IS 14754: Ships and marine technology - Air-conditioning and ventilation of accommodation spaces - Design conditions and basis of calculations

2008·1.4 MB·English

by  Bureau of Indian Standards

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in order to promote transparency and accountability in the working of every public authority,
and whereas the attached publication of the Bureau of Indian Standards is of particular interest
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timely dissemination of this information in an accurate manner to the public.
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IS 14754 (2008): Ships and marine technology -
Air-conditioning and ventilation of accommodation spaces -
Design conditions and basis of calculations [TED 17:
Shipbuilding]
“!ान $ एक न’ भारत का +नम-ण”
Satyanarayan Gangaram Pitroda
““IInnvveenntt aa NNeeww IInnddiiaa UUssiinngg KKnnoowwlleeddggee””
“!ान एक ऐसा खजाना > जो कभी च0राया नहB जा सकता हहहहै””ै”
Bhartṛhari—Nītiśatakam
“Knowledge is such a treasure which cannot be stolen”

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IS 14754:2008
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Indian Standard
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SHIPS AND MARINE TECHNOLOGY — }“
AIR-CONDITIONING AND VENTILATION OF
ACCOMMODATION SPACES — DESIGN CONDITIONS
AND BASIS OF CALCULATIONS
( First Revision)
ICS 47.020.80:47.020.90
0 BIS 2008
BUREAU OF INDIAN STANDARDS
MANAK BHAVAN, 9 13AHADUR SHAH ZAFAR MARC
NEW DELHI 1I0002

Price Group 5
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~h~pl?u~iding Sectional (hmm~ttec TED i7
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‘}”h~~lnd}an Standard (l-:irstRewsion) was adopted by the Bureau of Indian Standards, after the draft finalized by
{heShipbuilding Sectional Committee had been approved by the Transpot-t Engineering Division Council.
‘I”h)sstandard was first published in 1999. The present revision has been undertaken to harmonize with current ,, !
in{ernatit)nal practices. in tk,e revised standard beside other changes, heat gain from persons and thermal [’
c[)nductjvl(ies ()(’commonly used construction materials have been modified.
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In the i’{)rnlula[ion of this stmdard considerable assistance have been drawn from 1S0 7547 :2002 ‘Ships and $1
nlarlrlu [ethnology” — Air-c[)rlditiolllrlg and vcntilauon t)t accommodation spaces — Design conditions and
(
basis f)[’c:ilc[ll;itl{)ns’.
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Users t)t’this standard should note that, while obserwlng the requirements ofthis standard, they should atthe same #
Linleensure compliance with statutory requirements, rules and regulations as may be applicable to the individua]
ship concerned.
i
Attention is draiin to the possibility that some of’the elements of this Indian Standard may be the subject of
patent rights. BLII13:LLIof’Indian Standards shall not be held responsible for identifying any or all such patent
rights.
Annex A and Annex B are for information only.
,.
F{)rthe put-pose of deciding whether a particular requirement of this standard is complied with, the final value,
{)bserved orcalculated expressing the result ofatest or analysis, shall berounded off inaccordance with IS 2: 1960
‘Rules fbr rounding off numerical values (revised)’. The number of significant places retained inthe rounded off
value should be the same as that of the specified value in this standard. t
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IS 14754:2008
Indian Standard
SHIPS AND MARINE TECHNOLOGY —
AIR-CONDITIONING AND VENTILATION OF
ACCOMMODATION SPACES — DESIGN CONDITIONS
AND BASIS OF CALCULATIONS
( First Revision)
1 SCOPE sufficient for the needs of the occupants or the process.
This standard specifies design conditions and methods 3.4 Relative Humidity — Ratio, in humid air,
of calculation for air-conditioning and ventilation of expressed as a percentage, of the water vapour actual
immmmodatioo spaces and the radio cabin on hoard pressure m the saturated vapour pressure at the same
seagoing merchant ships for allconditions except those dry bulb temperature.
encountered in extremely cold or hot climates (that is
3.5 Dry Bulb Temperature — Temperature indicated
with lower orhigher conditions than those stated in 4.2
by a dry temperature-sensing element shielded from
and 4.3).
the effects of radiation.
Annex Aprovides guidance and detai1sof good practice
E.rample — The bulb of a mercury-in-glass
in the clesign of ventilation and t~ir-c~~rlditi(>lling
thermometer is an example of a dry temperature- ,.
systems in ships.
sensing element.
Anilex Bgives the thermal cmnductivities ofcommonly
4 DESIGN CONDIITONS
used construction materials.
4.1 General
2 REFER13NCF,
The system shall be designed for the indoor air
The following standard contains provision. which
conditions specified in4.2 and 4.3 inallaccommodation
thr~~ughreference in this text, constitutes provision of
spaces defined in3.1 atthe stated outdoor airconditions
this standard. At the time of publication the edition
and the outdoor supply airflow, ventilation and air
indicated was valid. Allstandards are subject torevision
balance given in6.2.1,6.2.2 and 6.5 respectively.
and parties to agreements based on this standard is
encouraged to investigate the possibility of applying NCSTE—Alltemperature statctlaredrybulbtemperatures.
the most recent edition of the standard indicated below.
4.2 Summer Temperatures and Humidities
ISA//). Title
Summer temperatures and humidities shall as follows
1S90 (Part 4) : Quantities, units and symbols: Part 4
unless otherwise specified by the user:
‘7~OJ Heut (.se(wncfrzwi.sio}f)
a) OUtd[>t)rair : +35° C and 70 percent
3 ‘rl;RNfs AND DEFINITIONS
humidity; and
Ft~rthe purpose of this standard the definitions given b) indoor air : +27g C and 50 percent
InIS 1890 (Part 4) and the following shall ap[Jly. humidity.
3.1 Accommodation — Space used as public rooms, NOTE — Inpractice.the indoor air conditions obtained.
>peciallyhumidity, cisnbediflercnt fromthosestated,
~alqins.offices, hospi[als. ci~,emas. games and hobby
rooms. ha[tx{ressirig sal(mns and pantries without 4.3 Winter Temperature /!
cooking appliances.
Winter temperatures shall as follows unless otherwise
3.2 .Air-Conditioning — Form of air treatment
specified by the user:
whereby temperature, hulnidity, ventilfition and air
cleanliness are all controlled within limits prescribed a) Outdoor air : –20”C; :lnd
for the enclosure to be air-conditioned. b) Indoor air : +22”C.
3.3 Ventilation — Provision of’airtoanenclosed space, N(.)TE—ThislndianStandarddotsnotspecifyrcquiremcnls
forhumidification inwinter,
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Is 14754:2008
4.4 Outcloor Air 5CALCULATION OF HEAT GAINS AND LOSSES $
‘[he minimum quantity of outdoor air shall be not less 5.1 Applicability
{h:in4(l pcrccntofthctota[ airsupplied to the spaces
cf)nccrncd, a) For the calculation of summer conditions, 5.2 )
,.
to 5.5 inclusive shall apply; and
4.5 Occupancy b) For the calculation of winter conditions, 5.2
only shall apply.
‘1‘hcnumber of persons to be allowed for inthe various
.lccommociation spaces shall be as follows, unless
5.2 Heat Transmission
~)(llcrwlsc stated by the purchaser. 1:
5.2.1 kfethod of Calculation
[
d) Cabins — the maximum number of persons 1’
for which the cabin was designed; The following formula shall be used for calculating
J
b) Public rooms such as saloons, mess or the transmission losses or gains, in watts, for each J 1
:
separate surface:
dining-rooms and recreation rooms — the ;,
,,. ,
number of persons who can be seated or, in
the case where the purchaser does not specify:
where
1j One person per 2mzfloor area forsaloons;
,.
2) One person per 1.5mzfloor area for mess AT = difference inairtemperature, inkelvins, for
— or dining-rooms; and the difference of air temperature between
air-conditioned and non-air-conditioned
3) one person per 5 m2 floor area for
internal spaces (see5.2.2);
recreation-room.
c) Coptffin’s and chief engineer’s clay-room — k, = total heat transfer coet%cient, in watts per
four persons; square metre kelvin, for the surface A, ,.
(see 5.2;3);
d) Other private dayrooms — three persons;
A, = surface, in square metres, excluding side
c) Hospital — thenumber of beds plus two;
scuttles and rectangular windows (glazing
1) Gy/nnasiunz, games-room — four persons;
+ 200 mm) (see Fig. 1and Fig. 2);
@ First-aid room — two persons;
kg = total heat transfer coefficient, in watts per ,
h) Ofices — two persons;
square metre kelvin, for the surface A~
i) M~lchiile control room — two persons; (see 5.2.3);
k) Wheel house — three persons; ~
Ag = a~ea, in square metres, of side scuttles and
m) C(~/7r/itl//2iccltiot/ equipment room — one rectangular windows (gla~ing + 200 mm)
pet-son: and (see Fig. 1and Fig. 2).
n) Gol[er)J — two person.
Dimensions inmillimetres
Fm. 1SIDE SCUTTLES
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IS 14754:2008
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Dimensionsinmillimetres.
Flci. 2 R~CTANCiULAWRINDOWS
5.2.2 Temperature Differences Between Adjoining watts per square metre kelvin, given inTable 2assume
[nternul Spaces that adequate thermal insulation is provided on all
surfaces exposed to outdoor conditions or adjoining
For differences of air temperature AT, in kelvins,
hot or cold spaces, or hot equipment or pipework.
he~ween conditioned and non-air-conditioned internal
spaces. see Table 1. The values given in Table 2 shall be used where
appropriate, unless otherwise advised by the purchaser.
5.2.3 Total Heat Transfer Coefficients
For other cases, amethod of calculation of coefficient
‘Mc values for the total heat transfer coefficients, k,in is given in 5.2.4.
Table 1Temperature Differences Between Adjoining Internal Spaces
(Clause 5.2.2)
S1No. Deckor Bulkhead AT, K
Summer Winter
(1) (2) (3) (4)
i) Deckagainsttankprovidedwithheating 43
ii) Deckwithbulkheadagainstboiler-room 28 17
iii) Deckandbulkheadagainstengine-roomandagainst 18
non-air-conditionedgallery
iv) Deckandbulkheadagainstnon-heatedtanks,cargo 13 42
spacesandequivalent
v) Deckandbulkheadagainstlaundry 11 17
vi) fleckandbulkheadagainstpublicsanitaryspace 6 0
vii) Deckandbulkheadagainstprivatesanitmyspace
n) withanypartagainstexposedexternalsurface 2 0
b) notexposed 1 0
c) withanypartagainstengine/boiler-room 6 0
viii) Bulkbe?dag~installeyway 2 5
NOI%—Itisunderstoodthatmeansofheatlrgare providedinexposedsanitaryspace,
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Is 14754:2008
5.2.4 Calculation of Heat Transfer Coefficient d = thickness of material, in m;
‘The heat transfer coefficient shall be calculated as ~ = thermal conductivity, in watts per metre
follows: kelvin [W/(m K)];
Ml< = thermal insulance for an air gap, in square
metres kelvin per watt [m~.K/W];
Mb = thermal instdance between different layers
where of material, in square metres kelvin per
watt [mZ.K/W];
L = total heat transfer coefficient. in watts per
square metre kelvin [W/(m2.K)]; P = correction factor for steel structure as
follows:
u= coefficient of heat transfer for surface air,
p = 1.2 for insulation in accordance with
in watts per square metre kelvin [W/(m2. K)],
Fig. 3,
as follows:
tx = 80 W/(m*. K) for outer surface P = 1.45 for insulatim inaccordance with
Fig. 4.
exposed to wind (20 m/s),
u = 80 W/(m2. K) for inside surface not
exposed to wind (0.5 m/s);
FIG. 3 PLANE InSUlatiOn OFUNIFORMTHICKNESS
FIG. 4 CORRUGATEDINSULATIONOFUNIFORMTHICKNESS
Table 2 Total Heat Transfer Coetllcient
(Clause 5.2.3)
s! Surfaces Total Heat Transfer
No. Coetlicient,
kW (m’.K)
(1) (2) (3)
i) Weather deck notexposed tosun’s md]ation a)ldshipsicieandexternal bulkheads 0.9
if) Deck andbulkhead against engine-room, cargo spaceorother non-air-conditioned space 0.8
Iii) Deck andbulkhead against boiler-room orboiler inengine-room 0.7
iv) Deck against open air orweather deck exposed w sun’s radiatioa anddeck ayainst bottanks 0.6
v) Side scuttles and rectangular windows, single glazing 6.5
vi) Side scuttles andrectangular windows, double glazing 3.5
\}i) Bolhhead against alleyway, non-sound reducing 2.5
viii) Bulkhead against alleyway, soundreducing 0.9
!NO1’l:s
I [~uidance onvalues oftbe:mal conductivities ofcommonly usedmaterials isgiven inAnnex B,
2Forthermal insulance, M., ofnon-ventilated air gaps,seeTable 3.
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IS 14754:2008
Table 3 Thermal Insulance of Non-ventilated Air Gap
(Zlt)lr’2)
SIN(J. BoundaryM-faces ofAir Gap Air GaISThickness. al) Thermal Insulnnccz)
m2.KAJ
(i) {2) (3) (4)
1) Bothsurtaccshavingblghemlsswty 5 ().11
20 (1.15
200 (1.1{>
Iil Onesurfmehavinghighermssivity,othersurfacelowwnmswtty 5 u,17
20 0,43
200 (:,47
iii) Bothsurfaceshavinglowemissivity 5 0.18
20 0.47
200 0.51
iv) Highemissivitysurfacesincontact3) o 0.9
“SeeFig,3andFig.4.
I)The~em-them,a] insu[ancc$,isusedaccordingtothedcfimtion~hll inis 1890 (part4).
‘)Aluminiumfoilandotherpolishedsurfacesareassumedtohavelowemissivity(0.2).Allothersurfacesareassumedtohavehigh
emissivity(0.9).
5.2.5 Measarernent ?f Transmission Areas Surface not included in A,. beeause of shadow from
.
overhanging deck or other means of sun protection,
The transmission areas for bulkheads, decks and ship
shall be calculated at a sun angle of 45°.
sides shall be measured from steel to steel.
NOTES
5.3 Solar Heat Gain
1Ifsolarradiationreflecting glassisused,G,maybe reduced.
2Theexcesstemperatures forverticalandhorizontal surfaces
So]tir heat gain, cD,.is calculated, in watts, Mfollows:
antitheadditiona!heatgainfromglasssurfacescausedbysolar
mrliationarebasedonthemostextremeaveragetemperatures
insubtropicalclimateandgiventheworstconditionoccurring
duringaday.
where
5.4 Heat Gain from Persons
A\, = surface exposed to solar radiation in squme
Values of sensible and latent heat emitted by aperson
metres (side scuttles and rectangular
at an indmjr temperature of ‘27°Care given inTable 4.
windows are not included); i
k= total heat transfer coefficient in accordance Table 4 Body Activity and Heat Emission
with 5.2.3 or 5.2.4 for aship structure (deck,
s]No. Activity Type ofHeat Emission
outer bulkhead, etc.) within the surface Av;
1 w
ATr= excess temperature (above the outside
(1) (2) (3) (4)
temperature of + 35°C) caused by solar —. .—
‘J radiation on surfaces as follows: i) Serrtatrest a)Sensibleheat 45 120
b)1.aten(heat 135,1
a) AT,= 12K for vertical light surfaces, ii) Mediumiheavywork a)Sensibleheat 85
b)Latentheat I50 235
b) AT, =29 K for vertical dark surflxes, I ‘4
c) .AT,= 16Kfor horizontal light surfaces,
5.5 Heat Gain from Lighting and Other Sources
d) AL = 32 Kfor horizontal dark surfaces,
In spaces with daylight, additional heat gain from
A= glass surfaces (clear opening) exposed to
:
solar radiation, in m2; lighting shall be ignored.
G, = heat gain per square metre from glass Inspaces without daylight, the heat gain from lighting
surfaces as follows: shall be calculated from the rated wattage of the
lighting, as advised by the purchaser or as specified
G,= 350 W/m~ for clear glass surfaces; and
by the appropriate authority. Where the rated output is
G,= 240 W/m> for clear glass surfaces with
not specified by the purchaser or the appropriate ,,,,
interior shading.
authority, the heat gain from general lighting shall be
For corner cabins, the surface w/hich gives the highest
taken as stated in Table 5, with consideration given to
cD,shall be chosen for calculation of the heat gain.
special lighting requirements.
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