Investigation of draught comfort in the occupied zone con-sidering the tangential air distribution system

(1)

BUDAPEST UNIVERSITY OF TECHNOLOGY AND ACONOMICS FACULTY OF MECHANICAL ENGINEERING

DEPARTMENT OF BUILDING SERVICE ENGINEERING AND PROCESS ENGINEERING

Investigation of draught comfort in the occupied zone con- sidering the tangential air distribution system

PhD proposition booklet Róbert Goda

Supervisor:

Dr. László Bánhidi, Prof. Emeritus

Budapest 2013.

(2)

1

1. Introduction and main aims

We spend a lot of time in closed spaces; as a result it is very important to investigate comfort parameters in ventilated spaces in HVAC systems. The tangential air distribution system is frequently used in designing practice, where the primary supply airflow is bordered with a surface (tangential air supplying). Besides, this air distribution type is a common solution in comfort and industrial type ventilated spaces. In my PhD dissertation the draught comfort was investigated, which is a widespread problem in the tangential air distribution systems.

As far as we know, draft (or draught) can be defined as a local discomfort factor, which can cause local overcooling of human’s body by airflow. This problem can be seen in residential buildings, on vehicles (e.g. cars, trains, airplanes, and so on). Consequently, draft is well known as one of the most disturbing discomfort factors in ventilated spaces. Because of draught, people usually require higher indoor air temperature, so the percentage of people dissatisfied with draft decreases, but the building’s energy consumption increases. Conse- quently, the investigations of air distribution systems are very important from the point of view of pleasant comfort, and energy saving in buildings.

Basically, the draught comfort is determined by: average air temperature, average air veloci- ty and fluctuating air velocity. The quotient of the fluctuating air velocity and average air ve- locity is named as turbulence intensity. There are several references investigating draught comfort in ventilated spaces, but the most important and nationally accepted investigations belong to Fanger et al.

Laboratory comfort investigations were completed with local investigations in residential buildings by applying measueremnt method.

Later, draught model (DR model) which was created by Fanger et al. in the 1970s was completed by several researchers. As a result, e.g. Wang et al. considered the exposure time of the occupants in the draft. With the help of this, the transient feature of ventilation could be considered. A further completion of the draught model is affect of local temperature drop on the skin.

The specific heat loss of the human skin (which depends on the amount of draught) can also be investigated by thermal manikin. It is known that the local skin temperature drop is connected to the draught.

Some researches (e.g. Fanger, Koskela, Moureh and Flick; Goda R. and Bánhidi L.) completed the measuerement results with numerical (CFD) simulation [35]. These investigations especially concentrated on thermal comfort and airflow pattern in the ventilated space.

By studying the international literature, I established that the aforementioned studies have not considered the connection between the exact type of the applied air distribution system and draught comfort. Each air distribution system makes different airflow characteristics in the ventilated space, therefore the velocity and temperature distribution can significantly change.

Based on the above it is obious that turbulence intensity distribution formed in the occupied zone of ventilated spaces depends on the exact type of the applied air distribution system. By the way, I have not found references investigating air supply and the occupied zone at the same time. As it is known, airflow pattern near the air supply strongly depends on the construction of the air diffuser and flow disturbances. These factors can significantly determine the airflow pattern in the room hereby draught comfort.

In spite of these facts, there only a few references investigating tangential air supply systems.

These investigations only focus on the airflow pattern in the room and the investigation of the air jets supplied from the air diffuser by numerically and experimentally.

(3)

2

Moreover, standards for calculating DR in the designing practice only suggest recommended turbulence intensity values. These standards do not consider the exact type of the applied air distribution system in the ventilated space. A very important question is that how many per- cent is the difference between turbulence intensities given in the standard and measured in a ventilated space applying tangential air distribution system.

To solve these aforementioned problems, in my PhD dissertation I have investigated a slot ventilated test room with tangential air distribution system at the Ventilation Laboratory of Budapest University of Technology and Economics. All the measurements were conducted in case of applying isothermal condition and stationary state airflow.

This dissertation investigates the draught comfort in the occupied zone of a test room according to standard MSZ EN CR 1752. This draught is caused by the fluctuating air velocity and the turbulence intensity. Actually, draught can de defined as a local overcooling of human’s body caused by airflow. This draught is marked as a local discomfort-factor which causes unpleasant comfort in the vebtilated space.

The problems connected to my field of research are the followings:

 In the ventilated space if the air velocity increases the local overcooling of the human’s body will be higher, as a result there will form a higher heat loss through the human’s skin. It will result draught discomfort.

 There are significant differences between turbulence intensities given in the standard and measured turbulence intensities in the occuopied zone considering a tangential air distribution system. The tangential air supply system with vertical air supply is not investigated considering the draught comfort.

My aims considering the problems (see above) and the professional requirements are the followings:

1. Measuring the fluctuating air velocoties and turbulence intensities in the occupied zone as accurately as possible.

2. Investigating the air velocity and turbulence intensity distribution in the occupied zone considering vertical air supply and tangential air distribution system. Based on these results, it is recommended to investigate the differences between turbulence intensity given in the standard and measured in the occupied zone.

3. A further aim to make a critical analysys of the professional literature and giving a proposal to complete the designing methods in order to calculate draught comfort in the occupied zone of ventilated spaces.

2. View of references

Several researchers found that draught (ot draft) can be defined as an unpleasant local discomfort factor in ventilated spaces, because it increases the local heat loss through the human body by airflow [3]; [4]; [12]; [30]. Besides, the presence of draught in the occupied zone is unfavourable, because the higher the amount of draught the higher the indoor air temperature required by the occupants. It may increase the energy consumption of the ventilation system [1]; [14]; [21]; [25].

The draught comfort was investigated by several researches in the past few decades in labora- tories [3]; [4]; [8]; [12]; [13]. The earliest study about draught is made by Houghten et al. in 1938 [14], and later in the 1970-80s Fanger et al. have investigated this problem [3]; [7];

[10]; [21]. The DR function the draught effect in beginning the average air velocity and it

(4)

3

was examined in the function of the temperature [3], this was supplemented with the turbulence intensity then [7]. Fanger and Melikov established it [7], that the fluctuating velocity component of the streaming air – beside the average air velocity – may increase the evolving draught sensation significantly. Later, draught model (DR model) which was created by Fanger et al. in the 1970s was completed by several researchers. As a result, e.g. Wang et al. [13] considered the exposure time of the occupants in the draft. With the help of this, the transient feature of ventilation could be considered. A further completion of the draught model is affect of local temperature drop on the skin [16]. In these studies the numbers of mea- surement points are less than in my investigations.

Only a few references considered the tangential air distribution system. These few ones especially concentrate on air jets and its features [6]; [15]; [17]; [18]; [20]. T. Magyar [5]

showed the different investigation methods for several air distribution systems, including the tangential air distribution system and its draught comfort problems. In his [12] study the qualification of the occupied zones are introduced by applying statistical methods.

During the designing of ventilation systems it is very important to predict the draught rate (DR) in the occupied zone. Standards for designing only suggest recommended values considering the comfort category, but do not consider the xact type of the applied air distribution system [sz1]. There are only mixing or discplacement ventilation systems, but the exact type is not investigated. Consequently, in case of applying mixing ventilation, the recommended turbulence intensity value for calculating DR is 40 [%], while in case of applying displacement ventilation it is only 20 [%] [sz1]; [sz2]; [sz3]; [sz4]; [3]. Besides, these standards con- tain the measurement method of these values for calculating DR.

The characteristics of turbulent airflow (turbulence intensity, average air velocity and fluctuating air velocity) are investigated in residential buildings (like schools, offices, etc.) [2];

[9]; [10]; [11]. From these quantites the DR can be calculated. With the help of these inves- tigations I established that the turbulence intensity distribution in the whole occupied zone was not investigated. Hanzawa, Melikov and Fanger also made local comfort investigations in residential buildings [10]. In this study a tangential air distribution system ca be found in an office, but this configuration differs from the configuration I have investigated. T. Magyar and R. Goda [23] made a mathematical model about a tangential air distribution system, but its solution by analytical method is almost impossible, therefore they give further investtiga- tion methods.

The aforementioned studies do not consider the connection between the applied air distribution system and draught comfort including the turbulence intensity distribution in the space.

By the way, the researchers have not analized the occupied zone and the air supply at the same time.

Only a few tangential air distribution systems were investigated by experimentally and numerically. These few ones are concentrating on the air supply and air jets. [6]; [18]. Using CFD simaulation the thermal comfort and indoor air quality were investigated [23]; [24], but sometimes the airflow pattern was analized in the ventilated space [6]; [18], but we can find the DR analysys in these studies too [19]; [25].

Some researchers have applied thermal manikin in order to investigate local discomfort- factors. However, it is important to know that turbulence intensity cannot be measured direct- ly by thermal manikin, but the heat loss through this manikin can be measured [26]; [27];

[28]; [29]. The higher the amount of draft the bigger the local skin temperature drop [30]. In accordance with the above, these investigations concentrate on thermal discomfort, but do not consider the turbulence intensity distribution in the whole occupied zone.

(5)

4

3. Experimental method

In order to solve the main aims a measuerement investigation method was applied using a full cale (M1:1) model in a test room.

3.1. Descritption of the test room

The measurement investigations were conducted in a test room in the Ventilation Laboratory of BUTE (Fig 3.1.1.) Basic area of the test room is 3x3 [m] and the interior height is 3 [m].

The supply air was circulated by a CRAC (Computer Room Air Conditioning). In the ventilation system an air-filter was used in order to filter the supply air. The airflow rate to the room was measured and controlled by a flow control valve by measuring the dynamic pressure (Δpdyn) in Pascal. In this room the slot diffuser was located on the ceiling, near the wall. In the box of the slot diffuser a perforated plate was settled in order to get a homogenous airflow at the air inlet. This tangential air distribution system had vertical air inlet and vertical air outlet on the ceiling.

Fig. 3.1.1 Key:

CRAC = Computer Room Air Conditioning; F* – airflow damper and orifice plate; F – airflow damper; SZ – air filter; PC – personal computer; Δp_mp – measured pressure difference on the orifice plate

The nominal airflow rate to the test room went from 50 to 150 [m³/h]. In order to get a homo- genoues airflow in the air duct an air filter was built in in front of the orifice plate. The ventilation system is totally re-circulated.

The nominal length of the 1 line slot diffuser is L0 = 1000 [mm] and the width is s0 = 12 [mm] with a supply box.

(6)

5

3. 2. Measurement of the parameters

The measurement of the physical parameters included the followings:

 average air temperature [°C]

 at the air inlet at 45 point, in 8 series of measuerements;

 at the whole occupied zone at 116 points, in 7 series of measurements;

 relative air humidity [%]

 at the air inlet, in the occupied zone and under the air outlet;

 average air velocity [m/s]

 at the air inlet at 45 point, in 8 series of measuerements;

 fluctuating air velcity [m/s]

 static pressure difference in the air supply box [Pa];

 pressure difference at the orifice plate [Pa];

 turbulence intensity [%]

 at the air inlet at 45 point, in 8 series of measuerements.

Measurement of average air temperature

At the air inlet, under the air outlet and in the whole occupied zone the dry bulb temperature was measured and the sensor was made of hot wire probe NiCr-Ni. The ISO 7726 standard recommends a radiation protection for the probe used for measuring the temperature (eg, hot- cold floor, wall, etc). In this case, the walls and floor had of the same temperature as the room temperature so the heat radiation effect is negligible.

In the occupied zone the average air temperature was measured by an omni-directional hot sphere anemometer. The principle of the measuerements are similar to the hot-wire anemome- try [31]. The head of the sensor is equipped with an electrical conductivity probe sensor, whose electrical resistance varies considerably with the measured temperature. The probe is electrically heated, while the electronic control unit of the probe temperature was kept constant (eg, electrical resistance and holding constant). The probe is cooled by the airflow, so a convective heat transfer occurs between the probe surface and the air. The control electronics can compensate for the decrease in temperature control by varying the resistance, is proportional to the measured temperature.

Measuerement of the relative air humidity

The relative humidity was measured in the dry temperature set at the same time with a hot wire probe. The [sz5] standard recommends that the value of the temperature does not require treatment, since changes in the density of the air in the room does not exceed the interval specified by the standard, such as:

1.16 < ρ < 1.24 [kg/m³].

In contrast cases, a correction is needed for calculating the air density.

(7)

6

Measueremnt of average air velocity and fluctuating air velocity

Standards for ventilation measurements developed to measure some physical quantities are offered on a variety of instruments. According to EN ISO 5167-1:2003 used to measure the air velocity of any suitable instrument may use supposing that the applied instrument does not cause any interefernce to the flow. In practice this means that the smaller the respective measurement section, the smaller instrument must be used.

A furthet requirement is that these instruments must be calibrated at regular intervals. Stan- dard MSZ EN 24006:2002 requires that the normal direction of the airflow should be ortogon- al to the cross section of the measurement plane.

Average air velocity and the fluctuating component were measured in the occupied zone of the test room by an omni-directional hot sphere anemometer in accordance with standard ISO 7726.

In order to achieve the accurate measurement results it is needed to use at least 3 minutes measurement periods in accordance with the standard.

All of the measurements were conducted at four relevant heights according to the standard ISO 7726 (see Table 3.1.1.). The measurement accuracy depends on the class: comfort class (C) or thermal stress class (S).

Location of the sensors

Weighting factors Recommended heights Homogenous envi-

ronment

Heterogene environ-

ment Sitting Standing Class C Class S Class C Class S

Head level 1 1 1,1 [m] 1,7 [m]

Waist level 1 1 1 2 0,6 [m] 1,1 [m]

Ankle level 1 1 0,1 [m] 0,1 [m]

Table 3.1.1

During the tests, a total of three types of sampling time were applied to the velocity, temperature and turbulence intensity measurements. These were 60; 200 és 400 seconds, and finally the 200 seconds interval was applied for the final measuerements.

Static pressure difference measuerements

The size of the supply box is: 1000x90x240 [mm]. Number of holes for the static pressure measurements: 2 on the front side; 2 on the back side and 1 – 1 on the side.

The design of the static pressure drain holes requires careful circumspection, as the inadequate implementation of the measurement error increases. The hole should be perpendicular to the surface, in the end no protrusion nor strong lowering can not be [MSZ EN 24006:2002.]; [33].

Measurement of pressure difference at the orifice plate

Iris volume flow controller with the orifice is placed in the duct so that fulfilled specified by the manufacturer required clearance distance causing interference in the flow elements (e.g.

T-elbow, etc). The last flow disturbing element of the adjustable orifice cross-section was 3.5*D from the direction of flow.

The airflow rate to the room could be changed by changing the cross section of the iris plate using the measured pressure difference of the orifice plate [32]:

orifice

p F Const

V^₀   ^ 

(8)

7 Measuring the turbulence intensity

A measurement device was made for turbulence intensity measurements in order to position- ing the anemometer among the slot width. The distance between the measueremnt points was Δx = 3mm and the positions 0 and 4 correspond to the main sides of the slot diffuser (mainj edges). Position 0 is the side of the slot diffuser next to the wall surface, while the position 4 is the side of the slot diffuser from the occupied zone. All of the measurements were conducted at four relevant heights according to the standard ISO 7726.

According to standasrds ISO 7726 [sz2] and ASHRAE [34] at least 3 minutes measurement period was applied for turbulence intensity and air velocity measurements. In order to achieve accurate results, I have used 200 seconds period, but only 60 seconds for the temperature measuerements.

4. New scientific results

Proposition 1:

By making the turbulence intensity distribution diagram in the whole occupied zone I have established that there are significant differences between the 40 [%] turbulence intensities given in the standard and measured turbulence values, in case of applying a tangential air distribution.

Most of the measured data are less than Tu = 40 % in all series of measurements. However, there is some turbulence intensity that is higher than 40 %.

Number of series of mea-

surements

V0 [m³/h] Number of

Tu ≤ 40 [%] Number of Tu> 40 [%]

Percentage values of turbulence inten-

sities are less or equal to than 40 [%]

Percentage values of turbulence inten-

sities are higher than

40 [%]

1 139 85 31 73 27

2 124 92 24 79 21

3 110 67 49 58 42

4 100 72 44 62 38

5 91 94 22 81 19

6 79 81 35 70 30

7 66 97 19 84 16

(9)

8

It is recommended to be a significant difference in the turbulent intensities from standard 40 [%]. It would be suitable to investigate other mixing air distribution systems, considering draught comfort and turbulence intensities.

Proposition 2:

I have established that by decreasing the turbulence intensity the changing of the average air velocity increases. This tendendy is significantly intensive at turbulence intensities are less than 40 [%].

However, by increasing DR, the sensibility of the average air velocity and turbulence intensity for each other will be higher. Based on my measueremnt results it is obious that the average air velocity and turbulence intensity have compensate mechanism for each other.

In the HVAC practice this mechanism has a significant importance against the recommen- dations in standards.

Proposition 3:

Based on my result I established that in case of applying tangential air distribution system, at the slot diffuser the apparent profile factor, indtroduced by myself is constant as a function of the airflow rate to the room. Its average value is 0.75 and its standard deviation is 0.023.

As far as we know, the profile factor can be written as the quotient of the average air velocity and the maximum air velocity at the air inlet. In my dissertation, the introduced apparent profile factor is a modified version of the aforementioned profile factor, which is

Sensibility of average air velocity and turbulence intensity as a function of the air temperature on DR = 20 %

(10)

9

not related to the air inlet in contrast to the classical profile factor. The reference plane for the apparent profile factor is farher, than the air inlet. In this plane, the measured velocity profile can be described as a continous and symmetric curve; therefore the Simpson method could be applied in order to predict the apparent profile factor by me. This method is based on a numerical integrating method.

Proposition 4:

I have established that in case of applying tangential air distribution system, the location of the slot diffuser affects the turbulence intensity distribution. The turbulence intensity distribution next to the wall is more significant then from the occupied zone.

Base don my results I can say that in this air distribution system at the ankle level (y = 0.1 m), where there are more nerves, than at the other part of the body the turbulence intensity distribution is not homogenous in constrast with the average air velocity distribution.

I found that amond the slot diffuser’s length the amount of turbulence intensity is less at the centre of the slot (where the average air velocity has a maximum) then at the edge of the slot on a costant airflow rate. At the edge of the test room there are higher turbulence intensities because of the presence of the wall.

Proposition 5:

Based on my measuerement results in the occupied zone I have established that in case of applying tangential air distribution system, the location of the slot diffuser affects the average air velocity distribution in the room. Near the floor surface this distribution is almost homogenous similarly to the fluctuating air velocity distribution.

In case of applying tangential air distribution system at the higher relevant heights the measured air velocities related to the ankle level and this tendency can be observed at any series of measurement.

Tha ankle level is a relevant height (see proposition 4) from the point of view of designing draught comfort, therefore it is important to know the airflow characteristics there.

The relative air velocities show a nearly homogenous distribution at y = 1.1 m.

(11)

10 Proposition 6:

I have found that the changing of the average turbulence intensities at each height (y = 0.1;

0.6; 1.1 and 1.7 m) as a function of the airflow rate to the room. The least measured turbulence intensities can be found near the flooe (y = 0.1 m), then it increases as the height increases. Between y = 1.1 and 1.7 m measurement heights, the difference between the average of turbulence intensities is minimal.

5. Use of the results

Apparent factor profile measurements near the air inlet introduced as a result of the verification measurements is significant. To take into consideration the impact on the design of the slot diffuser supply can determine the airflow pattern near the air inlet. The design of the construction of slot diffuser primarily based on manufacturing considerations, such as the measurement results can help in the appropriate design of the geometry these diffusers.

Based on my measurement results, in case of applying tangential air distribution system the turbulence intensity and air velocity distribution is known at the relevant heights. Measured in the occupied zone of discrete points values are comparable to the standard proposed a 40%

rate turbulence values. As a result, the definition of subjective drafts DR number is accurate as determining points of the occupied zone; there were significant differences between the degrees of turbulence.

6. References

[1] Thermal comfort, ASHAE Handbook 2005 - Fundamentals.

[2] P. O. Fanger, C. J. K. Pedersen: Discomfort due to air velocities in spaces. Proc. of the meeting of Commission B1, B2, E1 of the IIR, Belgrade, 1977, 4, pp. 289-296.

[3] P. O. Fanger – N. K. Christensen: Perception of draught in ventilated spaces. Ergonom- ics, 29:2, pp. 215-235.

[4] Magyar Tamás, Dr.: Laboratóriumi kísérletek a huzathatás mérésének továbbfej- lesztésére. Magyar Épületgépészet, LVII. évfolyam, 2008/5. szám, p. 3-7.

[5] Magyar Tamás: A helyiségek levegőátöblítése. Épületgépészet, 1990. 5-6. szám.

[6] J. Moureh, D. Flick: Airﬂow characteristics within a slot-ventilated enclosure. Interna- tional Journal of Heat and Fluid Flow 26 (2005), p12–24.

[7] P. O. Fanger, Dr. – A. K. Melikov, Dr – H. Hanzawa: Air turbulence and sensation of draught. Energy and Buildings, 12 (1988) p. 21-39.

Changing of the averaga air velocity and turbulence intensity on a constant airflow rate at y = 0,1 m

Length of the room, m

(12)

11

[8] P. O. Fanger, Dr. – A. K. Melikov, Dr.: Turbulencia és huzat. Épületgépészet, 1989/2.

szám, p. 52-54.

[9] K. Kovanen, O. Seppänen, K. Sirén, A. Majanen: Turbulent air flow measurements in ven- tilated spaces. Environment International, Vol. 15. pp. 621-626, 1989.

[10] H. Hanzawa, A. K. Melikow, P. O. Fanger: Airflow characteristics in the occupied zone of ventilated spaces. ASHRAE Trans., Vol. 93, Part 1, 1987, pp. 524-539.

[11] W.K. Chow, L.T. Wong, W.Y. Fung: Field measurement of the air flow characteristics of big mechanically ventilated spaces, Building and Environment 31 (6) (1996) 541–550.

[12] Magyar Tamás: Qualification of the occupied zones of different types of air supply sys- tems on the basis of measurements. Periodica Polytechnica vol. 44, No. 2, pp. 217-227 (2000).

[13] Yuemei Wang, Zhiwei Lian, Peter Broede, Li Lan: A time-dependent model evaluating draft in indoor environment. Energy and Buildings, 49 (2012) pp. 466-470.

[14] F.C. Houghten, C. Gutberlet, E. Witkowski: Draft temperatures and velocities in relation to skin temperature and feeling of warmth, ASHRAE Transactions 44 (1938) 289–308.

[15] Guangyu Cao, Claudia Kandzia, Dirk Müller, Jorma Heikkinen, Risto Kosonen, Mika Ruponen: Experimental study of the effect of turbulence intensities on the maximum velocity decay of an attached plane jet. Energy and Buildings 65 (2013) pp. 127-136.

[16] Yuemei Wang, Zhiwei Lian, Li Lan: The effect of turbulence intensity on local skin tem- perature and subjective responses to draft. Energy and Buildings 43 (2011) pp. 2678-2683.

[17] Hsin Yu, Chung-Min Liao, Huang-Min Liang: Scale model study of airflow performance in a ceiling slot-ventilated enclosure: isothermal condition. Building and Environment 38 (2003), pp. 1271 – 1279.

[18] Jean Moureh, Denis Flick: Wall air–jet characteristics and airﬂow patterns within a slot ventilated enclosure. International Journal of Thermal Sciences 42 (2003), p703–711.

[19] H. Koskela, J. Heikkinen, R. Niemelä, T. Hautalampi: Turbulence correction for thermal comfort calculation. Building and Environment 36 (2001) pp. 247-255.

[20] Magyar Tamás: Egy irányban határolt izotermikus levegősugár viselkedése zárt terek- ben. Műszaki doktori értekezés. Budapest, 1979.

[21] Fanger, P. O.: Efficient ventilation for human comfort. International Symposium on Room Air Convection and Ventilation Effectiveness (pp. 29 6-306) . Tokyo: University of Tokyo (1992).

[22] Zhang Lin, T. T. Chow, C. F. Tsang, K. F. Fong, L. S. Chan: CFD study on effect of air supply location on the performance of the displacement ventilation system. Building and En- vironment 40 (2005) pp. 1051-1067.

[23] Magyar Tamás, Goda Róbert.: Laboratory modeling of tangential air supply system.

PERIODICA POLYTECHNICA SER. MECH. ENG. VOL. 44, NO. 2, PP. 207–215 (2000).

[24] Jianhua Fan, Christian Anker Hviid, Honglu Yang: Performance analysis of a new design of office diffuse ceiling ventilation system. Energy and Buildings 59 (2013) pp. 73-81.

[25] Gouhui Gan: Numerical investigation of local thermal discomfort in offices with dis- placement ventilation. Energy and Buildings 23 (1995) pp.73-81.

[26] Barna Edit: A sugárzási hőmérséklet aszimmetria és a meleg padló együttes hatása a hőérzetre. PhD értekezés, Budapest 2012. Budapesti Műszaki és Gazdaságtudományi Egye- tem.

[27] Magyar Zoltán: Termikus műember alkalmazási lehetőségei hőkomfort vizsgálatoknál.

Doktori értekezés, Szent István Egyetem, Gödöllő, 2011.

[28] Tanabe, S.; Arens, Edward A.; Bauman, Fred; Zhang, H.: Evaluating thermal environ- ments by using a thermal manikin with controlled skin surface temperature. ASHRAE Trans- actions 1994, Vol. 100, Part 1.

(13)

12

[29] Nilsson, HO: Comfort climate evaluation with thermal manikin methods and computer simulation models. Dissertation, Department of Civil and Architectural Engineering, Royal Institute of Technology, Sweden. NR 2004:2.

[30] K. W. D. Cheong, W. J. Yu, R. Kosonen, K. W. Tham, S. C. Sekhar: Assessment of ther- mal environment using a thermal manikin in a field environment chamber served by displacement ventilation system. Building and Environment 41 (2006) pp. 1661-1670.

[31] Vad János, Dr.: Advanced flow measurements. University lecture note. Műegyetemi Kiadó, 2008.

[32] Lindab résbefúvó termékkatalógus, 2013. Elérhetőség:

http://itsolution.lindab.com/lindabwebproductsdoc/pdf/documentation/comfort/hu/technical/m tl.pdf

[33] Dr. Gruber József, Dr. Blahó Miklós: Folyadékok mechanikája. Tankönyvkiadó, Budap- est, 1981.

[34] ASHRAE. 1992. ANSI/ASHRAE Standard 55-1992, Thermal Environmental Conditions for Human Occupancy, Atlanta: American Society of Heating, Refrigerating, and Air- conditioning Engineers, Inc., USA.

[35] Goda Róbert, Dr Bánhidi László (szerk.), Modelling air flow around a clothed male by CFD, Clima2005.: Experience the Future of Building Technologies CD, Lausanne, Svájc, 2005.10.09-2005.10.12., 5 page, (2005.)

Standards:

[sz1] MSZ CR 1752:2000 [sz2] ISO 7726:1998 [sz3] ISO 7730:2005 [sz4] MSZ EN 13779:2007 [sz5] MSZ EN 308:2000 [sz6] ISO 5167-1:2003

7. References connected to the propositions

Magyar T, Goda R: Laboratory modelling of tangential air supply system. PERIODICA POLYTECHNICA-MECHANICAL ENGINEERING 44:(2) pp. 207-215. (2000)

Both Balázs, Goda Róbert: Résbefúvó anemosztátok méréses vizsgálata érintőleges légve- zetési rendszer alkalmazása esetén. MAGYAR ÉPÜLETGÉPÉSZET 60:(11) pp. 8-12. (2011) Goda Róbert, Both Balázs: Érintőleges légvezetési rendszerek síksugarainak vizsgálata.

MAGYAR ÉPÜLETGÉPÉSZET 62:(6) pp. 4-7. (2013)

Goda Róbert, Both Balázs, Dr Magyar Tamás: Laboratóriumi kísérletek érintőleges légve- zetési rendszerek síksugaraival. MAGYAR INSTALLATEUR 23:(05) pp. 20-21. (2013) Goda Róbert: Turbulence intensity and air velocity characteristics in a slot ventilated space.

Periodica Polytechnica Mechanical Engineering (elfogadva).

Barna Lajos, Barna Edit, Goda Róbert: Modelling of Thermal Comfort Conditions in Build- ings. In: Siavash H Sohrab, Haris J Catrakis, Nikolai Kobasko (szerk.) New Aspects of Heat Transfer: Thermal Engineering and Environment. Athén: WORLD SCIENTIFIC AND ENGINEERING ACAD AND SOC, 2008. pp. 354-359. ISBN: 978- 960-6766-97-8

Goda Róbert, Dr Bánhidi László (szerk.), Modelling air flow around a clothed male by CFD, Clima2005.: Experience the Future of Building Technologies CD, Lausanne, Svájc, 2005.10.09-2005.10.12., 5 page, (2005.)

(14)

13

Goda Róbert: Measurement and Simulation of Air Velocity in the Test Room with Slot Venti- lation. In: Clima2010: Sustainable Energy Use in Building. Antalya, Törökország, 2010.05.09-2010.05.12. Antalya: Paper R6-TS46-PP03.

In progress:

Goda Róbert: Investigation of Draught Comfort of an Occupied Zone Applying Tangential Air Distribution System. Energy and Buildings (editor review, ENB-D-13-01337R1 ).

Further references:

Goda Róbert: Desinging of 3D Air model with Measurement of Ventilation Room. Miskolc, Magyarország, 1999.08.08-1999.08.14. 430 p., ISBN:963 661 378 8 (1999).

L Bánhidi, E Láng, L Kajtár, E Stevensné Szaday*, R Goda, P Ordódy: Surveyed and/or measured data: Hungarian methods and experience ISIAQ Indoor Air 2005, Beijing, China, ISBN 978-7-89494-830-4

Goda Róbert, A. Adel, Száday Edit, Bánhidi László: Possibility to take into account the joint impact of draught and assymetrical radiation in dimensioning thermal comfort in a hot environment. Temesvár, Románia, 2005. (2005)