Report 2 - Mechanical - Functional Zone

Projects
Projects
Intended for
Northumbria University Newcastle
Student no.
W12001941
Date
18th
May 2016
Word Count
14625
REPORT 2 – MECHANICAL
FUNCTIONAL ZONE – 5 STAR
ACCOMODATION SPACE

Report 2 – Mechanical - Functional Zone – 5 Star Accomodation Space
CONTENTS
1. Executive summary 1
2. Introduction 2
3. Heating Load calculation 4
3.1 Infiltration 4
3.2 Fabric Heat Loss 5
3.3 Comparison of Heating Load Results 7
4. Cooling Load calculation 8
4.1 Internal Gain Calculation 8
4.2 Solar Gain Calculation 8
4.3 External Conduction Gain Calculation 8
4.4 Total Heat Gain Comparison 10
5. Ventilation and Air conditioning Design 11
5.1 Heat Recovery Condition Calculation 11
5.2 Cooling Coil Sizing 12
5.3 Heating Coil Sizing 14
5.4 Control Strategy 15
5.5 Condensate Removal 15
5.6 Ductwork and Fittings design 16
5.7 Pressure Loss through Ductwork Calculation 16
5.8 Louvre Sizing 19
5.9 Attenuator Sizing 20
5.10 Supply Diffuser Sizing 21
5.11 Extract Grille Sizing 22
5.12 Psychometric Charts 23
6. Heating Design 26
6.1 Radiator Sizing 26
6.2 Radiator Design and Distribution 28
6.3 Radiator Pipe sizing 29
6.4 Radiator Pipe Sizing Comparison 30
7. Domestic Water Services Design 32
7.1 Domestic Water Services Peak Flow Rate Calculation 32
7.2 Domestic Water Services Valve Arrangement 33
7.3 Domestic Water Services Pipe Sizing 33
7.4 Domestic Water Services Hevacomp Calculation 35
7.5 Domestic Water Services Pipe Sizing Comparison 36
8. Above Ground Drainage Design 37
8.1 Analysis of Drainage Pipework 37
8.2 Waste Water Flow Rate Calculation 38
9. Drawings 40
9.1 Domestic Water Services Distribution 40
9.2 Ventilation and Air Conditioning Distribution 41
9.3 Heating Services Distribution 42
10. Further Design Considerations 43
11. Bibliography 44
12. Appendices 45
12.1 MVHR Manufactures Data 45
12.2 Radiator (Bathroom Space) Manufactures Data 47
12.3 Radiator (Entrance Space) Manufactures Data 48

TABLES
Table 1 - Initial Design Criteria of 5 Star Accommodation Space............................................................... 2
Table 2 - Calculation of surface area of each construction used in the Bedroom Space ................................ 6
Table 3 - Calculation of total surface area corresponding thermal resistance for each construction used in the
Bedroom Space.................................................................................................................................. 6
Table 4 - estimate of Internal Gain within the five Star Accommodation Space........................................... 8
Table 5 - Calculation of Final Total Cooling Load for each space within five Star Accommodation .................10
Table 6 - Preliminary Data for Bedroom Spaces within five Star accommodation floor to design to ..............11
Table 7 - Final Selection of MVHR Unit's requirements and sizing ............................................................15
Table 8 - Maximum provided design conditions into Bedroom Space ........................................................15
Table 9 - Ductwork Fittings in Section 1 ...............................................................................................17
Table 10 - Pressure loss through straight ductwork calculation................................................................18
Table 11 - Total Pressure loss through section of ductwork.....................................................................19
Table 12 - Comparison of Results obtained using Manual and Heavacomp calculations ...............................19
Table 13 - Finalised selection data from figure .... for Linear Slot Diffuser ................................................22
Table 14 - Finalised selection data from figure .... for two Way blow Diffuser ............................................23
Table 15 - Finalised Heat Loss results based on IES Virtual Environment ..................................................26
Table 16 - Preliminary Selection of Radiators produced by Stelrad (Stelrad.co.uk).....................................26
Table 17 - Final Selection of Radiators .................................................................................................28
Table 18 - Heating Pipe Sizing Comparison...........................................................................................31
Table 19 - Outlets used in Bathroom Space and the Loading Units and respected Flow Rates,.....................32
Table 20 - Hot and Cold Peak Demand Flow rates for Bathroom Space.....................................................32
Table 21 - Summary of Loading Units and relevant flow rate to each draw off point...................................33
Table 22 - Domestic Water Services Pipe sizing comparison....................................................................36
Table 23 - Initial Design data for Above Ground Design within the Bathroom Space...................................38
Table 24 - Pipe diameter values taken from BS EN 12056-2 ...................................................................38
Table 25 - Discharge Units for each sanitary appliance within the Bathroom Space provided by BRE above
Ground Drainage Guide......................................................................................................................38

FIGURES
Figure 1 - Zone Layout of five star accommodation spaces ...................................................................... 2
Figure 2 - Occupational profile for Bedroom Space ................................................................................. 3
Figure 3 - Fabric Performance of Constriction used within five Star Accommodation Space .......................... 3
Figure 4 - Illustrated motion of Heat Loss through five star accommodation spaces .................................... 4
Figure 5 - Snapshot of Bedroom Space with dimensions to calculate internal surface area........................... 5
Figure 6 - Mechanical Heat Recovery Process within five star accommodation spaces.................................11
Figure 7 - Off Coil Condition Calculation from SPC2000 Software.............................................................12
Figure 8 - Mechanical Heat Recovery Process within five star accommodation spaces.................................12
Figure 9 - Summer Psychometric Process of the MVHR Unit ....................................................................13
Figure 10 - Winter Psychometric Process of the MVHR Unit .....................................................................14
Figure 11 - Configuration of MVHR Unit in Bedroom Space .....................................................................15
Figure 12 - Proposed ventilation design for Bedroom Space ....................................................................16
Figure 13 - Example of Circular Galvanised Ductwork used in the Bedroom Space Ventilation Design...........16
Figure 14 - Pressure Drop for air in galvanised circular ducts as found in CIBSE Guide C Figure 4.2,
(Representitives, CIBSE Guide C Reference Data, 2007) ........................................................................17
Figure 15 - Elbow values of varying with velocity as shown in CIBSE Guide C Table 4.20............................18
Figure 16 - Heavacomp ventilation design for Bedroom Space ................................................................19
Figure 17 - Indicative Louvre Spacing requirement for Five Star Accomodation Space................................20
Figure 18 - Indicative representation of Fixed Diffuser Bladesto be used in Grille Fittings ...........................21
Figure 19 - Sizing Nomogram for Linear Slot Diffuser produced by Gilberts Manufacture
(Gilbertsblackpool.co.uk)....................................................................................................................22
Figure 20 - Sizing table produced by Gilberts Manufactures for 2-way blow diffuser (Gilbertsblackpool.co.uk)
.......................................................................................................................................................23
Figure 21 - Preliminary selection of Stelrad Radiators in Bathroom Space (Stelrad.co.uk)...........................26
Figure 22 - Preliminary selection of Stelrad Radiators in Entrance Space (Stelrad.co.uk) ............................26
Figure 23 - Illustrated method of convection using LST Radiators............................................................27
Figure 24 - Process of calculating Radiant Mean and Mean Fluid Temperatures..........................................27
Figure 25 - Three Port Valve control to be used in Radiators ...................................................................29
Figure 26 - CIBSE Pipe sizing Spreadsheet for Heating Pipework .............................................................29
Figure 27 - Pipe sizing for Galvanised steel from CIBSE Guide C4 Table 4.34, (Representitives, CIBSE Guide C
Reference Data, 2007).......................................................................................................................30
Figure 28 - Indicative representation of Heating System distributioin in Five Star Accomodation Space ........30
Figure 29 - Heating Distribution Layout using Hevacomp........................................................................31
Figure 30 - Proposed Zone for Domestic Water Services Design ..............................................................32
Figure 31 - Distribution Layout of Domestic Water services with indicative lengths of pipework...................33
Figure 32 - CIBSE Pipe sizing Spreadsheet for Cold Water Pipework ........................................................34
Figure 33 - CIBSE Pipe sizing Spreadsheet for Hot Water Flow Pipework ..................................................34
Figure 34 - Cold Water Domestic Services Hevacomp Distribution Layout .................................................35
Figure 35 - Hot Water Domestic Services Hevacomp Distribution Layout ..................................................35
Figure 36 - Illustration of a typical Branch tee to be found in Bathroom Space ..........................................37
Figure 37 - Illustration of Drainage dessign to avoid cross flow into other branch tee.................................37

1
1. EXECUTIVE SUMMARY
This report will go through the design analysis of the Functional Zone chosen within this Hotel project
to be the Five Star Accommodation space. The functional zone is selected based on the system
provision on a particular zone where similar design requirements will be found in the majority of the
building. with regards to the five star accommodation, the loads associated are similar throughout the
whole five star accommodation spaces, therefore the systems provided with the design of selected
five star accommodation space will be applied to the other spaces as follows.
The systems analysed will include the ventilation and air conditioning provision, heating, domestic
water services and the above ground drainage design of the space. These system design approaches
will be limited to within the five star accommodation space as the main plant requirements have
already been analysed within Report 1 for All Zone Mechanical Design.
The systems designed within the five star accommodation spaces will be calculated using manual
calculations and then compared with results obtained from other calculation procedures such as BSRIA
Guides and software results, which then will be analysed on their accuracy and reliability from the
obtained results. After completion of the whole design of the five star accommodation spaces, drawing
will be produced to finalise the system provision to the space in whole.

2
2. INTRODUCTION
This report will go through the design process of the five star accommodations
within the hotel project. The selection of systems will be all based on manual
calculations which will compare with previously calculated results obtained from
software’s and discuss the variety of results obtained. The five star
accommodations are being designed to accommodate the occupants who pay
more for better accommodation in terms of design conditions and comfortability.
Therefore, the ventilation and air conditioning systems, heating and domestic
water services need to be designed to a high specification and be able to be
controlled well by the occupants.
The five star accommodation floors take up two of the 20 floors in the building.
The 19th
floor will be the floor, which this report will be based upon as all
calculations and discussions will be concluded in the design of all hotel bedrooms
amongst these floors.
The five star accommodation floors consist of four bedroom spaces each with
generous spaces as shown in Figure 1 each of these spaces have been given a
colour code which will be useful during the report as it distinguishes the zones
within each bedroom spaces so as to design the appropriate system for each
zone.
Below is a table of the design conditions, which have been already confirmed
with the client for the five star bedrooms as shown in Table 1 the data from the
table have been acquired from CIBSE Guide A, (Parand, 2015) and based on
recommendations for each space where the engineer has confirmed the final
data.
Table 1 - Initial Design Criteria of 5 Star Accommodation Space
Area Type Space Colour
Room Design Data Temperatures Ventilation
Occupants (m2
/P)
Equipment Gain
(W/m2
)
Lighting Gain
(W/m2
)
Winter (minimum)
(°C)
Summer
(maximum) (°C)
Room Change Rate Fresh Air Supply
Bedroom 1 Blue 10 2.5 12 19 22 - 10 l/s/p
Bedroom 2 Red 10 2.5 12 19 22 - 10 l/s/p
Bathroom Yellow - - 5.63 20 24 21 l/s -
Entrance Green - - 3.75 19 22 - -
Figure 1 - Zone Layout of five star accommodation spaces

3
The five star accommodations will be designed to specific times of the day depending on heating,
cooling and requirement of domestic water through the day. Below is a breakdown of the occupants
present within the spaces during the day being represented as a graph in Figure 2.
As shown in Figure 2 the occupational behaviour within the bedroom space shown the occupants will
be present within the space the longest during the evening period through to the morning due to
sleeping and resting. Therefore it is imperative that the design of the space meets design
requirements to when the occupants are present and modulates to when the occupants are not
present so that the client will be able to save on energy and costs from servicing the spaces.
The existing construction of the 5 star accommodation has been improved from the analysis
undergone in stage 2 where the fabric performances of the construction were improved by 25% as it
proved to reduce the heating and cooling loads by limited the amount of heat being lost through the
construction and the amount of heat being gained from adjacent spaces which ultimately kept the
spaces at their optimum design conditions.
The construction of five star accommodations is
shown in Figure 3, which gives a good
representation of the fabric performances that will
be involved with these spaces? The other spaces on
the five star accommodation floors will have similar
fabric performances so therefore heat loss will be
limited across spaces and limited further to
external constructions.
Glazing Construction
U Value – 1.65 W/m2
K
External Wall
Construction
K
Internal Partition
Construction
K
Door Construction
K
Internal Floor / Ceiling
Construction
K
Figure 3 - Fabric Performance of Constriction used within five Star Accommodation Space
Figure 2 - Occupational profile for Bedroom Space

4
3. HEATING LOAD CALCULATION
The heat loss through the five star accommodations will determine was heating requirements will be
needed in terms of air conditioning the spaces through winter conditions. When calculated the final
heat loss value for the spaces within the five star accommodations, it will be compared against the
heat loss value produced by IES Virtual
Environment and discuss if there are any
discrepancies with the results and why.
The motion of heat loss through the
spaces have been predicted in Figure 4
which gives an indicative idea of which
section of the fabric for each space the
heat loss calculation needs to be
conducted. On the same figure, there is
a preliminary calculation of the
differential temperature of the transfer
of heat from the higher dry bulb
temperature to the lower dry bulb
temperature, which makes part of the
heat loss calculation.
The Bedroom space highlighted within
Figure 4 will go through the heat loss
calculation and provide a breakdown of
what is involved in calculating the result.
This space has an external wall, internal
partition and glazing construction.
Therefore
3.1 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 in 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.
Heat Loss from
Bedroom to Outside
ΔT - 19°C – (-2.7°C)
= 21.7°C
Heat Loss from
Bedroom to Outside
ΔT - 19°C – (-2.7°C)
= 21.7°C
Heat Loss from
Bathroom to
Bedroom
ΔT - 20°C – 19°C =
21.7°C
Heat Loss from
Bedroom to
Circulation Space
ΔT - 19°C – Unheated
Space = 19°C
Heat Loss from
Bedroom to
Circulation Space
Space = 19°C
Heat Loss from
Entrance to
Circulation Space
Space = 19°C
Heat Loss from
Bedroom to
Circulation Space
Space = 20°C
Heat Loss from
Bathroom to Entrance
ΔT - 20°C – 19°C = 1°C
Figure 4 - Illustrated motion of Heat Loss through five star accommodation spaces

5
Initial Calculations:
𝐼𝑛𝑡𝑒𝑟𝑛𝑎𝑙 𝑆𝑢𝑟𝑓𝑎𝑐𝑒 𝐴𝑟𝑒𝑎 (𝑆)(𝑚2) = ((6.556 × 3.75) × 2) + ((3.96 × 3.75) × 2) + ((6.556 × 3.96) × 2) = 130.872 𝑚2
𝑉𝑜𝑙𝑢𝑚𝑒 𝑜𝑓 𝑆𝑝𝑎𝑐𝑒 (𝑚3) = ((6.556 × 3.96) × 3.75) = 97.36𝑚3
𝐴𝑖𝑟 𝐿𝑒𝑎𝑘𝑎𝑔𝑒 𝐼𝑛𝑑𝑒𝑥 𝑄50/𝑆 (𝑚3
/(ℎ. 𝑚2)) = 5.0 (𝑚3
/ℎ)/𝑚2
𝑡𝑖𝑛𝑠𝑖𝑑𝑒 = 19°𝐶
𝑡 𝑜𝑢𝑡𝑠𝑖𝑑𝑒 = −2.7°𝐶
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 𝑚𝑎𝑥𝑖𝑚𝑢𝑚 𝑎𝑖𝑟 𝑙𝑒𝑎𝑘𝑎𝑔𝑒 𝑖𝑛𝑑𝑒𝑥 𝑓𝑜𝑟 𝑔𝑜𝑜𝑑 𝑝𝑟𝑎𝑐𝑡𝑖𝑐𝑒 𝑖𝑠 𝑡𝑜 𝑏𝑒 5.0 (𝑚3
/ℎ)/𝑚2
Therefore:
𝐼 =
1
20
×
78.87
97.36
× 5.0
𝑰 = 𝟎. 𝟐𝟎𝟑 𝒂𝒄𝒉
From the calculated infiltration rate, the fabric heat loss now needs to be also calculated to calculate
the total heat loss for the Bedroom Space.
3.2 Fabric 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 required design information is as follows:
 Infiltration Rate – This has been calculated earlier in this report, which is 0.203 ach
 The inside dry resultant design temperature is to be 19°C
 The outside dry resultant temperature is -2.7°C
 The Fabric performances of the spaces are as follows:
Figure 5 - Snapshot of Bedroom Space with dimensions to calculate internal surface area

6
 Ground Floor – 0.19 W/m2
K
 Roof – 0.19 W/m2
K
 Door – 2.63 W/m2
K
 Partition – 1.31 W/m2
K
 External Wall – 0.26 W/m2
K
 Glazing – 1.65 W/m2
K
The following calculation procedure is carried out by BSRIA Guide to HVAC Calculations, (BSRIA,
2007) which he next thing to determine is the surface area of each of the constructions listed out
above to proceed with the fabric heat loss calculation.
Table 2 - Calculation of surface area of each construction used in the Bedroom Space
Ground
Floor
Roof Door Partition
External
Wall
Glazing
North Face - - - -
(6.556m ×
3.75m) –
18.029m2
=
6.556m2
(6.556m ×
2.75m) =
18.029m2
East Face - - -
(3.96m ×
3.75m) =
14.85m2
-
South Face - -
(0.91m ×
2.1m) =
1.911m2
((1.61 ×
3.75) –
1.911 m2
) +
(4.946m ×
3.75m)=
22.674 m2
- -
West Face - - -
(3.96m ×
3.75m) =
14.85m2
- -
Ceiling Face -
(6.556m ×
3.96m) =
25.962m2
- - - -
Ground
Face
(6.556m ×
3.96m) =
25.962m2
- - - - -
Total 25.962m2
25.962m2
1.911m2
52.374m2
6.556m2
18.029m2
Σ(A) = 130.872m2
The calculated surface areas of the Bedroom Space about each construction used within the space and
the total surface area of the whole space, which will come in use later on in the fabric heat loss
calculation, is shown in Table 3.
The total calculated surface area corresponding thermal resistance can now be calculated with regards
to each construction used in the Bedroom Space.
Table 3 - Calculation of total surface area corresponding thermal resistance for each construction used in the
Bedroom Space
Ground
Floor
Roof Door Partition
External
Wall
Glazing
North Face - - - -
(0.26W/m²K
× 6.556m²)
= 1.70W/K
(1.65W/m²K
× 18.029m²)
=
29.75W/K
East Face - - -
(1.31W/m²K
× 14.85m²)
=
19.45W/K
- -
South Face - -
(2.63W/m²K
× 1.911m²)
= 5.03W/K
(1.31W/m²K
×
22.674m²)
=
29.70W/K
- -
West Face - - -
(1.31W/m²K
× 14.85m²)
=
19.45W/K
- -
Ceiling
Face
-
(0.19W/m²K
× 25.96m²)
= 4.93W/K
- - - -
Ground
Face
(0.19W/m²K
× 25.96m²)
= 4.93W/K
- - - - -
Σ(AU) = 114.94 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 now be used in the calculkation process to determine the final total heat loss
based on the difference in temperature against the adjacent space conditions to the space in question.

7
Ground
Floor
Roof Door Partition
External
Wall
Glazing
North Face - - - -
-2.7°C
Δ25.7°C
-2.7°C
Δ25.7°C
East Face - - -
19°C
Δ0°C
- -
South Face - -
19°C
Δ1°C
20°C
Δ1°C
- -
West Face - - -
19°C
Δ0°C
- -
Ceiling Face -
19°C
Δ0°C
- - - -
Ground
Face
19°C
Δ0°C
- - - - -
As the table above outlines the difference in temperature against the adjacent spaces to that of the
Bedroom space where the calculation process is based on. This information produced can be utilised
further by multiplying the calculated total surface area with corresponding thermal resistance values
for each of the constructions found in the Bedroom space with the temperature difference of the
adjacent spaces as shown below.
Ground
Floor
Roof Door Partition
External
Wall
Glazing
North Face - - - -
(1.7 W / K
× Δ 25.7 K)
= 43.69 W
(29.75 W /
K × Δ 25.7
K) =
764.58 W
East Face - - -
(19.45 W /
K × Δ 0 K)
= 0 W
- -
South Face - -
(5.03 W / K
× Δ 1 K) =
5.03 W
(29.70 W /
K × Δ 1 K)
= 29.70 W
- -
West Face - - -
(19.45 W /
K × Δ 0 K)
= 0 W
- -
Ceiling Face -
(4.93 W / K
× Δ 0 K) =
0 W
- - - -
Ground
Face
(4.93 W / K
× Δ 0 K) =
0 W
- - - - -
Σ(W) = 843.0 W
From the total heat loss calculation the produced value from using manual calculation is 0.843 kW of
heat loss from the Bedroom Space
3.3 Comparison of Heating Load Results
The aquired value for the same Bedroom Space as chosen at the beginning of this section of the
report from using the IES Virtual Environment software is as follows.
 Total Heat Loss of Bedroom Space – 1.08kW
The IES Virtual Environemtn value for heat loss was calculated using the same initial design criteria,
however as it shows the manual calculated heat loss value is slightly less in terms of calculated
heating load. This is due to the Heating load produced by IES VE including solar gain loads during the
winter months as the simulation was ran with includance of the solar gain being present.

8
4. COOLING LOAD CALCULATION
The process of calculating the heat gains within the 5 star
accomodation spaces is to estimate how the effects of heat gaisn will
effect the design condition of the space with no cooling systems in use.
By doing this will provide an estimate of what heat gain load the cooling
system will need to offset when sized later on in this report.
The heat gain calculation will depend on the internal gains within the
space such as lighting, equipment and occupants. These gains have
been outlined in Table 5 which is shown in Watts per meters squared
form which has been converted into Watts so as to progress with the
heat gain calculation.
4.1 Internal Gain Calculation
The areas of the spaces as shown in Table 5 have been aquired from the floor plans created by the
client in designing this project. The Watts per meters squared values have been aquired from CIBSE
Guide A Section 6 which are dependant upon the type of space that is used for. The occupants Watts
per meter squared value is dependant upon the activity the occupants will be doing within that given
space. As it is a Bedroom Space the occupants are believed to be in a restful state so therefore a low
sensible gain is expected.
Further more, the internal heat gains within the space are not only the heat gains that the Bedroom
space will encounter. Solar Gain is also another value which will be experienced as well as External
Conduction Gain which will be calculated as follows.
4.2 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 oritentation for various locations in Table 5.2, (Representitives, CIBSE Guide C Reference Data,
2007). 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.
Table 4 - estimate of Internal Gain within the five Star Accommodation Space
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 18.029 𝑚2
𝐺 𝑉𝑎𝑙𝑢𝑒 𝑜𝑓 𝑔𝑙𝑎𝑧𝑖𝑛𝑔 𝑡𝑜 𝑏𝑒 0.3 𝜃𝑆
Therefore:
𝑄 𝑆𝑜𝑙𝑎𝑟 𝐺𝑎𝑖𝑛 = (355 × 18.029) × 0.3
𝑸 𝑺𝒐𝒍𝒂𝒓 𝑮𝒂𝒊𝒏 = 𝟏𝟗𝟐𝟎. 𝟎𝟗 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.
4.3 External Conduction Gain Calculation
The external conduction gain into the space now needs to also be confirmed by using the following
calculation.
𝑸 𝑬𝒙𝒕𝒆𝒓𝒏𝒂𝒍 𝑪𝒐𝒏𝒅𝒖𝒄𝒕𝒊𝒐𝒏 = 𝒎 × ∆𝒉
Where:
Area (m2
)
Occupants Equipment Lighting
(P) (W/P) (W) (W/m2
) (W) (W/m2
) (W)
Bedroom Space 1 25.96 2 70 140 2.5 64.90 12 311.52
Bedroom Space 2 32.79 2 70 140 2.5 64.90 12 311.52
Bathroom Space 14.41 - - - - - 5.63 81.13
Entrance Space 5.79 - - - - - 3.75 21.71

9
𝑄 𝐸𝑥𝑡𝑒𝑟𝑛𝑎𝑙 𝐶𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑜𝑛 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑚 = (
(𝑎𝑐ℎ × 𝑣𝑜𝑙𝑢𝑚𝑒)
3600
) × 𝐷𝑒𝑛𝑠𝑖𝑡𝑦 𝑜𝑓 𝑎𝑖𝑟 = (
(0.203 × 97.36)
3600
) × 1.2 = 0.0066 𝑘𝑔/𝑠
∆ℎ = 𝐸𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑑𝑖𝑓𝑓𝑒𝑟𝑒𝑛𝑐𝑒 𝑏𝑒𝑡𝑤𝑒𝑒𝑛 𝑒𝑥𝑡𝑒𝑟𝑛𝑎𝑙 𝑎𝑛𝑑 𝑟𝑜𝑜𝑚 𝑐𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛𝑠
Therefore:
𝑄 𝐸𝑥𝑡𝑒𝑟𝑛𝑎𝑙 𝐶𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑜𝑛 = 0.0066 × (51.95 − 48.30)
𝑸 𝑬𝒙𝒕𝒆𝒓𝒏𝒂𝒍 𝑪𝒐𝒏𝒅𝒖𝒄𝒕𝒊𝒐𝒏 = 𝟎. 𝟎𝟐𝟒𝟏 𝒌𝑾
From the calculated external conduction value, the sensible heat ratio can be confirmed by dividing
the Internal enthalpy by the External conditions enthalpy which produces the following value.
𝑺𝑯𝑹 =
𝑰𝒏𝒕𝒆𝒓𝒏𝒂𝒍 𝑬𝒏𝒕𝒉𝒂𝒍𝒑𝒚
𝑬𝒙𝒕𝒆𝒓𝒏𝒂𝒍 𝑬𝒏𝒕𝒉𝒂𝒍𝒑𝒚
Where:
𝐼𝑛𝑡𝑒𝑟𝑛𝑎𝑙 𝐸𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑡𝑜 𝑏𝑒 48.30 𝑘𝐽/𝑘𝑔
𝐸𝑥𝑡𝑒𝑟𝑛𝑎𝑙 𝐸𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑡𝑜 𝑏𝑒 51.95 𝑘𝐽/𝑘𝑔
Therefore:
𝑆𝐻𝑅 =
48.30
51.95
𝑺𝑯𝑹 = 𝟎. 𝟗𝟑
The sensible and latent gains can be confirmed with the use of the calculated Sensible heat ratio value
by the following processes.
For Sensble Conduction Gain:
𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 𝑮𝒂𝒊𝒏 = 𝑺𝑯𝑹 × 𝑬𝒙𝒕𝒆𝒓𝒏𝒂𝒍 𝑪𝒐𝒏𝒅𝒖𝒄𝒕𝒊𝒐𝒏 𝑮𝒂𝒊𝒏
Where:
𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝐺𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑆𝐻𝑅 ℎ𝑎𝑠 𝑏𝑒𝑒𝑛 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑 𝑡𝑜 𝑏𝑒 0.93
𝐸𝑥𝑡𝑒𝑟𝑛𝑎𝑙 𝐶𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑜𝑛 𝐺𝑎𝑖𝑛 ℎ𝑎𝑠 𝑏𝑒𝑒𝑛 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑 𝑡𝑜 𝑏𝑒 0.0241 𝑘𝑊
Therefore:
𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝐺𝑎𝑖𝑛 = 0.93 × 0.00241
𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 𝑮𝒂𝒊𝒏 = 𝟎. 𝟎𝟎𝟐𝟐𝟒𝟏𝟑 𝒌𝑾
For Latent Conduction Gain:
𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 𝑮𝒂𝒊𝒏 = (𝟏 − 𝑺𝑯𝑹) × 𝑬𝒙𝒕𝒆𝒓𝒏𝒂𝒍 𝑪𝒐𝒏𝒅𝒖𝒄𝒕𝒊𝒐𝒏 𝑮𝒂𝒊𝒏
Where:
𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝐺𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑆𝐻𝑅 ℎ𝑎𝑠 𝑏𝑒𝑒𝑛 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑 𝑡𝑜 𝑏𝑒 0.93
𝐸𝑥𝑡𝑒𝑟𝑛𝑎𝑙 𝐶𝑜𝑛𝑑𝑢𝑐𝑡𝑖𝑜𝑛 𝐺𝑎𝑖𝑛 ℎ𝑎𝑠 𝑏𝑒𝑒𝑛 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑 𝑡𝑜 𝑏𝑒 0.0241 𝑘𝑊
Therefore:
𝑆𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝐺𝑎𝑖𝑛 = (1 − 0.93) × 0.00241
𝑺𝒆𝒏𝒔𝒊𝒃𝒍𝒆 𝑮𝒂𝒊𝒏 = 𝟎. 𝟎𝟎𝟎𝟏𝟔𝟖𝟕 𝒌𝑾

10
4.4 Total Heat Gain Comparison
The total heat gain calculation will be total of all the previously calculated heat gains in associatiation
with the five star accomodation heat gains, where the total cooling load required to offse thse heat
gains can be determined. Threfore total heat gain values can now be calculated as follows.
Table 5 - Calculation of Final Total Cooling Load for each space within five Star Accommodation
Spaces
Sensible Heat
Gain (kW)
Latent Heat
Gain (kW)
Total Cooling
Load (kW)
IES VE Total
Cooling Load
(kW)
BSRIA Guide
Rule of
Thumb
Cooling Load
(kW)
Bedroom
Space 1
(0.140 +
0.0649 +
0.31152 +
0.0022413) =
0.5164 kW
(0.009 +
0.0001687) =
0.0092 kW
(0.5164 +
0.0092) =
0.5256 kW
1.62 kW 3.894 kW
Bedroom
Space 2
(0.140 +
0.0649 +
0.31152 +
0.0022413) =
0.5164 kW
(0.009 +
0.0001687) =
0.0092 kW
(0.5164 +
0.0092) =
0.5256 kW
2.16 kW 4.919 kW
Bathroom
Space
(0.08113 +
0.0022413) =
0.0834 kW
0.0002 kW
(0.0834
+0.0002) =
0.0836 kW
- 2.162 kW
Entrance
Space
(0.02171 +
0.0022413) =
0.0240 kW
0.0002 kW
(0.0240 +
0.0002) =
0.0242 kW
- 0.869 kW
From the calculated total cooling loads for each of the spaces of the 5 star accomodation spaces, these
results can be compared to that produced by IES Virtual Environemnt and the values set out by BSRIA
Guide Rule of Thumb 5th
Edition.
The gaps within the table for the IES VE produced results show that the model was created on the
basis that there will be no need for Cooling requirements for the Bathroom and Etrance spaces so
therefore there loads were to be not calculated. There is a wide range of results produced within Table
6 for determining the cooling load due to the different methods of determining the correct load. For
this report the IES VE method will be chosen as the most accurate method of calculating the Cooling
load as within the manual calculation the internal conduction gaisn were not calculated which will be a
contributing factor to the total cooling load which was howveer taken into account by the IES VE
software.

11
5. VENTILATION AND AIR CONDITIONING DESIGN
The ventilation and air conditioning requirements for the five star accommodation spaces are only
required for the Bedroom space as there are occupants present in only that space. It has been decided
to use Mechanical ventilation heat recovery boxes within the Bedroom spaces instead of Air Handling
Units, which will feed fresh air into the spaces via Variable Air Volume Units.
The benefits of using a Mechanical Ventilation Heat Recovery (MVHR) Unit are it limits the amount of
plant requirements. This then frees up space in the service risers and saves space in the main plant
area. Another benefit is it provides better maintenance to the plant supplying each individual space as
each unit will be located within each space.
The specific unit chosen for this application has a high efficiency plate exchanger, which is able to
recover sensible and latent gains within the spaces, which will benefit this application, as there are
occupants within the space.
Firstly, the MVHR Unit will need to be proceeded through a series of calculations to prove that with the
plate heat exchanger alone there will be sufficient cooling provided into the space during the summer
periods. During the winter periods, it is initially agreed that the MVHR Unit will be of no use as the
external design temperatures as shown in Table 7 deemed too low to be able to provide sufficient
heating requirements with the specified heat recovery efficiency of 0.9 as stated by Mitshibushi Air
Conditioning Manufactures.
As the MVHR Unit will only be looking into supplying the cooling requirements during the summer,
conditions to provide the Bedroom spaces with required internal design conditions, from Table 7 the
design conditions for summer periods will only be needed. From the calculated heat gains experienced
within the Bedroom space, it is important that the MVHR Unit is able to offset those gains and provide
a good living condition for the occupants within the space.
Table 6 - Preliminary Data for Bedroom Spaces within five Star accommodation floor to design to
The process of the MVHR Unit is shown above in Figure 6 where the external outside summer air will
be supplied into the ceiling void via a louvre, which will require sizing later on through this report. As
the outside air is being supplied into the ceiling void, it will enter the MVHR Unit and begin the process
of heat exchange via the plate exchanger with the return air from the Bedroom Space. The idea is the
return air will cool down the supply condition sufficiently enough so that after the heat recovery
process within the MVHR Unit the tempered air will be able to be supplied into the Bedroom Space to
provide cooling to the space to reach design conditions during summer.
5.1 Heat Recovery Condition Calculation
Firstly, the supply condition of the air under summer conditions when provided into the space needs to
be confirmed to make sure the MVHR Unit is capable of reaching the design conditions. Therefore, the
following calculation process will be undertaken.
Space
Colour
Space Identity
Occupants
(P)
Design Conditions (°C) Outside Conditions (°C)
Heating
Requirement
(kW)
Cooling
Requirement
(kW)
Fresh Air
Supply (l/s)
Winter Summer Winter Summer
Dry Bulb
Temp (°C)
Relative
Humidity
(%)
Dry Bulb
Temp (°C)
Relative
Humidity
(%)
Dry Bulb
Temp (°C)
Relative
Humidity
(%)
Dry Bulb
Temp (°C)
Wet Bulb
Temp (°C)
Blue Bedroom 1 4 19 30 - 70 22 30 – 70 -2.7 90 26.1 18.4 1.08 1.62 20
Red Bedroom 2 4 19 30 - 70 22 30 - 70 -2.7 90 26.1 18.4 1.08 2.16 20
Mechanical Heat Recovery Box with internal Heating and Cooling Coils
Situated in the Ceiling Void supplying five Star Accommodation Space
Figure 6 - Mechanical Heat Recovery Process within five star accommodation spaces

12
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 22°𝐶
𝑡 𝑂 = 𝑆𝑢𝑚𝑚𝑒𝑟 𝑜𝑢𝑡𝑠𝑖𝑑𝑒 𝑎𝑖𝑟 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 26.1°𝐶
Therefore:
𝑡 𝐻𝑅 = 0.9 × (22 − 26.1) + 26.1
𝒕 𝑯𝑹 = 𝟐𝟐. 𝟒𝟏 °𝑪
From the calculated heat recovered temperature supply condition, it shows that the supply
temperature is estimated to be 22.41°C, which is just above the design condition of the spaces during
the summer conditions. For a cooling supply condition being only a difference in supply temperature
and room temperature of 0.71°C. This however is not an acceptable difference between supply and
room conditions. It is seen in practice to have a difference of 8 - 10°C difference. So an additional
cooling requirement will be needed to reach supply conditions for the space.
When looking into possible equipment to provide localised heat recovery and provide cooling
requirements. The existing MVHR Unit can have an additional heat pump unit attached to the end of
the existing unit to create a similarly laid out localised Air Handling Unit. With this additional heat
pump unit is provided with a heating coil as well as the cooling coil. Therefore the MVHR Unit. Will also
take up the heating requirement for the space. For this new specified unit an outdoor unit will be
required to run the refrigerant through to the MVHR Unit to provide the heating and cooling
requirements, which will be sized through this report.
5.2 Cooling Coil Sizing
Looking at the illustrated process of the MVHR Unit now with the additional heating and cooling coil
included as shown in Figure 8 the cooling coil is required to be sized first based on summer conditions
and the required cooling load to offset the heat gains within the Bedroom space as set out in Table 7.
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 22.41 °C
 Air onto the cooling coil Wet Bulb is to be 17.4 °C
 Air off the cooling coil Dry Bulb is to be 14 °C
 Mass Flow Required to be 0.02 m3
/s
Mechanical Heat Recovery Box with internal Heating and Cooling Coils
Situated in the Ceiling Void supplying five Star Accommodation Space
Figure 8 - Mechanical Heat Recovery Process within five star accommodation spaces
Figure 7 - Off Coil Condition Calculation from SPC2000 Software

13
From inputting the following information as shown in figure…. 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 = 12.7 °C
 Face Velocity = 0.04 m/s
 Cooling Coil Capacity = 0.31 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.
However as the cooling coil sized has a face velocity of 0.04 m/s the problem has been avoided.
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 0.02 𝑚3
/𝑠
𝐷𝑒𝑛𝑠𝑖𝑡𝑦 𝑜𝑓 𝑎𝑖𝑟 𝑡𝑜 𝑏𝑒 𝑎𝑠𝑠𝑢𝑚𝑒𝑑 𝑎𝑠 1.2 𝑘𝑔/𝑚3
ℎ 𝐻𝑅 = 𝐻𝑒𝑎𝑡 𝑟𝑒𝑐𝑜𝑣𝑒𝑟𝑦 𝑎𝑖𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑡𝑜 𝑏𝑒 48.7 𝑘𝐽/𝑘𝑔
ℎ 𝑆 = 𝑆𝑢𝑝𝑝𝑙𝑦 𝑎𝑖𝑟 𝑒𝑛𝑡ℎ𝑎𝑙𝑝𝑦 𝑡𝑜 𝑏𝑒 36.4 𝑘𝐽/𝑘𝑔
Therefore:
𝑄 𝑐 = (0.02 × 1.2) × (48.7 − 36.4)
𝑸 𝒄 = 𝟎. 𝟑𝟎 𝒌𝑾
The acquired values from the equation above have been selected based on the plotted psychometric
chart as seen on Page 24 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 0.31 kW. From the SPC2000 software, the calculated cooling coil capacity was sized to be 0.31 kW,
which when compared to the manual calculation result show that the cooling coil capacity calculated is
a reliable value to use.
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 1.08 𝑘𝑊
𝑄 𝐿𝑎𝑡𝑒𝑛𝑡 = 𝑆𝑢𝑚𝑚𝑒𝑟 𝑙𝑎𝑡𝑒𝑛𝑡 𝑔𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 0.0092 𝑘𝑊
Therefore:
𝑅𝑅𝐿 =
1.62
1.62 + 0.0092
𝑹𝑹𝑳 = 𝟎. 𝟗𝟗𝟒
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 9 to illustrate this process.
Heat Recovery Process RRL
Cooling Coil Load Extract Process
1
2
3
4
1
2
3 4
Figure 9 - Summer Psychometric Process of the MVHR Unit

14
5.3 Heating Coil Sizing
The second component in the MVHR Unit, the heating coil now needs to be sized which will be based
on the winter outside conditions and heating load to compensate for the heat loss within the bedroom
space as set out in Table 6.
Firstly, the supply condition of the air under winter conditions when provided into the space needs to
be confirmed to make sure the MVHR Unit is capable of reaching the design conditions. Therefore, the
following calculation process will be undertaken.
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 19°𝐶
𝑡 𝑂 = 𝑆𝑢𝑚𝑚𝑒𝑟 𝑜𝑢𝑡𝑠𝑖𝑑𝑒 𝑎𝑖𝑟 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 − 2.7°𝐶
Therefore:
𝑡 𝐻𝑅 = 0.9 × (19 − (−2.7)) + (−2.7)
𝒕 𝑯𝑹 = 𝟏𝟔. 𝟖𝟑°𝑪
The calculated heat recovery condition is deemed too low of a supply condition into the space to
provide for heating. Therefore using a difference in temperature of 8 °C between the room conditions,
a supply temperature of 27 °C has been chosen. From the calculated heat recovery condition of the air
after the heat recovery process, the required size of the heating coil can be determined by using the
following calculation:
𝑸 𝒉 = 𝒎 𝒐 × 𝑪𝒑 × ∆𝑻
Where:
𝑄ℎ = 𝐻𝑒𝑎𝑡𝑖𝑛𝑔 𝐶𝑜𝑖𝑙 𝑠𝑖𝑧𝑒 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑚 𝑜 = 𝐹𝑟𝑒𝑠ℎ 𝑎𝑖𝑟 𝑟𝑒𝑞𝑢𝑖𝑟𝑚𝑒𝑛𝑡 𝑡𝑜 𝑏𝑒 0.02 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 𝐻𝑅 = 𝐻𝑒𝑎𝑡 𝑟𝑒𝑐𝑜𝑣𝑒𝑟𝑦 𝑑𝑟𝑦 𝑏𝑢𝑙𝑏 𝑎𝑖𝑟 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 16.83 °𝐶
𝑡 𝑆 = 𝑆𝑢𝑝𝑝𝑙𝑦 𝑑𝑟𝑦 𝑏𝑢𝑙𝑏 𝑎𝑖𝑟 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 27 °𝐶
Therefore:
𝑄ℎ = (0.02 × 1.2) × 1.02 × (27 − 16.83)
𝑸 𝒉 = 𝟎. 𝟐𝟓 𝒌𝑾
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 = 𝑊𝑖𝑛𝑡𝑒𝑟 𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒 𝑔𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 1.08 𝑘𝑊
𝑄 𝐿𝑎𝑡𝑒𝑛𝑡 = 𝑊𝑖𝑛𝑡𝑒𝑟 𝑙𝑎𝑡𝑒𝑛𝑡 𝑔𝑎𝑖𝑛 𝑡𝑜 𝑏𝑒 0.009 𝑘𝑊
Therefore:
𝑅𝑅𝐿 =
1.08
1.08 + 0.009
𝑹𝑹𝑳 = 𝟎. 𝟗𝟗𝟐
By plotting the RRL from the supply condition plotted, the room humidity condition at 19 °C can be
confirmed on the psychometric chart. To give an indicative idea of how the winter process will be a
mock psychometric chart has been created in Figure 10 to illustrate this process.
Heat Recovery Process RRL
Heating Coil Load Extract Process
From the finalised heating and cooling coil loads required for the MVHR Unit the final selection of the
units can be made following the use of the manufactures technical data sheet where the required
heating and cooling load requirements are shown for the designers choice. The same process as
1
2
3
4
Figure 10 - Winter Psychometric Process of the MVHR Unit
1 2
3
4

15
shown above for bedroom 1’s MVHR Unit sizing of components are done for Bedroom 2 so therefore
the following table shows the final heating and cooling coil sizes and their MVHR Unit respectively
chosen for that space.
Table 7 - Final Selection of MVHR Unit's requirements and sizing
Heating
Coil (kW)
Cooling
Coil (kW)
MVHR Sizing
Model
Sized Flow
Rate
(m3
/s)
Heating
Requirement
(kW)
Cooling
Requirement
(kW)
Bedroom
1
0.25 0.30
GUF –
50RD4
0.265 2.04 1.94
Bedroom
2
0.25 0.30
GUF –
50RD4
0.265 2.04 1.94
5.4 Control Strategy
The control of the MVHR units will be controlled via a wall-mounted controller, which will provide the
heating and cooling requirements through a thermostat controller. The thermostat will be located
upon the flat surface of the wall closest to the window façade due to that area being the predicted
coldest part of the room due to the distribution of air from the MVHR Unit. The controller will be able
to detect the air temperature within the space and adjust the heating and cooling requirements via fan
speed accordingly automatically depending on the thermostat situated in the space. Manual control
will also be available for the occupants within the space if they require further heating and cooling.
Table 8 - Maximum provided design conditions into Bedroom Space
Set Design Conditions Maximum Design Conditions
Winter 19 22
Summer 22 19
From Table 9 it shows that with the maximum design conditions for the Bedroom space, a new sizing
calculation will be needed to be conducted to provide the required maximum heating and cooling
design conditions. Therefore following the previous processes of sizing the heating and cooling a
further new set of heating and cooling coil sizes have been provided as follows:
 Revised Heating Coil Size – 0.13 kW
 Revised Cooling Coil Size – 0.19 kW
From the revised heating and cooling coil sizes, a new set of psychometrics charts will be shown to
illustrate the psychometric process during winter and summer conditions to provide the maximum
heating and cooling demand.
5.5 Condensate Removal
As it is assumed the MVHR Unit will provide the heating and cooling requirements to the space via
coils. The coils will require refrigerant to provide the required heating and cooling conditions. From the
process, the by-product of this is the build-up of condensate within the unit. Therefore, this build-up
of condensate will need to be removed via drain runs within the space, which will then fall into the
closest Soil Vent Pipes, which will run down the building at various locations of convenience.
The common process of removing the condensate build up is by using Gravity to let the condensate
free fall into the closest soil vent pipe location where available and then drop below ground where all
main drainage products will accumulate. This same process will be used within this project due to the
available depth of ceiling void there is as illustrated in Figure 11 the benefits of using gravity drainage
systems instead of the using a pump to boost the process of flushing the condensate through the
ceiling void is to save space and minimise the noise created from using pumps.
Condensate pipe to drain
Supply into Space
Extract from Space
Controller
Access Panel
Figure 11 - Configuration of MVHR Unit in Bedroom Space

16
5.6 Ductwork and Fittings design
The final sizing of the MVHR Unit has now been confirmed so therefore the ductwork
design can now follow to allow the supply and return process of air from outside to
inside. The material that will be used for the ductwork will be thin galvanised mild
steel sheets. These are the most commonly found materials in projects for creating
ductwork due to their wide range of availability in fittings, circular, rectangular as well
as their low cost attractiveness to contractors.
The method of ductwork sizing is to determine the correct duct area to deliver the air
volume required for the space at a controlled and manageable pressure requirement.
As air is seen as a fluid so therefore the fundamental principles of fluid will apply to
this scenario in that the D’Arcy fluid flow equation will be used to determine the
required pressure difference when sizing a section of ductwork which the fan will have
to accommodate with.
In Figure 12 is the supply ductwork layout with dimensions and each section, which
will need to be calculated to determine the overall pressure difference that the fan will
have to accommodate with when supplying the fresh air from the outside to the MVHR
Unit.
By calculating, the relevant ductwork sizes will determine the attenuators, louvres,
grilles and other fittings within the ventilation ductwork design. There are many
limiting factors to ensure a good ventilation design such as noise rating and pressure
as well as flow temperatures.
The ductwork material will be
galvanised steel which will be
circular in shape so as for ease
of fitting connection to other
fittings such as attenuators,
grilles and the MVHR Unit. The
ductwork will consist of
insulation to maintain the
temperature within the ductwork before
supplying into the space to prevent any losses.
A brief drawing showing the ductwork
installation will be found later on in the report.
5.7 Pressure Loss through Ductwork Calculation
The calculation process of determining the pressure required for the fresh air to pass from one end of
the ductwork to the other will be used with Section 1 of the supply ductwork as all other sections will
incorporate a similar process.
Within Figure 12, the highlighted section one has been shown where is the section where it will be
sized and all other sections of ductwork will go through a similar process of sizing.
Figure 12 - Proposed ventilation design for Bedroom Space
Section 1
Figure 13 - Example of Circular Galvanised
Ductwork used in the Bedroom Space Ventilation
Design

17
The duct diameter used within the section highlighted has been determined to be a diameter of
100mm based on using the ductulator apparatus which can determine the indicative duct size
dependent upon flow rate and velocity of the air fluid running through the ductwork.
Section one of the ductwork will require a supply flow rate of fresh air to be 0.02 m3
/s and will contain
the following fittings within section one of the ductwork as shown in Table 10.
Table 9 - Ductwork Fittings in Section 1
Section Fitting
Flow Rate
(l/s)
Diameter
(mm)
Pressure
Loss (Pa)
Length (m)
1 Louvre 20 - 30 -
2 Fire Damper 20 - 15 -
3
Straight
Ductwork
20 200
Calculation
Process 1
0.541
4 90° Bend 20 200
Calculation
Process 2
-
5
Straight
Ductwork
20 200
Calculation
Process 1
0.895
6 Attenuator 20 - 15 -
7 90° Bend 20 200
Calculation
Process 2
-
8
Straight
Ductwork
20 200
Calculation
Process 1
0.341
The louvre, Fire damper and Attenuator fitting pressure loss have been acquired from Part F
Ventilation document where it is a standard value for when applying those fittings into the ductwork
design. The straight ductwork and 90° Bend fittings will need to be calculated to determine the
pressure loss through them, which is shown as follows. The calculation procedure carried out as
follows is with reference to CIBSE Guide C, (Representitives, CIBSE Guide C Reference Data, 2007) for
Ductwork design as follows.
Figure 14 - Pressure Drop for air in galvanised circular ducts as found in CIBSE Guide C Figure 4.2,
(Representitives, CIBSE Guide C Reference Data, 2007)

18
5.7.1 Calculation 1 – Straight Ductwork
To determine the pressure loss through a straight piece of ductwork, Figure 14 will help determine
this. By already determining, the diameter of the ductwork to be 100mm and the velocity through the
ductwork to be 2.5 m/s. by plotting these values on the chart as shown in Figure 14 will determine the
pressure loss every meter of ductwork as indicated.
From plotting the initial figures that are known at the initial stages of the ductwork design, the
pressure loss every meter of ductwork has been determined as follows.
Acquired values from Figure 14 are as follows:
Volume Flow Rate – 0.02 m3
/s
Diameter of Circular Ductwork – 100 mm
Velocity – 2.5 m/s
Pressure drop per unit length – 1.2 Pam-1
Now that a pressure drop per unit length figure has been determined, the pressure loss at each
straight ductwork piece can be calculated as shown in Table 11.
Table 10 - Pressure loss through straight ductwork calculation
Section Length (m)
Pressure drop per
unit Length (Pam-1
)
Pressure loss
through Ductwork
(Pa)
3 0.541 1.2 0.649
5 0.895 1.2 1.074
8 0.341 1.2 0.409
From Table 11 the calculated pressure loss through the straight ductwork pieces within the calculated
section is shown.
5.7.2 Calculation 2 – 90° Bend
The pressure drops across fittings is determined with the use of D’Arcy’s equation which is as follows
∆𝑷 = 𝜻 × 𝟎. 𝟓 × 𝝆 × 𝒗 𝟐
Where:
∆𝑃 = 𝐹𝑖𝑡𝑡𝑖𝑛𝑔 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑑𝑟𝑜𝑝 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝜁 = 𝑃𝑟𝑒𝑠𝑠𝑢𝑟𝑒 𝑙𝑜𝑠𝑠 𝑓𝑎𝑐𝑡𝑜𝑟 𝑏𝑎𝑠𝑒𝑑 𝑜𝑛 𝐶𝐼𝐵𝑆𝐸 𝐺𝑢𝑖𝑑𝑒 𝐶 𝑇𝑎𝑏𝑙𝑒 4.20
𝜌 = 𝐷𝑒𝑛𝑠𝑖𝑡𝑦 𝑜𝑓 𝑎𝑖𝑟 𝑡𝑜 𝑏𝑒 1.2 𝑘𝑔/𝑚3
𝑣 = 𝑉𝑒𝑙𝑜𝑐𝑖𝑡𝑦 𝑜𝑓 𝑎𝑖𝑟 𝑡𝑜 𝑏𝑒 2.5 𝑚/𝑠
Figure 15 - Elbow values of varying with velocity as shown in CIBSE Guide C Table 4.20
As the duct fitting is a 90° Bend the table in Figure 15 acquired from CIBSE Guide C where the ζ
number can be determined. As highlighted in Figure 15 the determined value is 0.34. Placing this
acquired value from the equation as shown before the pressure loss can be confirmed.
Therefore:
∆𝑃 = 0.34 × 0.5 × 1.2 × 2.52
∆𝑷 = 𝟏. 𝟐𝟕𝟓 𝑷𝒂
From the calculation as set out above the pressure loss through the 90° Bend fittings can be added to
the other fittings included in the section of ductwork used to calculate the overall pressure loss which
is shown in Table 12.

19
Table 11 - Total Pressure loss through section of ductwork
Section Fittings Pressure Loss (Pa)
1 Louvre 30
2 Fire Damper 15
3 Straight Ductwork 0.649
4 90° Bend 1.275
6 Attenuator 15
7 90° Bend 1.275
Σ(Pressure Loss) = 64.682 Pa
5.7.3 Pressure Loss Calculation Comparison
The calculated pressure loss has been determined to be 64.682 Pa for the indicated section of
ductwork for the Bedroom Space. This value can also be compared to the pressure loss calculated by
using the Hevacomp software to determine the pressure loss. By inputting the same amount of fittings
and regulating the software to have the same initial values as used in the manual calculation. The
following results as shown in Table 13 have been produced.
Table 12 - Comparison of Results obtained using Manual and Hevacomp calculations
Flow Rate (m3
/s) Pressure Loss (Pa)
Manual Calculation 0.02 64.68
Hevacomp Calculation 0.02 62.28
From the produced Table 13 the comparison between the manual calculation and the result produced
by Hevacomp show minimal difference. This shows that the Hevacomp software is reliable software to
use for when using to calculate the pressure loss through a section of ductwork and when compared to
the manual calculation process on time elapsed the Hevacomp software is a much quicker way to
determine the pressure loss through ductwork compared with the manual calculations. Although to
check the results produced by Hevacomp, providing manual calculation results for a section of
ductwork is recommended within design work. This process has been done so for the five star
accommodation ductwork designs.
As shown below in Figure 16 the ductwork distribution layout has been drawn up on Hevacomp to
determine the circular ductwork sizes and pressure loss through the ductwork to calculate the Static
Fan Power value at which the MVHR has to handle. In Report 7 for Hevacomp Data the full results
package for the Ductwork distribution layout results produced by Hevacomp can be found.
5.8 Louvre Sizing
The louvre will need to be sized in order to determine the amount of free area that will be needed for
when the louvre grille will be placed on the external façade for the supply of the fresh air into the
Bedroom Space and the Extraction of air from the Bedroom Space. Therefore using the following initial
data, the free area that will be required can be determined.
Initial Design Data:
 Air Flow Rate – 0.02 m3
/s
 Air Speed – 2.5 m/s
Using the initial data, it can be inputted into the following equation to determine the amount of free
space required for the Louvre to be sized upon.
Figure 16 - Heavacomp ventilation design for Bedroom Space

20
𝑨 =
𝒒
𝒗
Where:
𝐴 = 𝐿𝑜𝑢𝑣𝑟𝑒 𝑠𝑒𝑐𝑡𝑖𝑜𝑛𝑎𝑙 𝑎𝑟𝑒𝑎 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑞 = 𝐴𝑖𝑟 𝐹𝑙𝑜𝑤 𝑅𝑎𝑡𝑒 𝑡𝑜 𝑏𝑒 0.02 𝑚3
/𝑠
𝑣 = 𝐴𝑖𝑟 𝑠𝑝𝑒𝑒𝑑 𝑡𝑜 𝑏𝑒 2.5 𝑚/𝑠
Therefore:
𝐴 =
0.02
2.5
𝐴 = 0.008 𝑚2
From the calculated Louvre sectional area to be 0.008 m2
the final louvre selection can be made.
Using Gilbert’s manufacture of grilles and diffusers, the Louvre can be sized for the Bedroom space for
supply and extract.
The Gilberts series L Grilles (Gilbertsblackpool.co.uk) will be specified for the Bedroom Space and will
be required to be manufactuered using Marine Grade Steel to prevent corrosion over time from the
high levels of salt air as the project is located near the sea. Below is an indacative idea of how the
Louvre will be fitted into the façade of the Bedroom Space for the supply and extract requirements.
Figure 17 - Indicative Louvre Spacing requirement for Five Star Accommodation Space
5.9 Attenuator Sizing
Due to application of the provision of ventilation and air conditioning requirements being all-local to
the Bedroom Space. All the fittings will provide noise when air is travelling through those fittings,
which is dependent on the velocity of the air and the pressure corresponding to those fittings.
Therefore, attenuators will need to be sized to accommodate for the noise being created, as it is
unwanted, sound that the five star accommodation occupants will not be satisfied with.
The sizing of the required attenuator(s) is dependent upon the MVHR Units specification, which is
shown as follows.
Required Louvre
Space as calculated

21
Initial Data:
 Fan Duty – 0.02 m3
/s
 Fan Static Pressure – 140 Pa
 Sound Pressure Level – 29.5 dBA
Following the produced data, a suitable attenuator can be sized using manufactures data where the
selected attenuator will be located in the supply and extract part of the MVHR Unit, which will be
shown in the drawings, produced at the end of this report. However, it should be noted, the use of
attenuators is not necessary as the MVHR Unit is specified at a low sound pressure level which is well
below the design noise requirements for the Bedroom space so therefore attenuators will not be
required.
5.10 Supply Diffuser Sizing
Gilberts will manufacture the sizing of the supply diffuser into the space as they provide bespoke
diffusers on demand from the designer’s request. Therefore from Figure 18, where the position of the
supply diffusers are located are to provide fresh air that is heated or cooled depending on summer or
winter conditions externally to offset the heat losses experienced from the façade. The linear slot
diffusers allow for a very aesthetically pleasing ceiling mounted installation fit for the five star
accommodations Bedroom Space.
The linear slot diffusers will have fixed blade orientation as shown in Figure 18 as the main priority of
the supply system is to offset any heat gains or heat losses experienced in the space and provide
fresh air requirements into the space for the occupants whilst not giving any discomfort for the
occupants within the space.
Figure 18 - Indicative representation of Fixed Diffuser Blades to be used in Grille Fittings
To size the required supply diffuser the following initial data need to be used as follows.
 Air Flow Rate through each Supply Grille – 0.01 m3/
s
 Noise Rating of Space to be between 20 – 30 NR acquired from CIBSE Guide A for the
recommended noise rating to be in a Bedroom Space
 Required throw of supply diffuser to be a maximum of 3.15 meters
Using the initial data and using the sizing monogram produced by Gilberts manufacture for the Liner
slot diffusers, the static pressure and the actual throw of the grille can be confirmed as Figure 19
illustrates this process.

22
Figure 19 - Sizing Nomogram for Linear Slot Diffuser produced by Gilberts Manufacture
(Gilbertsblackpool.co.uk)
From the sized requirements from Figure 17, the sizing data is shown in Table 14 where each section
corresponds to the numbering scheme on Figure 12.
Table 13 - Finalised selection data from Figure 19 for Linear Slot Diffuser
Section Output Data
1 Flow Rate of 0.02 m3
/s
2 Throw of 2.5 meters
3 Sound Level is under Initial Design Criteria
4 Static pressure is to be 2 Pa
5 Number of Slot to be 2
The linear slot diffuser configuration from Table 14 shows that from the initial design requirements
some changes have been made. As the sizing, nomogram is limited to 0.02 m3
/s that does not
however mean the required flow rate of 0.01 m3
/s cannot flow through the diffuser. The throw has
been determined to be 2.5 meters which is under the maximum throw requirement set out by the
initial design data, however when estimating how much throw 2.5 meters provides with within the
Bedroom Space, it is shown as acceptable as Figure 17 illustrates this. The noise rating is well below
the initial design data, it is predicted in fact that there will be minimal noise provided when the linear
slot diffuser diffuses the required flow rate into the space. The predicted static pressure is to be two
Pa, which is a low-pressure loss to be handled by the MVHR Unit so therefore is acceptable. Finally,
the required slots within the slot diffuser will be two, which is to angulate the flow of air into the space
with sufficient control of the blades at a fixed angle without putting too much pressure on them. All
output data has been clarified with Gilberts manufacture by communicating with technical staff.
5.11 Extract Grille Sizing
The requirement for extract grilles within the Bedroom space of the 5 star accommodation space is so
extract the air that has been provided already by the supply system of the MVHR so the extracting air
can be recovered and provide additional heating or cooling requirements for the supply of the air into
the space. Therefore, an extract grille is required for this process to extract the required air from the
space to the MVHR Unit then exhausted from the building through the already sized louvre.
Using the initial design data as follows, the appropriate extract grille can be sized.

23
 Air Flow Rate – 0.02 m3
/s
 Limiting Air Velocity – 2.5 m/s
From the initial design data stated above and using Gilberts manufacture data for square extract
grilles technical data, the require size for the extract grille can be determined which is as shown in
Figure 18.
From the sized requirements from Figure 18, the sizing data is shown in Table 15.
Table 14 - Finalised selection data from Figure 20 for two Way blow Diffuser
Neck Velocity (m/s) 1.75
Total Pressure (Pa) 8
Neck Size (mm) 200
Dimension of Grille (mm × mm) 150 × 150
NC Level (1.1 × 8) = 8.8
Volume flow Rate (m3
/s) 0.02 m3
/s per side
Throw (m) 2.1 + 1 = 3.1
From the final selection made from using Figure 18 the final selected diffuser is shown in Table 15 the
neck velocity to be 1.75 m/s will be sufficient to extract the air from the space in a controlled manor
without creating unwanted noise within the ductwork initially sized at a maximum velocity of 2.5 m/s.
the dimension of the sized diffuser will mean it will be a small square provision required within the
mounted ceiling for the grille to sit within and be connected from a 200 mm neck diameter as stated
within the table to then connect to the circular ductwork within the ceiling void. The calculated noise
rating from the diffuser is below the recommended noise rating criteria, which is applicable for this
situation for the Bedroom Space. The specified volume flow rate that the diffuser is capable of is at
0.02 m3
/s, which doubles the required flow rate to be extracted from each side of the diffuser of the
space so therefore this is also acceptable.
5.12 Psychometric Charts
The summer and winter condition psychometric charts have been produced in the following pages to
illustrate the summer and winter process of the MVHR Unit conditioning the air coming into the
Bedroom Space.
The plotted values on the chart correspond to the values that have been calculated through this
section of the report to determine each point through the summer and winter process to plot it on the
chart to complete the process. The psychometric charts can be found in the following pages.
Figure 20 - Sizing table produced by Gilberts Manufactures for 2-way blow diffuser (Gilbertsblackpool.co.uk)

24

25

26
6. HEATING DESIGN
The heating requirements within the 5 star accommodation mainly coincides within the bathroom
space where the space is negatively pressured to keep odours and contaminants within the space so
sufficient extraction is possible as explained within this report. Therefore, the requirement of heating
through using air conditioning systems within this space is not feasible. Instead, radiators will be
utilised to provide the heating requirements needed for this space.
The entrance space will also go through a similar radiator sizing process, as it is required set out by
the client’s brief that is to be heated to 19°C. As proven through analysis from using IES Virtual
Environment in stage 2 of the report, using natural ventilation these spaces will not reach their design
conditions so therefore additional heating is required.
This section of the report will go through the process of sizing the required radiators in the five star
accommodation space chosen to design for in this report. The radiator sizing will be based on the final
heat loss value that was calculated using manual calculations as set out above which provided the
final heat loss figure as shown in Table 15.
Table 15 - Finalised Heat Loss results based on IES Virtual Environment
Heat Loss (kW)
Bathroom Space 1.1 kW
Entrance Space 0.6 kW
The means of heating these two spaces will be done so by Low Surface Temperature (LST) Radiators.
The benefits of suing this heating system is to provide a safe heating system to the space which will
limit the temperature on the surface of the system so as to prevent accidental contact to hot surfaces
within the spaces, whilst providing sufficient heating requirement to offset the calculated heat loss
within the spaces.
6.1 Radiator Sizing
Stelrad (Stelrad.co.uk) manufactures the radiators chosen. A preliminary choice has been made in
terms of types of radiators that will be used within the Bathroom and Entrance space based on the
manufactures recommendations to the applicability of the radiator selection.
Table 16 - Preliminary Selection of Radiators produced by Stelrad (Stelrad.co.uk)
Model of Stelrad Radiator
Bathroom Space Vertical Ultra
Entrance Space Concord Lo-Line
Figure 21 - Preliminary selection of Stelrad Radiators in Bathroom Space (Stelrad.co.uk)
Figure 22 - Preliminary selection of Stelrad Radiators in Entrance Space (Stelrad.co.uk)

27
The convective heat transfer from the radiator for the Bathroom and Entrance space is shown in
Figure 23 illustrate the methods of convection from the radiator in their selected spaces.
When selecting the appropriate radiators for the space it is important to calculate the tabulated heat
output with respect to the correction factor produced by the manufacture. The reason for the
correction factor is that the technical data sheet from which the sizes of the radiators are found, are
designed under ideal test conditions at dry bulb temperatures of 50°C and 30°C respectively.
Therefore, the correction factor is applied to determine the radiator size required under actual design
conditions.
To determine the correct correction factor by use of interpolation from Table 16 the radiator mean
temperature and mean fluid temperature needs to be determined for both spaces.
From Figure 24 the inlet and outlet temperatures are given for the radiator sizing. Using these values,
we can now determine the radiator mean temperature and mean fluid temperature using the following
equations:
Convective
Heating flows
into space at
high level
Room air passes
through radiator
fins and panel
where gradually
room is being
heated
Cooler air
from space
enters
radiator at
low level
Figure 23 - Illustrated method of convection using LST Radiators
Inlet
Temperature
80 °C
Outlet
Temperature
60 °C
Figure 24 - Process of calculating Radiant Mean and Mean Fluid Temperatures

28
𝑹𝒂𝒅𝒊𝒂𝒕𝒐𝒓 𝑴𝒆𝒂𝒏 𝑻𝒆𝒎𝒑𝒆𝒓𝒂𝒕𝒖𝒓𝒆 =
(𝑰𝒏𝒍𝒆𝒕 𝑻𝒆𝒎𝒑𝒆𝒓𝒂𝒕𝒖𝒓𝒆 + 𝑶𝒖𝒕𝒍𝒆𝒕 𝑻𝒆𝒎𝒑𝒆𝒓𝒂𝒕𝒖𝒓𝒆)
𝟐
Where:
𝑅𝑎𝑑𝑖𝑎𝑡𝑜𝑟 𝑚𝑒𝑎𝑛 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝐼𝑛𝑙𝑒𝑡 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 = 80 °𝐶
𝑂𝑢𝑡𝑙𝑒𝑡 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 = 60 °𝐶
Therefore:
𝑅𝑎𝑑𝑖𝑎𝑡𝑜𝑟 𝑀𝑒𝑎𝑛 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 =
(80 + 60)
2
𝑹𝒂𝒅𝒊𝒂𝒕𝒐𝒓 𝑴𝒆𝒂𝒏 𝑻𝒆𝒎𝒑𝒆𝒓𝒂𝒕𝒖𝒓𝒆 = 𝟕𝟎 °𝑪
From gaining the radiant mean temperature value of the radiator system, the mean fluid temperature
can also, be determined. However, the mean fluid temperature involves the room condition of the
space in the calculation, therefore two results will be produced for Bathroom and Entrance space.
𝑴𝒆𝒂𝒏 𝑭𝒍𝒖𝒊𝒅 𝑻𝒆𝒎𝒑𝒆𝒓𝒂𝒕𝒖𝒓𝒆 = 𝑹𝒂𝒅𝒊𝒂𝒏𝒕 𝑴𝒆𝒂𝒏 𝑻𝒆𝒎𝒑𝒆𝒓𝒂𝒕𝒖𝒓𝒆 − 𝑰𝒏𝒕𝒆𝒓𝒏𝒂𝒍 𝑹𝒐𝒐𝒎 𝑪𝒐𝒏𝒅𝒊𝒕𝒊𝒐𝒏
Where:
𝑀𝑒𝑎𝑛 𝐹𝑙𝑢𝑖𝑑 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑖𝑠 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑅𝑎𝑑𝑖𝑎𝑛𝑡 𝑀𝑒𝑎𝑛 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 ℎ𝑎𝑠 𝑏𝑒𝑒𝑛 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑 𝑡𝑜 𝑏𝑒 70 °𝐶
𝐼𝑛𝑡𝑒𝑟𝑛𝑎𝑙 𝑅𝑜𝑜𝑚 𝐶𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛 𝑜𝑓 𝐵𝑎𝑡ℎ𝑟𝑜𝑜𝑚 𝑆𝑝𝑎𝑐𝑒 𝑡𝑜 𝑏𝑒 20°𝐶
𝐼𝑛𝑡𝑒𝑟𝑛𝑎𝑙 𝑅𝑜𝑜𝑚 𝐶𝑜𝑛𝑑𝑖𝑡𝑖𝑜𝑛 𝑜𝑓 𝐸𝑛𝑡𝑟𝑎𝑛𝑐𝑒 𝑆𝑝𝑎𝑐𝑒 𝑡𝑜 𝑏𝑒 19°𝐶
Therefore the mean fluid temperature in the Bathroom space is:
𝑀𝑒𝑎𝑛 𝐹𝑙𝑢𝑖𝑑 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝐵𝑎𝑡ℎ𝑟𝑜𝑜𝑚 𝑆𝑝𝑎𝑐𝑒 = 70 °𝐶 − 20 °𝐶
𝑴𝒆𝒂𝒏 𝑭𝒍𝒖𝒊𝒅 𝑻𝒆𝒎𝒑𝒆𝒓𝒂𝒕𝒖𝒓𝒆 𝑩𝒂𝒕𝒉𝒓𝒐𝒐𝒎 𝑺𝒑𝒂𝒄𝒆 = 𝟓𝟎°𝑪
Therefore the mean fluid temperature in the Entrance space is:
𝑀𝑒𝑎𝑛 𝐹𝑙𝑢𝑖𝑑 𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝐸𝑛𝑡𝑟𝑎𝑛𝑐𝑒 𝑆𝑝𝑎𝑐𝑒 = 70 °𝐶 − 19 °𝐶
𝑴𝒆𝒂𝒏 𝑭𝒍𝒖𝒊𝒅 𝑻𝒆𝒎𝒑𝒆𝒓𝒂𝒕𝒖𝒓𝒆 𝑬𝒏𝒕𝒓𝒂𝒏𝒄𝒆 𝑺𝒑𝒂𝒄𝒆 = 𝟓𝟏°𝑪
From the produced values for the Radiant Mean Temperature and the two mean fluid temperatures for
their respected spaces, the radiators can be selected. The need for applying a correction factor to
determine the correct heat output for the radiators is not required at this stage of the calculation. The
reason behind this is that Stelrad the manufactures used to design the radiators for this project
provide technical data for the difference in flow and return temperature that has been specified for the
radiator design. As there is a pre-heat margin already being applied, the need to compensate the heat
output with applying for a correction factor is not needed.
The final selection of the radiator sized for the two spaces are as shown in Table 17.
Table 17 - Final Selection of Radiators
Model
Dimension Heat Output
(kW)Height (mm) Width (mm) Depth (mm)
Bathroom
Space
Vertical Ultra 2040 470 72 1.584
Entrance
Space
Concord Lo-
Line
144 1200 60 0.796
The radiators sized in this section of the report will be found located in the proposed locations in the
drawings produced within the drawings section of this report.
6.2 Radiator Design and Distribution
The radiators sized on the 19th
and 20th
floors for the five star accommodation spaces will be fed the
low temperature hot water requirements from the 18th
floor plant room. The boilers will be located in
the 18th
floor plant room where the relevant pipe requirements based on sizes produced by the
Hevacomp software will run of their designated service risers. As shown in the drawings produced
within the drawings section of this report, the boilers pipe runs will rise into the 19th
and 20th
floors of
the building to serve the radiators required flow temperatures and the corresponding return pipework
from the radiators.
The LTHW system requirements will be supplied via a ‘tap off’ from the low loss header situated in the
18th
floor plant room which will then have two main runs from the left and right section of the 19th
and
20th
floors of the 5 star accommodation floors. The LTHW system at each space required will
incorporate with a three port to allow for mixing configuration to allow variable temperature to apply
to the radiators within the space to save on energy used to heat up the spaces to their design
conditions.

29
Figure 25 - Three Port Valve control to be used in Radiators
For maintenance reasons, isolation valves will be fitted at each level within the riser to allow for
isolation. Thermostatic radiator valves (TRV) and lock shield valve components with drain off are also
installed as part of the installation of the radiators for complete control of the system which Figure 25
illustrates this.
6.3 Radiator Pipe sizing
The radiator pipe sizing process will be done to the Bathroom space, as the same process will apply to
all other spaces that require pipe sizing for the radiators used. The sized Vertical Ultra radiator will be
radiator that will be installed within the Bathroom space where the room air temperature will be 20°C
and the heat loss has been calculated to be 1.1 kW. The hot water flow is to be 80 °C and a return of
60 °C. Using the acquired initial values the water flow rate can be calculated as follows.
𝑾𝒂𝒕𝒆𝒓 𝑭𝒍𝒐𝒘 𝑹𝒂𝒕𝒆 =
𝟏. 𝟏 × 𝑸
𝑪𝒑 × (𝒕 𝑭 − 𝒕 𝑹)
Where:
𝑊𝑎𝑡𝑒𝑟 𝑓𝑙𝑜𝑤 𝑟𝑎𝑡𝑒 𝑡𝑜 𝑏𝑒 𝑐𝑎𝑙𝑐𝑢𝑙𝑎𝑡𝑒𝑑
𝑄 = 𝐻𝑒𝑎𝑡𝑖𝑛𝑔 𝑅𝑒𝑞𝑢𝑖𝑟𝑚𝑒𝑛𝑡 𝑓𝑜𝑟 𝑠𝑝𝑎𝑐𝑒 𝑡𝑜 𝑏𝑒 𝑚𝑢𝑙𝑡𝑖𝑝𝑖𝑒𝑑 𝑏𝑦 10% 𝑚𝑎𝑟𝑔𝑖𝑛
𝐶𝑝 = 𝑆𝑝𝑒𝑐𝑖𝑓𝑖𝑐 𝐻𝑒𝑎𝑡 𝐶𝑎𝑝𝑎𝑐𝑖𝑡𝑦 𝑜𝑓 𝑤𝑎𝑡𝑒𝑟 𝑡𝑜 𝑏𝑒 4.18
𝑡 𝐹 = 𝐹𝑙𝑜𝑤 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑜𝑓 𝐻𝑜𝑡 𝑊𝑎𝑡𝑒𝑟 𝑠𝑢𝑝𝑝𝑙𝑦 𝑡𝑜 𝑏𝑒 80°𝐶
𝑡 𝑅 = 𝑅𝑒𝑡𝑢𝑟𝑛 𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 𝑜𝑓 𝐻𝑜𝑡 𝑊𝑎𝑡𝑒𝑟 𝑟𝑒𝑡𝑢𝑟𝑛 𝑡𝑜 𝑏𝑒 60 °𝐶
Therefore:
𝑊𝑎𝑡𝑒𝑟 𝐹𝑙𝑜𝑤 𝑅𝑎𝑡𝑒 =
1.1 × 1.1
4.18 × (80 − 60)
𝑾𝒂𝒕𝒆𝒓 𝑭𝒍𝒐𝒘 𝑹𝒂𝒕𝒆 = 𝟎. 𝟎𝟏𝟒𝟓 𝒌𝒈/𝒔
The water flow has been calculated to be 0.0145kg/s. From this, the radiator mean water temperature
has been calculated to be 70°C and the radiators output and the mean calculated temperature is to be
50°C.
From the acquired water flow of the system, the pressure loss rate through pipework sections can be
determined to determine the required pipe sizes. This can be determined by the excel spreadsheet
produced by CIBSE to size pipework. As Figure 23, the pipe material is to be chosen as medium grade
steel for heating purposes with a water temperature of 70°C with no glycol mixture, as the pipework
will not be used externally outside the building where the water content within the pipework is at risk
at freezing. By inputting the mass flow rate and preliminary pipe diameter used in the Bathroom space
the velocity, pressure and velocity pressure values can be determined.
Figure 26 - CIBSE Pipe sizing Spreadsheet for Heating Pipework
Port
A
Port
AB
Port
Ab
Port
A
Port
B
Port
B
Mixing Arrangement Diverting Arrangement

30
From Figure 26 the finalised output data is as follows.
 Velocity – 0.07 m/s
 Pressure Loss – 7 (Pa/m)
 Velocity Pressure – 3 (Pa)
To check the acquired values produced by the CIBSE Spreadsheet for the pipe sizing, a manual
calculation process has also been carried out as shown below. Using Figure 24 to determine the
relevant pipe size required as shown below.
Figure 27 - Pipe sizing for Galvanised steel from CIBSE Guide C4 Table 4.34, (Representitives, CIBSE Guide C
Reference Data, 2007)
From Figure 27 the selected pressure loess through a section of pipework is to be seven Pa/m and the
velocity to be 0.07 m/s.
Using the calculation process as shown above to acquire the correct pipe sizes for the required flow
rate through a pipe compared to the value acquired from the CIBSE pipe sizing spreadsheet, both
results are very similar so therefore proves the CIBSE produced method of pipe sizing using the excel
spreadsheet is accurate and a reliable methods as it is seen as an industry standard for pipe sizing
within projects.
Using the same process as shown to calculate this particular section of pipework, the same process
will be done to the other pipework on the five star accommodations for the heating required spaces.
As Figure 28 shows the heating pipework for the Bathroom space and the Entrance space is shown
with all relevant pipe sizes notes as well as the distribution layout out as shown.
Figure 28 - Indicative representation of Heating System distribution in Five Star Accommodation Space
6.4 Radiator Pipe Sizing Comparison
As the final selection radiator pipe size has been determined for the Bathroom space pipework to
serve the radiator, a Hevacomp distribution layout has also been created so that the final pipe sizes
for the heating can be compared with. As shown in Figure 29 is the distribution layout of the heating
pipework to the radiators in their rightful positions with the pipe size note linked to each section of
pipe work as shown.

31
Figure 29 - Heating Distribution Layout using Hevacomp
From the produced Hevacomp indicative layout of the radiator distribution for the five star
accommodation spaces as shown in Figure 29 the system resistance and total flow rate values were
produced for the two distribution layouts as produced using the Hevacomp software. The results from
the produced Hevacomp and manual calculation processes as shown above have been provided as
shown in Table 18 below.
Table 18 - Heating Pipe Sizing Comparison
System 1 System 2
Manual
Calculation
Flow Rate 0.155 0.155
System Resistance 10.35 10.35
Hevacomp Calculation
Flow Rate 0.175 0.176
System Resistance 10.96 11.45
From the produced table as shown above the comparison between the manual calculation process and
the results obtained from the Hevacomp calculation process. The results analysed have shown that the
results obtained from both calculation processes have very similar results however the Hevacomp
results have shown to be slightly oversized which is due to the oversizing factors associated with the
software’s calculation process.
The radiator distribution design will be based on the results obtained by the Hevacomp software, as it
is a much easier calculation process to determine the various pipe sizes associated with the radiator
distribution pipe sizing. The Hevacomp software has proven its reliability with the comparison of the
obtained results with the manual calculation process performed earlier within this section of the
report.

32
7. DOMESTIC WATER SERVICES DESIGN
The Bathroom space will be the only space that will require domestic water services to
be designed for as shown in Figure 30 within this section, the design of the domestic
water services to the building will be shown.
7.1 Domestic Water Services Peak Flow Rate Calculation
The Bathroom space will contain the following outlets as shown in Table 19 with the
required loading unit and corresponding flow rate to that outlet using BS806,
(Standards, 2006).
Table 19 - Outlets used in Bathroom Space and the Loading Units and respected Flow Rates,
Outlet Loading Units (LU) Peak Flow Rate (l/s)
Washbasin 1 0.1
WC 1 0.1
Shower 2 0.2
Bath 4 0.4
From the required outlets within the Bathroom, space from Table 19 the peak demand
of the cold-water services can be determined as well as the peak demand of the hot
water services as shown in Table 20.
Table 20 - Hot and Cold Peak Demand Flow rates for Bathroom Space
Peak Hot Water Flow Rate (l/s) Peak Cold Water Flow Rate (l/s)
0.7 0.8
The peak demand flow rates for the water services within this space is intermittent and mainly random
but however has distinct peaks at fairly regular periods during the day. The pipe sizing process is for
those peak periods where the highest demand of water is required through the pipework and can be
delivered at a reasonable amount of pressure and velocity to the outlets.
The cold water services will be the first to be designed which will be based on an indicative pipe run as
shown in Figure 30 where the cold water main run flows at ceiling void level in the corridor and enters
the Bathroom space and drops at the corner of the space to supply the outlets within the Bathroom
space at low level.
Figure 30 - Proposed Zone for Domestic Water Services Design

33
7.2 Domestic Water Services Valve Arrangement
Within Figure 30, the pipework has incorporated the required valve fittings that will be required to
ensure the domestic cold-water services functions properly in terms of regulating the pressure
required for the Bathroom space at the outlets as well as filtering any composites that may have been
picked up during the pipe run from the Cold-water tank to the outlets.
A brief description of what each valve is required to do is as follows as well as an illustration of the
symbol used in the drawing to explain how it helps the domestic cold water services.
Isolation Valve – The isolation valve will be used within the Bathroom Space and
Entrance space for isolation purposes as of when maintenance
is required for the radiators within those spaces.
Meter – The meter fitting will be used within the entry of the 5-tar accommodation
space to monitor the usage of the water being used by the occupants plainly for
business use to modulate the tariff of water being allowed for occupants at a
later date.
7.3 Domestic Water Services Pipe Sizing
To firstly determine the required flow through the pipework for hot and cold-water services, the
loading units that will be required at each outlet need to be determined with the use of the British
Standards Guide 806. It states within the document that one loading unit equates to the draw off flow
rate to be 0.1 l/s. therefore following this conversion from loading units to flow rate in litters per
second the following table outlines the flow rate of each outlet used within the Bathroom Space as
follows.
Table 21 - Summary of Loading Units and relevant flow rate to each draw off point
Draw Off Point Loading units (LU) Flow Rate (l/s)
Wash Basin 1 0.1
WC 1 0.1
Shower 2 0.2
Bath 4 0.4
From the produced table of loading units for each outlet converted into the corresponding flow rate,
the maximum flow rate of hot and cold water can be determined as follows
 Hot Water Peak Flow Rate – 0.7 l/s
 Cold Water Peak Flow Rate – 0.8 l/s
Firstly an indicative layout of the pipe runs from the outlets within the Bathroom Space to the service
riser needs to be shown to determine the pressure through that section of pipework. An indicative pipe
run for hot and cold-water services is as shown in Figure 31.
Figure 31 - Distribution Layout of Domestic Water services with indicative lengths of pipework
From Figure 31 the lengths of each pipework can be determined as well as the velocity of the
pipework depending on the flow rate running through that pipework which is acquired from the
produced spreadsheet by CIBSE for pipe sizing which is seen as an industry standard as shown in
Figure 31 where the cold water pipe sizes will be determined first as shown.
When initially plotting in the details to determine the pressure, velocity y and velocity pressure values.
A pipe diameter of 28mm was inserted which produced a pressure value of 928 Pa/m which is
considered to be too high as quoted by CIBSE Guide C. the deal pressure range for pipework is to be

34
between 200-300 Pa/m although pressure values above and below this range is not seen as
unacceptable. Therefore the pipe size was reduced to 35mm where pressure value of 346 Pa/m was
determined which is just above the recommended range provided by CIBSE so therefore carried on
through the design as shown in Figure 32.
Figure 32 - CIBSE Pipe sizing Spreadsheet for Cold Water Pipework
From Figure 32 the finalised output data is as follows.
 Velocity – 0.96 m/s
 Pressure Loss – 346 (Pa/m)
 Velocity Pressure – 458 (Pa)
From the acquired values as shown above the pipe section with a flow rate of 0.8 l/s can be sized to
35mm.
Using the same process as shown to calculate this particular section of pipework, the same process
will be done to the other pipework on the five star accommodations for the cold waters services within
the Bathroom Space. A similar process will be done for the hot water services pipework with different
variables as shown in Figure 33 for the hot water flow.
The return pipework size is to be estimated to be two sizes recommended within the CIBSE pipe sizing
spreadsheet as it is seen as an industry standard to do so. Therefore, the return pipe size for this
section of the pipework will be 20mm.
Figure 33 - CIBSE Pipe sizing Spreadsheet for Hot Water Flow Pipework
From the pipe sizing calculations produced below is a summary of the final pipe sizes produced for the
Cold Water Flow and Hot water flow and return.
 Cold Water Flow Pipe Size – 35mm
 Hot Water Flow Pipe Size – 32mm
 Hot Water Return Pipe Size – 20mm
From the produced pipe sizes from the manual calculation process, a Hevacomp calculation process
will be also undertaken to compare the accuracy and reliability of the results obtained. An indicative
domestic water services distribution layout has been produced using the Hevacomp software to
determine the relevant flow rate, system resistance and final pipe sizes used for the domestic water
services.

35
7.4 Domestic Water Services Hevacomp Calculation
Within the Hevacomp software, the cold-water services and the hot water supply services are laid out
in two different distributions. Therefore two separate Hevacomp distribution layouts need to be
produced however both will be compared with the final produced manual calculation process pipe sizes
produced.
Figure 34 - Cold Water Domestic Services Hevacomp Distribution Layout
As Figure 34 shows the produced cold-water services for the five star accommodation been distributed
through the floor using Hevacomp software. The software will run a calculation process with the data
that has been installed on the software to produce the system resistance, flow rate and pipework size
dependant on which section of pipe is being analysed for the cold-water services.
The hot water pipework distribution now needs to be determined with the aid of the Hevacomp
software, which is shown as follows in Figure 35.
Figure 35 - Hot Water Domestic Services Hevacomp Distribution Layout
From the both distribution layouts as shown from using the Hevacomp software, below is the provided pipe size for
the section of pipework analysed using manual calculation process. The results produced will be compared to
discuss the similarities or difference in results and discuss why that may be.

36
7.5 Domestic Water Services Pipe Sizing Comparison
The section of pipework used to analyse the correct pipe sizes to be used in the final distribution
layout of the five star accommodation’s domestic water services have been confirmed using manual
calculation and Hevacomp calculation process as shown below in Table 22.
Table 22 - Domestic Water Services Pipe sizing comparison
Manual Calculation Hevacomp Calculation
Cold Water Supply 35 32
Hot Water Supply 32 28
Hot Water Return 22 15
The pipe sizes listed out above are acquired from the relevant section of pipework analysed earlier
within this section of this report. The pie sizes relate to the incoming pipe run upon entering the hotel
space. From the produced table comparing the acquired pipe sizes for the relevant pipe system type,
it shows that both calculation processes produce similar results. The manual calculation process has
been slightly oversized due to limiting velocity values however the Hevacomp calculation process has
a much higher limiting velocity value therefore is capable of utilising smaller pipe sizes.
The Hevacomp calculation process of determining the relevant pipe sizes for the distribution of
domestic water services will be carried out throughout this project, as the process is easier than the
manual calculation process as well as time consuming. The results produced by the Hevacomp results
have proven to be reliable based on the comparison carried out with the manual calculation process
carried out earlier in this report.

Report 2 - Mechanical - Functional Zone

Report 2 - Mechanical - Functional Zone

Recommended

Recommended

More Related Content

What's hot

What's hot (7)

Viewers also liked

Viewers also liked (20)

Similar to Report 2 - Mechanical - Functional Zone

Similar to Report 2 - Mechanical - Functional Zone (20)

Report 2 - Mechanical - Functional Zone