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ВИРОБНИЧО-ТЕХНОЛОГІЧНІ СИСТЕМИ:
ТЕХНОЛОГІЇ ТА СИСТЕМИ ЕНЕРГОПОСТАЧАННЯ
52 ТЕХНОЛОГІЧНИЙ АУДИТ ТА РЕЗЕРВИ ВИРОБНИЦТВА — № 3/1(41), 2018, © Basok B., Tkachenko M., Nedbailo A.,
Bozhko I.
ISSN 2226-3780
hazu zrilykh rodovyshch // Komunalne hospodarstvo mist. Seriia:
Tekhnichni nauky ta arkhitektura. 2017. No. 134. P. 52–57.
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rence. Miskolc, 2004.
16. Alyaari M. Paraffin wax deposition: Mitigation and removal
techniques // SPE Saudi Arabia section Young Professio-
nals Technical Symposium. 2011. P. 1–10. doi: http://doi.org/
10.2118/155412-ms
17. Gupta A., Sircar A. Introduction to Pigging & a Case Study on
Pigging of an Onshore Crude Oil Trunkline // Journal of Latest
Technology in Engineering, Management & Applied Science.
2016. Vol. 5, No. 2. P. 18–25. URL: https://www.researchgate.
net/publication/307583466_Introduction_to_Pigging_a_Case_
Study_on_Pigging_of_an_Onshore_Crude_Oil_Trunkline (Last
accessed: 16.01.2018).
18. Skorobagach M. A. Problemy ekspluatatsii sistemy sbora gaza
na mestorozhdenii Medvezh’e // Tekhnologii nefti i gaza. 2011.
No. 6. P. 42–47.
Grudz Volodymyr, Doctor of Technical Sciences, Professor, Head
of Department for the Construction and Repair of Gas Pipelines
and Gas Reservoirs, Ivano-Frankivsk National Technical University
of Oil and Gas, Ukraine, ORCID: https://orcid.org/0000-0003-
1182-2512, e-mail: v.grudz@nung.edu.ua
Marushchenko Victor, Head of the Department of Ground Infrastruc-
ture, JSC «UkrGasVydobuvannya», Kyiv, Ukraine, ORCID: https://
orcid.org/0000-0001-8732-2712, e-mail: marushchenko@ugv.com.ua
Bratakh Mikhailo, PhD, Senior Researcher, Head of Gas Trans-
portation Department, Ukrainian Research Institute for Natural
Gases, Subsidiary of the UkrGasVydobuvannya, Joint-Stock Company,
Kharkіv, Ukraine, ORCID: https://orcid.org/0000-0002-5464-7921,
e-mail: mikhailo_bratakh@ukr.net
Savchuk Myroslav, Head of Industrial Pipelines And Electrochemical
Protection Sector, Department of Ground Infrastructure, JSC «UkrGas-
Vydobuvannya», Kyiv, Ukraine, ORCID: https://orcid.org/0000-0003-
0879-0476, e-mail: mirosavchuk@gmail.com
Filipchuk Oleksandr, Division for the Collection, Preparation and
Transport of Hydrocarbons, Department of Ground Infrastructure,
JSC «UkrGasVydobuvannya», Kyiv, Ukraine, ORCID: https://orcid.org/
0000-0003-4255-1663, e-mail: oleksandr.filipchuk@outlook.com
UDC 628.88
DOI: 10.15587/2312-8372.2018.135783
RESEARCH INTO ENERGY EFFICIENCY
OF THE UNDERFLOOR HEATING
SYSTEM, ASSEMBLED DRY
Об’єктом дослідження є теплотехнічні параметри роботи фрагмента системи підлогового опалення
сухого монтажу в умовах реальної експлуатації, який встановлено в лабораторному приміщенні.
Одним з найбільш проблемних місць при проведенні експериментальних досліджень виявилась мала площа
досліджуваної системи опалення, відносно об’єму приміщення. При значних добових коливаннях температури
зовнішнього повітря виявлялись складнощі з виходом роботи системи опалення на квазістаціонарний режим.
В ході дослідження встановлено вплив товщини теплоізоляційного шару під опалювальним контуром на
зміну густини теплового потоку від поверхні підлоги до повітря в опалювальному приміщенні. Зазначається,
що система підлогового опалення сухого монтажу має малу теплову інерційність завдяки відсутності відносно
товстого шару монолітної бетонної плити (із високою питомою теплоємністю), в якій зазвичай облашто-
вується контур системи опалення.
Зокрема встановлено, що використання керамічної плитки, як фінішного покриття, в порівнянні із ламі-
натом, суттєво зменшує загальний термічний опір теплопередачі від теплоносія до повітря в приміщенні, що
опалюється. При цьому наявність алюмінієвої теплорозподільної пластини, з якою безпосередньо контактує
зовнішня поверхня труби опалювального контуру, позитивно впливає на рівномірність розподілу теплового
поля в площині підлоги. Це в свою чергу призводить до зменшення термічних напружень у фінішному покритті.
Розрахунки показують, що кількісне регулювання теплового навантаження такої системи, завдяки зміні
витрати теплоносія, виявляється менш ефективним аніж якісне, за допомогою зміни його температури.
Експериментальні дослідження демонструють, що густина теплового потоку на поверхні підлоги
збільшується майже вдвічі при використанні керамічної плитки у порівнянні із ламінатом при всіх, майже
ідентичних, інших теплотехнічних параметрах системи.
Проведені дослідження дають змогу розробити математичну модель роботи системи підлогового
опалення сухого монтажу, за допомогою якої, стане можливим провести оптимізаційні розрахунки та
вдосконалити конструкцію даного опалювального приладу.
Ключові слова: водяне підлогове опалення, опалювальний контур, теплове навантаження, термічний
опір теплопередачі, тепловий режим приміщення.
Basok B.,
Tkachenko M.,
Nedbailo A.,
Bozhko I.
1. Introduction
Global trends in increasing the energy efficiency of heat-
ing supply systems in general are aimed at the utilization
of natural renewable energy sources, damped secondary
energy resources, decentralization of heat supply, as well
as a transition to low-temperature heating systems. When
applying heat pump installations as part of heat supply
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systems, predominant are the low-temperature systems of
water underfloor heating. This is due to the fact that at
such heating the area of heat exchange between a heat
carrier and air in a room is much larger in comparison
with other systems and, accordingly, the temperature po-
tential of the heat carrier can be reduced. In addition, the
underfloor heating provides the most comfortable sanitation
conditions for the stay of a person in premises.
Therefore, it is a relevant task to study influence of
the design and a finishing coating of the low-temperature
underfloor heating systems on their thermal-engineering
characteristics and energy efficiency.
2. The object of research
and its technological audit
The object of research is the heat-technical characteristics
of operation of a fragment of the system of underfloor
heating, assembled dry, with an area of 6.36 m2 and the
size of 1.2 × 5.3 m.
The heating system was arranged in the middle of the
laboratory facility with an area of 18 m2 and the size of
3×6×3 m. Its mounting scheme is shown in Fig. 1.
Fig. 1. Diagram of the underfloor heating, assembled dry:
1 – finishing flooring (laminate, ceramic tiles); 2 – substrate (cellulose,
gypsum fiber); 3 – aluminum heat distributor; 4 – foam polystyrene plate;
5 – pipe in a heating circuit; 6 – starting floor
The heating circuit is made of the PeX metallic poly-
meric pipe with an outer diameter of 16 mm and a wall
thickness of 2 mm. Thicknesses of the aluminum heat dis-
tributor and the plate made of extruded foam polystyrene
with grooves (channels) were, respectively, 0.2 mm and
40 mm (total, varies in different experiments).
By using such a technical solution, we thermostated air
of the room according to sanitary-hygienic norms (20 ± 2 °C)
under quasi-stationary conditions. Depending on the tem-
perature of ambient air, we discretely assigned the values
for electric power (thermal load) at the flow-through elec-
tric water heater to compensate for the heat losses in the
premises at a constant flow rate of the heat carrier in a
heating system circuit. To adjust the power of the electric
water heater VPO-5,5/220, we used the stabilized source
SSK-1-3-220 (Russia) with electric current 220 V at 50 Hz,
the laboratory auto-transformer RNO-250-5 (Ukraine) and
the portable measuring Kit K-50 (Ukraine), which regis-
tered electric current, electric voltage, and power, in the
course of our research.
Experimental values for electrical power were set: 200,
300, 400, 500, and 600 W. The experiment continued until
the stabilization of the temperature field distribution in
the air above the floor and in the layers of the premises
floor (the absence of change in the values of temperature
and heat flow at specific locations of measurement). The
time it took for the examined system with a laminate
coating to enter the quasi-stationary operating mode was
about 8–12 hours depending on the heat load.
One of the most problematic issues when conducting
experimental research was a small area of the examined
heating system, relative to the volume of the premises.
Considerable daily ambient air temperature fluctuations
resulted in certain difficulties while the heating system
entered the quasi-steady mode.
3. The aim and objectives of research
The aim of present research is to identify ways to im-
prove the overall energy efficiency of the underfloor heating
system, assembled dry. To achieve the set aim, the following
tasks have been solved:
1. To research experimentally the effect of thickness of
the heat insulating layer on the properties of heat transfer
from the heat carrier to the air in the premises.
2. To investigate experimentally the influence of the
type of a finishing coating in the system of underfloor
heating, assembled dry, on the properties of heat transfer
from the heat carrier to the air in the premises.
3. To determine the optimal operational mode and
a method to control the heat output of the underfloor
heating system.
4. Research of existing solutions
of the problem
Insufficient attention has been given to studying the
process of heat transfer in the systems of underfloor heating.
The basic method of research is mathematical modeling of
the operation of a warm water floor under different bound-
ary conditions. Thus, papers [1, 2] considered a classic
problem on modeling the heat supply to premises using
an underfloor heating system. The authors introduced the
concept of equivalent thermal resistance – using which
may enable the optimization calculations and selection of
a finishing coating composition. However, a significant num-
ber of simplifications of geometrical shapes and boundary
conditions degrade the accuracy of the results obtained.
Several papers address the development of non-stationary
models of the thermal interaction between an underfloor
heating system and air inside the premises under different
conditions. Authors consider the dynamics in heating the
premises [3] and propose non-standard multi-layer heating
systems [4]. However, it is difficult to evaluate the adequacy
of their work without verification of these models on the
basis of experimental studies. These studies lack any analy-
sis of the effect of thermal-physical properties of the floor
finishing coating on the efficiency of underfloor heating.
Several articles report studies into operation of the
system of underfloor heating and the effect of furniture on
the distribution of temperature and a thermal regime in
the premises. Thus, paper [5] investigated a living premi-
ses with an underfloor heating system in the presence
of furniture. The authors present results of mathematical
ВИРОБНИЧО-ТЕХНОЛОГІЧНІ СИСТЕМИ:
ТЕХНОЛОГІЇ ТА СИСТЕМИ ЕНЕРГОПОСТАЧАННЯ
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modeling and their comparison with experimental data.
The most detailed analysis of the impact of a floor fini-
shing coating is given in [6]. The study was conducted
using a warm water floor laid in a concrete pillow in
line with a standard method. The authors constructed
a mathematical model and carried out experimental study,
which showed expediency of using materials with high
thermal conductivity as a finishing coating. Another im-
portant factor is the thermal insulation of the surface over
which an underfloor heating system is assembled.
Another area of research into low-temperature heating
devices is the optimization calculations and search for
innovative solutions when creating systems of underfloor
heating. Paper [7] considers the model and results of cal-
culation of the floor heating device, which exploits effects
of phase transitions of the heat carrier during heat supply
from a heat pump. Articles [8, 9] examine the possibility
of joint application of low-temperature and classic heating
appliances in homes. However, there are no data on the
experimental research and evaluation of the effectiveness
of such systems of underfloor heating.
Work [10] explores the operation of an underfloor hea-
ting system along with a heat pump of the «air-water» type.
A series of experiments were conducted, which resulted
in the detected economically optimal mode of operation
of a given heating system.
Thus, the research into and improvement of the ope-
ration of an underfloor heating system is a promising task
related to increasing the efficiency of heat supply systems
to premises. However, the cited authors consider «clas-
sic» systems of underfloor heating, namely tubular heat
exchangers, which are built into concrete or cement pil-
lows. At the same time, little attention is paid to the
development of new designs for the underfloor heating
systems and to studying influence of the finishing coating
on the effectiveness of their operation and a temperature
regime of premises under conditions of actual operation.
5. Methods of research
Undertaking the experimental research implied mea-
suring, in real-time mode, the density of heat flow and
temperature in specific locations of the heating system
and the temperature of air inside, using thermoelectric
converters, followed by an analysis of the efficiency of heat
transfer between the heat carrier and air in the premises.
While conducting experiments, the following values
were registered by a system of secondary control-measuring
instruments at intervals of 10 minutes:
– air temperature for the height of the room at 16 mea-
suring points (we determined the average temperature t) ;
– temperature of the external air;
– temperature at different control points (including at
the floor surface above the feed and reverse pipelines)
in the underfloor heating system, both horizontally (in
various locations relative to the heating circuit) and
vertically, under the heating area and between layers
of the system (– 430.0…0.0 mm);
– value of the heat carrier temperature at the inlet
and outlet of the heating circuit;
– value of the heat flow density under the floor, bet-
ween different layers of the floor, at the floor surface
in specific locations relative to the heating circuit (rect-
angular designations) (Fig. 2).
Using readings from the heat meter Apator LQM-III-K
(Poland), which is installed before the inlet to the system
circuit, we determined a discrete heat load, which corres-
ponded to the installed power for the electric water heater.
When conducting all experiments, we chose days with
a minimum daily fluctuation of values in the outdoor tem-
perature and its motion speed (wind). That ensured the
maximum proximity to the permanence of heat losses in
the premises over time.
According to the specifications, one should accept, in
the areas of the greatest cooling in premises (close to
external enclosures), that temperature at the surface of
a heated floor should does not exceed 35 °C. That was
also taken into consideration while carrying out experi-
ments (accordingly, the heat load was not exceeded).
In this case, the overall relative error of measuring
the basic physical quantities under the automated mode
was not more than 5 %.
We conducted a series of experiments with the values
of the volumetric flow rate of heat carrier in the circuit of
underfloor heating of G = 0.102 and 0.058 m3/h, different
total thickness of the foam polystyrene plate of 40, 50,
80 mm, and finishing coatings made of laminate and tile.
Laminate with a thickness 8 mm was laid in line with
technology onto a cellulose substrate with a thickness of
4 mm, and 8-mm thick ceramic tiles were glued, using
a specialized mixture, onto an aluminum heat distributor.
If we are to consider premises with water underfloor
heating as a heat exchanger between the heat carrier in
a heating circuit and air in the room, it is possible to
write the equation of heat transfer for a given system:
Qk
Ft
=⋅⋅Δ , (1)
where k is the coefficient of heat transfer in the system of
underfloor heating, W/(m2·K) (it takes into account a con-
siderable number of factors related to the design of underfloor
heating); F is the heat exchange surface area, m2.
Fig. 2. Arrangement of sensors in the system of underfloor heating
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In this case, the average difference between tempera-
tures of water and air (a temperature head)
Δ
t is derived
here from formula [11]:
Δ
ΔΔ
Δ
Δ
t
tt
t
t
=−
ma
xm
in
max
min
ln
, (2)
where Δtmax is the temperature difference between water
at the inlet to the heating circuit and air in the premises;
Δtmin is the difference between water temperature at the
outlet from the heating circuit and air in
the premises, °C.
Specific heat flow from the surface of
the floor, which can be provided by the
system of water underfloor heating of a
certain design, is directly proportional to
the average temperature difference between
a heat carrier in the system and air in the
heated premises:
qkt=⋅Δ. (3)
The above coefficient accounts for the
thermal resistances of a pipe in the hea-
ting circuit and of a monolithic hea ting
slab (panel), inside which a heating cir-
cuit is installed, a finishing layer of the
floor, layers of thermal insulation under the
heating circuit. As well as the geometrical
parameters of the system: pitch of laying
a pipe and its diameter [12]. This gives
rise to computational difficulties related to
analytical determining of the heat transfer
coefficient of such a system.
6. Research results
The results of calculations that we de-
rived can be represented in the form of no-
mograms of thermal load for separate designs
of water underfloor heating whose thermal-
technical parameters are investigated. The
nomograms were constructed for different
values of thickness of thermal insulation
(foam polystyrene plates), volumetric flow
rate of heat carrier in the circuit, outdoor
temperature (heat losses in the premises)
and the floor finishing coating.
The nomograms allow us to determine
the heat transfer coefficient k. Its magni-
tude is equal to the value of the tangent
of the inclination angle in the nomogram
of thermal load in the heating system to
the horizontal axis of the abscissa.
By using the constructed nomograms,
given the assigned temperature in a room
and the temperature diagram of heat carrier
in the system, it is possible to determine
the required area for an underfloor heating
system whose heat output capacity would
provide for known heat losses from the
premises. These nomograms could form the
basis for an engineering technique of the
thermal calculation of low-temperature water underfloor
heating systems. Results of the experiments are represented
graphically in Fig. 3–5.
Fig. 3 shows that a significant increase in the ave rage
temperature of the floor surface is predetermined by the
use of ceramic tiles as a finishing coating. This is ex-
plained by the greater value of the thermal conductivity
coefficient of a given material. At the same time, diffe-
rent flow rate of the heat carrier over a certain range
has almost no impact on a change in the laminate sur-
face temperature.
Fig. 3. Dependence of the average temperature of floor surface on temperature of the heat
carrier at the inlet to the circuit of underfloor heating
Fig. 4. Dependence of density of the heat flow from the floor surface on the average difference
between temperatures of water and air in premises
15
17
19
21
23
25
27
29
31
20 25 30 35 40 45 50 55 60
Температура теплоносія на вході до контуру,
о
С
Середня температура поверхні підлоги,
о
С
ламіна т та 40 мм теплоізоляц ії
(G=0,102 м3/ год)
ламіна т та 40 мм теплоізоляц ії
(G=0,058 м3/ год)
ламіна т та 50 мм теплоізоляц ії
(G=0,102 м3/ год)
ламіна т та 80 мм теплоізоляц ії
(G=0,102 м3/ год)
плитка та 80 мм тепло ізоляції
(G=0,102 м3/ год)
(
Average temperature of floor surface
, oC
Temperature of heat carrier at the inlet to the circuit, oC
laminate and 40 mm of thermal
insulation (G=0.102 m3/h)
laminate and 40 mm of thermal
insulation (G=0.058 m3/h)
laminate and 50 mm of thermal
insulation (G=0.102 m3/h)
laminate and 80 mm of thermal
insulation (G=0.102 m3/h)
tile and 80 mm of thermal
insulation (G=0.102 m3/h)
0
10
20
30
40
50
60
70
80
90
100
0 5 10 15 20 25 30 35
Різниця середньої температури теплоносія та повітря, °С
Густина теплового потоку з поверхні підлоги, Вт/м
2
ламіна т та 40 мм те плоізоляц ії
(G=0,102 м3/ год)
ламіна т та 40 мм те плоізоляц ії
(G=0,058 м3/ год)
ламіна т та 50 мм те плоізоляц ії
(G=0,102 м3/ год)
ламіна т та 80 мм те плоізоляц ії
(G=0,102 м3/ год)
плитка та 80 мм тепло ізоляції
(G=0,102 м3/ год)
laminate and 40 mm of thermal
insulation (G=0.102 m3/h)
laminate and 40 mm of thermal
insulation (G=0.058 m3/h)
laminate and 50 mm of thermal
insulation (G=0.102 m3/h)
laminate and 80 mm of thermal
insulation (G=0.102 m3/h)
tile and 80 mm of thermal
insulation (G=0.102 m3/h)
Density of heat flow from floor surface, W/m
2
Difference between average temperatures of heat carrier and air, oC
ВИРОБНИЧО-ТЕХНОЛОГІЧНІ СИСТЕМИ:
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ISSN 2226-3780
That proves the thesis that the quantitative control
over heat efficiency of low-temperature heating systems is
not expedient. More effective in this case is the qualitative
regulation of heat load with a change in the temperature of
the heat carrier in the system. Increasing the thickness of
thermal insulation by two times reduces, based on certain
calculations, heat losses from the heat carrier in the circuit
into space under the floor heating system by about 12 %.
This, accordingly, leads to that a lower temperature of the
finishing coating surface helps achieve compensation for the
heat losses in the premises according to acting standards.
Fig. 4 demonstrates a substantial increase in the density
of heat flow at the surface of ceramic tiles as a result
of its lower thermal resistance and the denser (adhesive)
contact with the aluminum heat distributor. Changing
the values of flow rate of the heat carrier in the circuit
insignificantly affects specific thermal flow from the sur-
face of the laminate. Increasing the thickness of thermal
insulation by 10 mm makes it possible to increase the
density of heat flow at the surface of the floor by 5 W/m2.
Fig. 5 shows that the air temperature in the premises
rises higher in proportion to the growth in the temperature
of heat carrier at the inlet. It should be noted that the
average temperature of the outside air while conducting
various experiments ranged, in each, respectively, from –7
to 3 °С, which influenced heat losses in the premises. In
most cases, almost all experimental variants of a heating
system ensured the required thermal sanitary conditions.
7. SWOT analysis of research results
Strengths. Compared to analogues, a system of underfloor
heating, assembled dry, has a number of advantages – low
operation inertia, uniform distribution of the temperature
field due to the application of an aluminum heat distribu-
tor, and ease of assembly.
Weaknesses. The weaknesses of a given system of un-
derfloor heating include weak resistance to mechanical
damage. Because this system lacks a monolithic concrete
or cement pillow, a damage to the finishing coating may
result in a very high probability of the depressurization
of a heating circuit.
Opportunities. The experimental study that we con-
ducted make it possible to further develop a mathematical
model for the operation of an underfloor heating system,
assembled dry. Employing the model would enable perfor-
ming the optimization calculations to improve the design
of a given heating device.
Threats. The application of the examined system of
underfloor heating is associated with higher initial invest-
ments in comparison with similar heating devices. This
relates to the use of aluminum in the structure of a heat
distributor and a foam polystyrene plate with special slots.
8. Conclusions
1. We established in the course of our experimental
studies the influence of thickness of a thermal insulating
layer on the properties of heat transfer from the heat car-
rier to the air in the premises. A standard plate made of
extruded foam polystyrene with a thickness of 40 mm is
not capable to minimize heat losses into the floor under
a floor heating system, assembled dry. This is explained by
the design features of a given heating system – grooves
under the circuit pipe decrease by almost twice the ther-
mal insulating layer under it. Increasing the thickness of
thermal insulation to 50 mm makes it possible to improve
the operating efficiency of an underfloor heating system
by 10 % (density of the heat flow increases from 50 to
55 W/m2 at a temperature of 20 °C in the premises).
A further increase in the thickness of an insulating layer
to 80 mm has not produced any significant effect.
Fig. 5. Dependence of the heat carrier temperature at the inlet to the circuit of underfloor heating on the difference
between average temperatures of heat carrier and air in the premises
16
17
18
19
20
21
22
23
20 25 30 35 40 45 50 55 60
Температура теплоносія на вході до контуру, ºС
Температура повітря в приміщенні, ºС
ламіна т та 40 мм те плоізоляц ії
(G=0,102 м3/ год)
ламіна т та 40 мм те плоізоляц ії
(G=0,058 м3/ год)
ламіна т та 50 мм те плоізоляц ії
(G=0,102 м3/ год)
ламіна т та 80 мм те плоізоляц ії
(G=0,102 м3/ год)
плитка та 40 мм тепло ізоляції
(G=0,102 м3/ год)
Temperature of heat carrier at the inlet to the circuit, oC
Air temperature in premises, oC
laminate and 40 mm of thermal
insulation (G=0.102 m3/h)
laminate and 40 mm of thermal
insulation (G=0.058 m3/h)
laminate and 50 mm of thermal
insulation (G=0.102 m3/h)
laminate and 80 mm of thermal
insulation (G=0.102 m3/h)
tile and 80 mm of thermal
insulation (G=0.102 m3/h)
INDUSTRIAL AND TECHNOLOGY SYSTEMS:
TECHNOLOGY AND SYSTEM OF POWER SUPPLY
57TECHNOLOGY AUDIT AND PRODUCTION RESERVES — № 3/1(41), 2018
ISSN 2226-3780
2. Considerable influence on the properties of heat
transfer from the heat carrier to the air in the premises
is exerted by a finishing coating. When using ceramic
tiles and at the same consumption and temperature of
the heat carrier at the inlet, the density of heat flow at
the floor surface increased by 50 % (from 57 to 86 W/m2
at a temperature of 20 °C in the premises).
3. The experimental research that we conducted al-
low us to argue about the system of underfloor heating,
assembled dry, yielding a greater thermal maneuverability
compared with a fill-in screed, as well as demonstrating
a low heat-accumulating capacity. A small thermal-inertial
component is achieved through the absence of a relatively
thick layer of the monolithic concrete slab, inside which
the heating system circuit is typically installed. The ap-
plication of aluminum heat-distributing plates contributes
to the levelling of a heat flow in the plane of the floor
surface, which positively influences the heat distribution
and reduces thermal stresses in the finishing coating. Exe-
cuting the quantitative control over a thermal load of the
system, owing to a change in the consumption of a heat
carrier, turns out to be less effective than the qualitative
regulation via changing its temperature.
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Basok Boris, Doctor of Technical Sciences, Professor, Head of the
Department of Thermophysical Basics of Energy-Saving Technologies,
Institute of Engineering Thermophysics of the National Academy
of Sciences of Ukraine, Kyiv, Ukraine, e-mail: basok@ittf.kiev.ua,
ORCID: http://orcid.org/0000-0002-8935-4248
Tkachenko Mуroslav, PhD, Senior Researcher, Department of
Thermophysical Basics of Energy-Saving Technologies, Institute of
Engineering Thermophysics of the National Academy of Sciences of
Ukraine, Kyiv, Ukraine, e-mail: tkamyr@gmail.com, ORCID: http://
orcid.org/0000-0001-8345-1613
Nedbailo Aleksandr, PhD, Senior Researcher, Department of Ther-
mophysical Basics of Energy-Saving Technologies, Institute of En-
gineering Thermophysics of the National Academy of Sciences of
Ukraine, Kyiv, Ukraine, e-mail: nan_sashulya@ukr.net, ORCID:
http://orcid.org/0000-0003-1416-9651
Bozhko Igor, PhD, Researcher, Department of Thermophysical Basics
of Energy-Saving Technologies, Institute of Engineering Thermo-
physics of the National Academy of Sciences of Ukraine, Kyiv,
Ukraine, e-mail: bozhkoik@gmail.com, ORCID: https://orcid.org/
0000-0001-7458-0835
