻𝑅 = 0.8 × (30 − 26.1) + 26.1
𝒕 𝑯𝑹 = 𝟐𝟗. 𝟐𝟐 °𝑪
From the calculated heat recovery condition of the supply air after the heat recovery process within the air
handling unit, it has been determined that 80% of the exhausted heat energy has been recovered to
provide a supply condition of 29.22°C. The required design condition within the pool space is to be 30°C
therefore additional heating would be required. Although as the heat recovered condition provides
29.22°C at the supply condition, this calculation is based on the peak outside condition during the
summer periods at the chosen location. Therefore lower heat recovered condition would be expected
1 2 3
4
1
2
3
4
Figure 13 – Illustration of the Psychometric Process during the Winter Conditions

28. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
24
through the summer. To determine the relevant cooling coil size the following calculation process is
required as follows.
The required off coil supply condition is to be confirmed with the aid of the software SPC2000, which by
inputting the following values will determine the off coil condition that is required to size the cooling coil
within the MVHR Unit.
 Air onto the cooling coil Dry Bulb is to be 29.22 °C
 Air onto the cooling coil Wet Bulb is to be 19.2 °C
 Air off the cooling coil Dry Bulb is to be 22 °C
 Mass Flow Required to be 2.644 m3
/s
Figure 14 - Determining Off coil condition from use of SPC Coils software
From inputting the following information as shown in Figure 14 the off coil condition has been determined
as well as the face velocity and calculated cooling capacity as follows.
From the SP Coils software, the following results were produced:
 Off Coil Wet Bulb Temperature = 16.8 °C
 Face Velocity = 5.73 m/s
 Cooling Coil Capacity = 23.61 kW
It should be taken into account that the supply rate calculated included a 10% increase margin to
compensate for commission purposes.
When looking into the calculated face velocity figure it should be taken note of that, the cooling coils are
most effective when there is as much condensation available as possible due to the latent properties of
the air stream within the air-handling unit. Therefore, it is recommended not to size a cooling coil, which
results in a face velocity greater than that of 2.5 m/s. if done so this would results in condensation to
blow off the coil and ultimately results in the reduction of performance of the coil. Therefore, as the face
velocity calculated from the SPC coils software shows to be 5.73 m3
/s it is recommended to install
moisture eliminators so that the provision of possible moisture build up being blown over the coils is
eliminated.
The required size of the cooling coil can be determined by using the following calculation:
𝑸 𝒄 = 𝒎 𝒐 × (𝒉 𝑯𝑹 − 𝒉 𝑺)
Where:
𝑄 𝑐 = 𝐶𝑜𝑜𝑙𝑖𝑛𝑔 𝑐𝑜𝑖𝑙 𝑙𝑜𝑎𝑑 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑚 𝑜 = 𝐹𝑟𝑒𝑠ℎ 𝑎𝑖𝑟 𝑟𝑒𝑞𝑢𝑖𝑟𝑚𝑒𝑛𝑡 𝑡𝑜 𝑏𝑒 2.644 𝑚3/𝑠
𝐷𝑒𝑛𝑠𝑖𝑡𝑦 𝑜𝑓 𝑎𝑖𝑟 𝑡𝑜 𝑏𝑒 𝑎𝑠𝑠𝑢𝑚𝑒𝑑 𝑎𝑠 1.2 𝑘𝑔/𝑚3
ℎ 𝐻𝑅 = 𝐻𝑒𝑎𝑡 𝑟𝑒𝑐𝑜𝑣𝑒𝑟𝑦 𝑎𝑖𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑡𝑜 𝑏𝑒 54.5 𝑘𝐽/𝑘𝑔
ℎ 𝑆 = 𝑆𝑢𝑝𝑝𝑙𝑦 𝑎𝑖𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑡𝑜 𝑏𝑒 47.0 𝑘𝐽/𝑘𝑔
Therefore:
𝑄 𝑐 = (2.644 × 1.2) × (54.5 − 47.0)
𝑸 𝒄 = 𝟐𝟑. 𝟖𝟎 𝒌𝑾
The acquired values from the equation above have been selected based on the plotted psychometric chart
as seen on Page 28 where the summer psychometric process incorporating the MVHR Unit application to
the bedroom space. From the equation, set out above the cooling coil has been sized to be 23.80 kW.
From the SPC2000 software, the calculated cooling coil capacity was sized to be 23.61 kW, which when
compared to the manual calculation result show that the cooling coil capacity calculated is a reliable value
to use based on two significant figures.

29. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
25
Furthermore, the actual room humidity condition can be determined by plotting the Room Ration Line
(RRL) on a psychometric chart. This is calculated by using the following calculation.
𝑹𝑹𝑳 =
𝑸 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆
𝑸 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 + 𝑸 𝑳𝒂𝒕𝒆𝒏𝒕
Where:
𝑅𝑅𝐿 = 𝑅𝑜𝑜𝑚 𝑟𝑎𝑡𝑖𝑜 𝑙𝑖𝑛𝑒 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑄 𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 = 𝑆𝑢𝑚𝑚𝑒𝑟 𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝑔𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 12.51 𝑘𝑊
𝑄 𝐿𝑎𝑡𝑒𝑛𝑡 = 𝑆𝑢𝑚𝑚𝑒𝑟 𝑙𝑎𝑡𝑒𝑛𝑡 𝑔𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 24.07 𝑘𝑊
Therefore:
𝑅𝑅𝐿 =
12.51
12.51 + 24.07
𝑹𝑹𝑳 = 𝟎. 𝟑𝟒
By plotting the RRL from the supply condition plotted, the room humidity condition at 22 °C can be
confirmed on the psychometric chart. To give an indicative idea of how the summer process will be a
mock psychometric chart has been created in Figure 15 to illustrate this process.
Heat Recovery Process RRL
Cooling Coil Load
From the indicative psychometric process shown in figure … the heat recovery process as plotted seems to
play no benefit in the overall of the air handling unit siszing therefore the decision has been made to avoid
the heat recovery process during the summer months for when the external temperatures exceed to
calculated heat recovery condition from sensors controlling the allotment of the heat recovery process
between the returning air from the pool space and the fresh air supply from outside to occur. Therefore
the following calculation process will determine the off coil condition to ultimately re-design the cooling
coil size and the supply condition of the fresh air into the pool space as follows.
The required off coil supply condition is to be confirmed with the aid of the software SPC2000, which by
inputting the following values will determine the off coil condition that is required to size the cooling coil
within the MVHR Unit.
 Air onto the cooling coil Dry Bulb is to be 26.1 °C
 Air onto the cooling coil Wet Bulb is to be 18.4 °C
 Air off the cooling coil Dry Bulb is to be 22 °C
 Mass Flow Required to be 2.644 m3
/s
1
2
3
4
12
3
Figure 15 - Illustration of the Psychometric Process during Summer Conditions

30. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
26
Figure 16 - Revised Off coil condition confirmed with the use SPC Coils software
From inputting the following information as shown in Figure 16 the off coil condition has been determined
as well as the face velocity and calculated cooling capacity as follows.
From the SP Coils software, the following results were produced:
 Off Coil Wet Bulb Temperature = 17.0 °C
 Face Velocity = 5.74 m/s
 Cooling Coil Capacity = 13.44 kW
It should be taken into account that the supply rate calculated included a 10% increase margin to
compensate for commission purposes.
As previously mentioned with regards to the face velocity involved with the sizing of the cooling coil, the
re-calculated face velocity is 5.74 m/s which ensures that the requirement of moisture eliminators will be
utilised to ensure that the provision of possible moisture build up being blown over the coils is eliminated.
Furthermore, from re-designing the sized cooling coil for the air handling unit to provide the necessary
supply conditions into the pool by passing the heat recovery process shows that a 10.17 kW saving is
apparent which is beneficial for the air handling unit design as it ensures there are no oversizing of
components involved in the design. A manual calculation will also be carried out to ensure the reliability of
he provided cooling coil duty output from the SPC Coils software.
The required size of the cooling coil can be determined by using the following calculation:
𝑸 𝒄 = 𝒎 𝒐 × (𝒉 𝑶 − 𝒉 𝑺)
Where:
𝑄 𝑐 = 𝐶𝑜𝑜𝑙𝑖𝑛𝑔 𝑐𝑜𝑖𝑙 𝑙𝑜𝑎𝑑 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑚 𝑜 = 𝐹𝑟𝑒𝑠ℎ 𝑎𝑖𝑟 𝑟𝑒𝑞𝑢𝑖𝑟𝑚𝑒𝑛𝑡 𝑡𝑜 𝑏𝑒 2.644 𝑚3
/𝑠
𝐷𝑒𝑛𝑠𝑖𝑡𝑦 𝑜𝑓 𝑎𝑖𝑟 𝑡𝑜 𝑏𝑒 𝑎𝑠𝑠𝑢𝑚𝑒𝑑 𝑎𝑠 1.2 𝑘𝑔/𝑚3
ℎ 𝑂 = 𝐻𝑒𝑎𝑡 𝑟𝑒𝑐𝑜𝑣𝑒𝑟𝑦 𝑎𝑖𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑡𝑜 𝑏𝑒 51.7 𝑘𝐽/𝑘𝑔
ℎ 𝑆 = 𝑆𝑢𝑝𝑝𝑙𝑦 𝑎𝑖𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑡𝑜 𝑏𝑒 47.5 𝑘𝐽/𝑘𝑔
Therefore:
𝑄 𝑐 = (2.644 × 1.2) × (51.7 − 47.5)
𝑸 𝒄 = 𝟏𝟑. 𝟑𝟑 𝒌𝑾
From the produced manual calculation process, the SPC Coils software has proven itself to provide reliable
results based on the acquired cooling coil load to be accurate to two significant figures.
Furthermore, the actual room humidity condition can be determined by plotting the Room Ration Line
(RRL) on a psychometric chart. This is calculated by using the following calculation.
𝑹𝑹𝑳 =
𝑸 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆
𝑸 𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 + 𝑸 𝑳𝒂𝒕𝒆𝒏𝒕
Where:
𝑅𝑅𝐿 = 𝑅𝑜𝑜𝑚 𝑟𝑎𝑡𝑖𝑜 𝑙𝑖𝑛𝑒 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑄 𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 = 𝑆𝑢𝑚𝑚𝑒𝑟 𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝑔𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 12.51 𝑘𝑊
𝑄 𝐿𝑎𝑡𝑒𝑛𝑡 = 𝑆𝑢𝑚𝑚𝑒𝑟 𝑙𝑎𝑡𝑒𝑛𝑡 𝑔𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 24.07 𝑘𝑊
Therefore:
𝑅𝑅𝐿 =
12.51
12.51 + 24.07
𝑹𝑹𝑳 = 𝟎. 𝟑𝟒

31. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
27
By plotting the RRL from the supply condition plotted, the room humidity condition at 22 °C can be
confirmed on the psychometric chart. To give an indicative idea of how the summer process will be a
mock psychometric chart has been created in Figure 17 to illustrate this process.
Cooling Coil Load RRL
Following the determined process for the winter and summer conditions externally for the Swimming Pool
Space, the final psychometric charts have been provided as follows.
1 3
4
1
2
Figure 17 - Revised Illustration of the Psychometric Process during Summer Conditions

32. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
28

33. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
29

34. Report 3 – Mechanical – Specialist Zone – Swimming Pool Space
30