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Article

Influence of the Positive Pressure Ventilator Setting Distance in Front of the Doorway on the Effectiveness of Tactical Mechanical Ventilation in a Multistory Building

by
Piotr Kaczmarzyk
1,2,
Łukasz Warguła
1,*,
Piotr Krawiec
1,
Paweł Janik
2,
Rafał Noske
2 and
Wojciech Klapsa
2
1
Institute of Machine Design, Faculty of Mechanical Engineering, Poznań University of Technology, 60-965 Poznań, Poland
2
Scientific and Research Centre for Fire Protection, National Research Institute, 05-420 Józefów, Poland
*
Author to whom correspondence should be addressed.
Appl. Sci. 2023, 13(9), 5536; https://doi.org/10.3390/app13095536
Submission received: 16 March 2023 / Revised: 24 April 2023 / Accepted: 28 April 2023 / Published: 29 April 2023
Browse Figures
Versions Notes

Abstract

:
Proper positioning of the positive pressure ventilator is an important aspect of conducting rescue operations. The purpose of this article was to determine the effect of the parameter of the distance of setting up a mobile fan (distance from 1 to 7 m) on the efficiency of implemented ventilation in a multistory building. The volumetric airflow rate was determined by measuring the flow velocity at 120 measurement points on the surface of the window opening (which served as the measurement plane) of a four-story building. Two positive pressure ventilators were tested (one was a conventional fan and the second a turbo type). The obtained volumetric airflow values ranged from 8591 to 15,656 m3/h, depending on the type of unit and positioning distance, respectively. The analysis performed in the article showed that the general guidelines for the distance of mobile fan positioning that are present in the literature may be inaccurate and outdated.

1. Introduction

The equipment and tools used in rescue operations, depending on the requirements of the country, may be subject to special testing and certification procedures [1]. With regard to mobile fans, for the moment in Poland there are no requirements for testing and verification of important technical and performance characteristics that determine their effectiveness. However, it should be pointed out that these devices are an important tool for the implementation of rescue operations, allowing, for example, to carry out activities related to the evacuation of people from inside the building covered by fire (techniques: positive pressure ventilation, negative pressure ventilation and positive pressure attack) and other, unconventional actions such as support for activities concerning the elimination of fires of free-standing objects [1]. There are many types of mobile fan units on the market. In 2022, Wargula and Kaczmarzyk showed that there are about 60 models of positive pressure ventilators dedicated to rescue operations, with half being electric and the other half driven by an internal combustion engine [2]. Given the nature of the work of such units, it is very important that the parameters that determine the effectiveness of their operation are properly verified. Kaczmarzyk et al. in 2021 [3] showed that the critical parameters that can determine the success of operations are the volumetric flow rate and the area of effective jet distribution (its shape), respectively. Referring to the issue related to the study of volumetric flow rate, various methodologies are used to assess this parameter [4,5,6]. It should also be noted that the manufacturers of these devices themselves have their own proprietary methodologies for assessing flow rates. As shown in the study performed by Kaczmarzyk et al. in 2022 [4], it was demonstrated that the method of measuring volumetric flow rate should reflect the actual conditions of use of such units (free-flow operation). Similar conclusions were also made in 2018 by Fritsche et al., who showed that the volumetric flow rate parameters declared by the manufacturers may vary and be unreliable due to the lack of a unified methodology [7]. Numerous studies presenting experimental research of mobile fans under field conditions are present in the literature. In 2022, Kaczmarzyk et al. [8] determined the flow characteristics of a mobile fan in a fan-building system. During the tests, the team evaluated the effect of selected fan positioning parameters on the achieved volumetric flow rate. As a result of the performed work, the team showed that the ventilation efficiency for the tested fan increased as the distance of positioning the mobile fan increased, but only up to 5 m. The indicated distance was determined as the most favorable distance. Similar tests were performed by Lougheed [9], who evaluated the effect of the distance parameter (1.2, 1.8 and 2.8 m) of a positioning of a mobile fan on its efficiency. In this case, for the fan he had, the greatest efficiency was achieved when the fan was positioned directly at the door opening. Another team of researchers [10] showed that the flow rate increases as the fan is brought closer to the doorway. The team also noted that greater efficiency can be achieved by using more units. In the available literature related to the subject of testing mobile PPV fans in published conditions, it is necessary to mention two reports of the National Institute of Standards and Technology on the evaluation of the effectiveness of PPV in large-volume buildings. In a report, Kerber et al. [11] studied the issues surrounding the use of PPV ventilation in high-rise facilities. An optimal distance range of 1.2 to 1.8 m between the door opening and the fan was found. They also concluded that placing the fans in a V-shape leads to better efficiency than a series configuration. In addition, they stressed that for high buildings, fans located on the ground floor may not be sufficient to achieve positive pressure on the gas exchange path.
In this publication, the issue of determining the impact of setting the distance of mobile fans of various types (turbo and conventional fans) on the volumetric flow rate pumped through four storys of a building has been addressed. A flow resisting curtain (FRC) stand was used for testing [8]. Distribution of the air flow velocity profile was tested at 120 measurement points on the surface of the window opening. In parallel, the pressure value was also recorded at four points (on each floor) inside the building. The performed research will allow updating the procedures for positioning mobile fans for new unit designs that are currently in use in Poland and Europe. In addition, the obtained results will also be used to validate the models of numerical fluid mechanics.

2. Materials and Methods

The tests were performed on commonly used mobile fans, a conventional fan and a turbo fan. Detailed parameters of the positive pressure ventilators used are presented in Table 1.
The flow tests were carried out in a 7-story building, inside which 4 storys (constituting a gas exchange line) were adapted for testing by sealing the remaining storys. Only 4 floors were selected for the tests, in order to maintain a compromise between the measuring range of the generated volume flow rates and at the same time maintaining the configuration reflecting the staircase of a multistory building. The tested cubic capacity (for 4 storys) was 198 m3, respectively. On the fourth story, in a window located on the southeast wall, a FRC test stand for evaluating velocity profiles had been installed, which is the equipment of Scientific and Research Centre for Fire Protection—National Research Institute, Jozefów, Poland [8]. The test stand consisted of the following elements:
  • − A steel body allowing for a tight fit to the window opening;
  • − A special screen wound on a roll made of plastic (intended to change the size of the outlet opening) mounted on steel guides;
  • − A measuring module on which a thermoresistance anemometer was mounted, which moved in a synchronized way on the surface of the measuring plane (communication with the controller was carried out using a radio module);
  • − Guides made of aluminum profiles dedicated to the transport of the measuring module;
  • − A drive (stepper motor), allowing the measurement module to be moved.
The test stand had the ability to evaluate the flow velocity field taking into account the variable size of the outlet opening area, but these tests were performed for the full throttle opening area (1.2 m2).
The test configuration of the stand is shown in Figure 1 and Figure 2.
During the course of the tests, measurements were made:
  • Distribution of air flow velocity profiles on the surface of the outlet opening. The measurement was performed at 120 points located evenly on the surface of the FRC measurement plane. The measurement module was equipped with a TSI 8455 thermoresistive anemometer (with a measurement range of 0.127–50 m/s and an accuracy of 1%) (m/s).
  • Pressure values (using Setra pressure transducers) distributed 1 piece on each of the 4 floors with a measurement range of 0–100 Pa and accuracy of 0.25%.
The acquisition frequency of the flow velocity and pressure parameters was 10 Hz, and the measurement duration corresponded to a value of 30 s. During the tests, the volumetric flow rate was evaluated for varying fan positioning distances from 1 to 7 m. For each test, the rotor angle was set so that the rotor axis was directed as close as possible to the center of the doorway. For fan 1, the angle of inclination was 1, 2, 3 m—17°; 4 m—11° and 5, 6, 7 m—6°, respectively. Fan 2 was positioned as follows 1, 2, 3 m—18°; 4 m—12° and 5, 6, 7 m—6°. The volumetric flow rate Q was calculated according to the following relationships [12] (1):
Q = V · S ,   [ m 3 h = m h · m 2 ]
where:
  • V—the average value of the air flow velocity generated by the positive pressure ventilator (m/s);
  • S—measuring surface (measuring plane) of the door opening (m2).
The data in Table A1 and Table A2 were used to calculate the flow rate. Referring to the analysis of measurement error, the arithmetic mean was taken as the estimator of the desired value, and the standard deviation of the arithmetic mean was taken as the error of the estimator. Whereas the main test results provided average values of the air flow rates from 120 trials (N = 120), for which confidence intervals were determined at a confidence level of 95% (p = 0.05). Significant statistical differences were analyzed using Student’s t-test. The tests were performed between August and September. Environmental conditions were monitored during the tests. The tests were performed at a temperature of 21 ± 5 °C and humidity of 50 ± 10%. Research was carried out on days when wind speed was ≤0.2 m/s.

3. Results and Discussion

The results of the tests of the characteristics of the air velocity profiles on the surface of the discharge opening, depending on the positioning distance of the positive pressure ventilator, are shown in Figure 3, Figure 4, Figure 5 and Figure 6 for fan 1 and Figure 7, Figure 8, Figure 9 and Figure 10 for fan 2. Due to the large quantity of data, information on measurement accuracy was not marked on the data, and for this reason, Table A1 and Table A2 with the results of average airflow velocities and measurement errors on the surface of the outlet opening are also included in the Appendix A. Table A3 indicates the average volumetric airflow rate values that were obtained for each setting position—for both positive pressure ventilators, whereas Table A4 and Table A5 also indicate the average pressures that were recorded on each floor (I–IV), taking into account variable positioning distances (1–7 m). It can be seen that the highest velocity of air flow through the door opening was in the central and lower part of the door opening.
The effect of the distance of fan positioning on the flow parameters—volumetric flow rate and static pressure value—is shown in Figure 11 and Figure 12. The presented flow characteristics were made on the basis of the data in Table A1, Table A2, Table A3, Table A4 and Table A5. Analyzing the obtained test results, it should be pointed out that fan No. 1 achieved the highest efficiency when it was located at a distance of 1 m from the door opening. With these positioning parameters, the fan pumped 14,020 m3/h. The lowest efficiency of this unit was recorded for a distance of 7 m and was 8591 m3/h.
Describing fan No. 2, it should be noted that in this case the highest efficiency was obtained for a positioning distance corresponding to 5 m. In this area, the fan pumped 15,656 m3/h. On the other hand, the smallest efficiency was obtained for 1 m of positioning distance of the unit (10,365 m3/h).
Lambert and Merci (2014) studied similar ventilators used in rescue operations. In this case, for the fans used by them, the manufacturer (based on AMCA research) declared a flow of 30,800 and 30,000 m3/h, respectively, for a fan with a combustion engine and for a fan with an electric drive [10].
Describing the obtained values of the volumetric flow rate during the field tests (fan No. 1—14,020 m3/h and fan No. 2—15,656 m3/h), it is noted that they are much lower than those declared by the manufacturers, respectively 30,000 and 31,799 m3/h. The above relationship results from the fact that the flow parameters indicated by the manufacturers were obtained on a standardized test stand, based on the procedure according to ANSI/AMCA 240-15 [6]. In this case, it should be noted that the capabilities of the test stand (the presence of an auxiliary fan) allowed forcing flows and adjusting resistances inside the ventilated volume. Such functionality makes it possible to test a wider fragment of the flow characteristics generated by the tested fan, even in negative pressure conditions, where the pumped stream is additionally sucked into the test stand, which makes it possible to obtain high flows in the absence of overpressure inside the test volume. This condition applies to an unrealistic case of negligible pressure losses in the building. This assumption is particularly inaccurate for complex channel geometries like those of multistory staircases.
The test configuration built with a gas exchange track consisting of four floors made it possible to assess the efficiency of mobile fans’ operation, taking into account the obstacles present in nominal operating conditions, where for each volumetric flow pumped through the volume, there is a back pressure caused by flow resistance. For most flow configurations, the back pressure is proportional to the square of the volumetric flow rate. The lack of an auxiliary fan in the configuration of the field tests made it possible to determine only a fragment of the characteristics (in this case roughly half); hence, the differences between the streams measured at the test facility and at the AMCA 240-15 stand.
Referring to the average pressure values obtained for both units, it should be noted that fan No. 1 generated the highest pressure in the ventilated volume of 20.2 Pa when it was set at a distance of 1 m, while the lowest—4.6 Pa—was at a distance of 7 m. In turn, fan No. 2, at a distance of 1 m, achieved the lowest pressure—8.2 Pa, while at a distance of 5 m, it managed to generate the highest value of pressure inside the ventilated volume—26.0 Pa.
According to the principles of open flow jets theory [13], a fan operating in free flow generates all its work in the form of jet kinetic energy. Mobile fans working in a free flow form a pumping system, the efficiency of which is conditioned by such parameters as: the type (power) of positive pressure ventilator, the characteristics of the generated stream, the accompanying turbulence and the diffuser (door opening—constituting a damming opening).
Bearing in mind the above, it should be noted that the described parameters, with the exception of the damming hole, did not change for the determined positioning conditions of both tested units. With regard to the opening, it is indicated that it may have a different size, depending on the purpose of the object. However, it should be noted that the opening in the tested object had standard dimensions (2.03 × 0.9), which correspond to the size of most door openings in multi-family, office and public buildings.
In this case, it should be noted that the highest values of pressures and flow rates were obtained for the same positioning conditions, respectively fan No. 1—1 m and fan No. 2—5 m. Taking into account the obtained correlation, it should be noted that in the case of using the tested fans in other facilities (with variable room configurations and similar opening sizes), it should be assumed that the determined optimal positioning parameters would not differ significantly.
In 2022, Kaczmarzyk et al. [8] studied the effect of the angle of inclination of a mobile fan on the size of the pumped air stream and obtained a flow rate of 2471 to 17,997 m3/h and pressures of 40.1 and 32.4 Pa, respectively. Complementing the analysis of the specificity of the operation of both positive pressure ventilators, it should be noted that ventilator 1, along with increasing the distance from the door opening, worked less efficiently. The indicated relationship can be attributed to the specificity of operation of conventional fans—which generate a stream in the shape of a cone. As the distance increases, the proportion of airflow that enters the ventilated object is reduced. This phenomenon was described by Kaczmarzyk et al. (2021) [3]. Describing the specifics of the operation of fan No. 2, it should be pointed out that it was a ventilator which, due to the presence of specially formed blades, in combination with a special housing (which is also a kind of flow straightener) generated a stream shaped like a cylinder. In this case, a stream of a cylinder-shaped fan (set at a distance of 5 m) induced additional portions of air taken from the environment. This is a characteristic feature attributed to turbo units [3]. The described phenomena of the positioning of mobile fans and efficiency evaluation have been described in the literature [9,13,14,15,16,17,18].

4. Conclusions

The distance of the position of the positive pressure ventilator from the doorway affects the effectiveness of implementing tactical mechanical ventilation of a building facility. Depending on the distance of mobile fan positioning from the door opening (from 1 to 7 m) and the type of fan impeller (conventional fan (1) and turbo type (2)), the obtained values of volumetric air flow were from 8591 to 15,656 m3/h, respectively. Fans with a conventional impeller (1) had the highest building ventilation efficiency at the closest tested distance from the doorway (1 m). With these positioning parameters, the fan pumped 14,020 m3/h. As the distance from the door opening increased, the value decreased up to 8591 m3/h (at a distance of 7 m). On the other hand, the fan with a turbo impeller achieved the highest efficiency for a distance of 5 m from the door opening. In this area, the fan pumped 15,656 m3/h. At distances greater and less than 5 m, the value of volumetric airflow decreased. Due to the shape of the generated airflow of fan 1 (conical) and fan 2 (cylindrical), their effective positioning in relation to the door opening can vary by up to about 5 m. The performed tests demonstrate the need to update procedures for positioning mobile fans during rescue operations and to develop methods to support optimal positioning. The detailed results of the tests can be used to validate numerical models for ventilation of Multistory buildings.

Author Contributions

Conceptualization, P.K. (Piotr Kaczmarzyk), Ł.W. and P.J.; methodology, P.K. (Piotr Kaczmarzyk), R.N., W.K.; software, P.K. (Piotr Kaczmarzyk), R.N.; validation, P.K. (Piotr Kaczmarzyk), P.J. and W.K.; formal analysis, P.K. (Piotr Kaczmarzyk); investigation, P.K. (Piotr Kaczmarzyk) and P.K. (Piotr Krawiec); resources, P.K. (Piotr Kaczmarzyk); data curation, P.K. (Piotr Kaczmarzyk), R.N., W.K., P.J.; writing—original draft preparation, P.K. (Piotr Kaczmarzyk), Ł.W. and P.K. (Piotr Krawiec); writing—review and editing, P.K. (Piotr Kaczmarzyk), Ł.W.; visualization, P.K. (Piotr Kaczmarzyk); supervision, P.K. (Piotr Kaczmarzyk); project administration, P.K. (Piotr Kaczmarzyk); funding acquisition, P.K. (Piotr Kaczmarzyk). All authors have read and agreed to the published version of the manuscript.

Funding

The research presented in the article was carried out as part of the Ministry of Education and Science program “Implementation Doctorate” executed in 2020–2024 (agreement no. DWD/4/22/2020).

Institutional Review Board Statement

Not applicable.

Informed Consent Statement

Not applicable.

Data Availability Statement

Not applicable.

Conflicts of Interest

The authors declare no conflict of interest.

Appendix A

Table
Table A1. Air flow velocity, measured at 120 points on the surface of the window opening (for 7 positioning distances)—positive pressure ventilator 1, where: x—position of the measurement point with respect to the x-axis, y—position of the measurement point with respect to the y-axis, AVG—arithmetic mean of the air flow velocity, SD—standard deviation taken as measurement error.
Table A1. Air flow velocity, measured at 120 points on the surface of the window opening (for 7 positioning distances)—positive pressure ventilator 1, where: x—position of the measurement point with respect to the x-axis, y—position of the measurement point with respect to the y-axis, AVG—arithmetic mean of the air flow velocity, SD—standard deviation taken as measurement error.
Distance of the Fan from the Door Opening 1 m
The Inclination Angle of the Fan Impeller Relative to the Ground 18°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)503.230.142.410.411.930.242.350.272.740.292.870.212.820.302.880.41
1502.390.152.820.072.890.102.790.032.800.062.770.092.660.152.320.16
2502.120.252.680.072.600.062.600.062.650.122.780.072.600.102.250.11
3502.160.212.720.062.580.082.470.102.220.050.980.070.910.180.890.53
4502.160.202.650.062.530.072.390.052.490.172.390.122.340.101.270.43
5502.000.262.670.062.600.092.430.102.430.082.430.101.990.151.440.40
6502.040.182.760.032.520.062.460.132.440.062.300.092.080.071.480.30
7501.910.172.750.042.740.162.530.092.450.102.370.072.070.171.580.38
8501.690.112.670.052.740.112.610.122.440.082.440.082.060.311.760.20
9501.670.252.730.052.820.112.950.102.900.182.790.182.500.082.000.16
10501.670.142.680.082.770.172.810.133.060.122.790.162.350.082.000.16
11501.620.162.600.092.670.092.680.132.680.112.740.122.480.112.110.16
12501.690.192.680.112.660.082.710.052.590.082.550.112.550.102.090.10
13501.720.162.580.092.730.092.640.072.700.082.620.112.400.152.230.15
14501.990.222.650.062.480.162.680.162.750.082.470.202.240.202.270.12
Distance of the fan from the door opening 2 m
The inclination angle of the fan impeller relative to the ground 18°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)503.740.093.540.173.020.512.840.323.050.403.610.373.450.263.290.43
1502.790.163.330.173.500.133.380.283.300.223.300.103.330.182.810.15
2502.640.173.130.103.080.063.080.093.050.053.140.183.100.112.550.23
3502.580.323.210.103.060.082.910.073.090.153.110.092.930.082.480.32
4502.830.203.200.092.870.082.820.082.660.102.780.132.860.122.070.30
5502.720.143.020.102.940.062.760.082.690.142.680.162.590.131.780.30
6502.490.193.020.042.970.122.800.082.730.092.800.172.360.131.700.33
7502.560.163.130.083.040.113.150.122.950.102.820.082.610.122.080.25
8502.110.253.180.093.110.093.410.283.010.183.000.092.730.102.190.11
9502.230.193.250.083.280.213.700.203.480.183.220.212.860.212.310.14
10502.220.133.230.163.220.093.500.273.540.163.160.112.850.102.380.17
11502.190.173.590.133.210.103.390.193.150.092.950.082.780.182.460.14
12501.740.203.030.093.240.153.410.263.140.073.200.142.750.102.610.14
13502.070.323.340.113.170.153.110.123.260.133.080.122.790.122.440.10
14502.60.133.010.083.230.213.240.073.230.212.850.503.050.322.910.25
Distance of the fan from the door opening 3 m
The inclination angle of the fan impeller relative to the ground 18°
Stage 5/5x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)503.730.344.180.153.110.343.530.373.790.304.390.274.000.393.640.58
1502.220.863.780.333.660.113.040.273.670.123.600.113.670.193.050.32
2502.520.613.290.293.540.063.420.103.410.193.690.123.690.333.110.16
3502.330.273.640.233.310.153.260.153.350.073.630.173.530.122.740.42
4502.480.343.230.083.230.133.140.123.320.203.280.133.190.163.350.11
5502.010.312.630.392.830.333.110.143.460.173.620.233.040.353.080.14
6502.030.363.030.373.320.183.240.273.080.363.290.153.310.162.980.26
7502.290.313.470.163.480.203.330.083.290.193.360.082.850.162.540.14
8502.240.263.300.183.630.183.460.253.410.163.340.142.990.242.570.17
9501.760.483.260.243.390.203.420.273.400.123.480.153.010.112.670.17
10501.400.273.100.203.330.553.540.183.740.283.570.142.810.192.900.14
11502.100.193.470.234.020.503.760.363.550.183.510.223.360.192.660.30
12501.840.343.260.193.340.093.370.173.330.123.640.163.220.222.770.30
13501.820.373.320.143.200.123.170.233.670.243.010.273.260.213.190.24
14502.460.243.100.223.550.123.740.323.420.323.350.343.160.282.890.22
Distance of the Fan from the door opening 4 m
The inclination angle of the fan impeller relative to the ground 12°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)504.590.104.080.524.540.473.990.283.220.614.200.304.520.395.080.19
1503.250.203.900.054.090.084.620.253.870.174.070.094.080.153.310.31
2503.140.333.760.153.480.193.570.153.800.113.950.274.040.123.160.29
3503.380.233.600.163.660.093.560.113.770.263.890.183.750.122.740.18
4503.340.193.600.213.460.043.170.233.510.143.690.253.570.261.810.48
5503.010.393.670.083.280.093.500.143.220.173.380.173.200.171.690.21
6503.060.263.680.243.400.153.350.183.250.093.410.102.990.221.870.42
7502.680.373.630.253.600.123.470.253.680.123.440.082.990.222.850.18
8502.840.253.310.253.890.213.850.294.130.273.590.103.070.092.850.20
9502.720.293.800.233.690.444.210.273.890.543.710.203.010.262.760.12
10501.660.443.790.183.570.244.190.284.140.283.830.242.320.232.110.19
11501.500.503.330.393.460.423.530.363.890.252.430.623.630.173.290.15
12502.060.442.420.563.770.293.200.483.990.363.420.163.510.183.090.22
13502.250.443.630.173.730.113.820.093.780.103.930.173.630.313.360.34
14502.720.303.900.164.200.244.450.133.710.153.430.313.450.633.230.48
Distance of the fan from the door opening 5 m
The inclination angle of the fan impeller relative to the ground 6°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)504.400.074.200.124.220.174.250.284.090.074.130.244.360.284.580.22
1503.700.184.200.054.400.144.230.064.510.124.360.194.370.124.630.14
2503.380.324.060.074.080.103.950.074.090.094.100.184.320.193.050.26
3502.950.433.910.113.790.083.810.163.780.143.920.173.920.082.680.35
4502.310.543.090.133.200.153.550.083.500.103.300.243.210.262.370.20
5502.290.633.650.123.420.083.360.133.540.103.270.133.050.262.400.26
6503.470.213.780.093.830.133.590.063.630.133.310.113.240.172.520.26
7503.130.243.830.083.790.184.280.343.610.103.470.093.240.172.430.24
8502.480.643.500.314.000.264.090.253.850.093.870.163.480.232.880.16
9502.810.194.040.104.220.114.220.374.320.144.090.163.180.232.390.25
10502.590.334.310.224.300.134.220.164.330.204.080.13.530.213.220.13
11502.620.274.290.094.150.164.000.214.160.164.390.153.530.253.260.20
12502.410.333.850.173.930.123.870.123.910.123.690.122.380.393.470.18
13502.380.193.880.093.850.103.790.183.400.203.410.573.040.303.110.45
14502.980.113.720.183.980.113.910.203.940.323.540.363.660.363.350.11
Distance of the fan from the door opening 6 m
The inclination angle of the fan impeller relative to the ground 6°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)504.460.174.790.214.140.304.060.233.580.294.200.194.170.514.340.46
1503.100.343.950.094.000.084.180.094.060.094.050.124.130.133.510.11
2502.980.193.740.083.690.073.740.083.990.084.030.093.910.123.090.24
3503.020.253.700.103.710.073.470.113.500.133.730.213.820.092.670.38
4502.920.133.720.113.460.083.390.143.270.143.360.163.280.202.020.31
5503.040.173.670.093.510.093.320.143.220.143.230.153.010.141.750.49
6502.930.253.680.113.680.183.570.143.260.093.340.112.840.222.000.37
7502.740.203.690.123.630.093.460.143.380.093.380.113.240.212.690.14
8502.420.203.790.103.940.064.020.133.730.113.520.233.370.112.820.20
9502.630.383.870.123.950.154.270.244.070.213.890.113.330.232.620.20
10502.420.303.740.103.530.163.900.264.300.283.870.113.440.092.670.15
11502.120.243.690.143.770.103.780.133.690.093.610.123.540.103.120.15
12502.720.253.700.093.640.083.710.193.500.103.590.123.460.193.150.18
13502.870.323.740.103.580.123.690.053.750.113.740.063.560.073.270.22
14502.880.213.380.063.350.133.530.273.450.113.410.123.580.363.180.21
Distance of the fan from the door opening 7 m
The inclination angle of the fan impeller relative to the ground 6°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)504.220.094.340.124.050.203.860.233.070.243.960.173.930.324.310.49
1503.130.193.730.083.750.113.790.093.840.093.720.163.680.153.180.16
2502.870.193.450.113.390.113.420.073.500.123.740.153.600.132.560.23
3502.920.173.320.083.230.093.270.113.330.093.390.173.330.142.320.22
4502.770.253.320.083.160.093.010.163.150.163.040.273.170.211.740.21
5502.850.213.300.133.200.083.070.093.050.102.950.162.660.161.450.37
6502.710.283.340.103.220.073.250.123.000.072.870.122.660.202.130.24
7502.960.213.340.103.310.153.150.203.180.182.980.152.850.132.310.24
8502.580.263.440.113.530.153.550.133.270.183.200.112.900.172.220.27
9502.460.263.290.183.400.393.440.263.520.153.160.202.820.212.400.15
10502.250.333.290.123.390.113.500.213.850.233.280.112.970.132.590.14
11502.000.203.320.153.390.173.480.093.390.153.270.123.070.122.580.11
12501.920.213.260.073.360.103.230.103.240.163.350.093.200.092.700.12
13502.130.203.210.133.280.073.230.123.250.113.160.123.130.072.780.21
14503.210.163.180.173.330.173.180.33.050.263.350.213.090.192.540.25
Table
Table A2. Air flow velocity, measured at 120 points on the surface of the window opening (for 7 positioning distances)—positive pressure ventilator 2, where: x—location of the measurement point relative to the x-axis, y—location of the measurement point relative to the y-axis, AVG—arithmetic mean of the flow rate, SD—standard deviation taken as the measurement error.
Table A2. Air flow velocity, measured at 120 points on the surface of the window opening (for 7 positioning distances)—positive pressure ventilator 2, where: x—location of the measurement point relative to the x-axis, y—location of the measurement point relative to the y-axis, AVG—arithmetic mean of the flow rate, SD—standard deviation taken as the measurement error.
Distance of the Fan from the Door Opening 1 m
The Inclination Angle of the Fan Impeller Relative to the Ground 18°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)503.230.142.410.411.930.242.350.272.740.292.870.212.820.302.880.41
1502.390.152.820.072.890.102.790.032.800.062.770.092.660.152.320.16
2502.120.252.680.072.600.062.600.062.650.122.780.072.600.102.250.11
3502.160.212.720.062.580.082.470.102.220.050.980.070.910.180.890.53
4502.160.202.650.062.530.072.390.052.490.172.390.122.340.101.270.43
5502.0.262.670.062.600.092.430.102.430.082.430.101.990.151.440.40
6502.040.182.760.032.520.062.460.132.440.062.300.092.080.071.480.30
7501.910.172.750.042.740.162.530.092.450.102.370.072.070.171.580.38
8501.690.112.670.052.740.112.610.122.440.082.440.082.060.311.760.20
9501.670.252.730.052.820.112.950.102.900.182.790.182.500.082.000.16
10501.670.142.680.082.770.172.810.133.060.122.790.162.350.082.000.16
11501.620.162.600.092.670.092.680.132.680.112.740.122.480.112.110.16
12501.690.192.680.112.660.082.710.052.590.082.550.112.550.102.090.10
13501.720.162.580.092.730.092.640.072.700.082.620.112.400.152.230.15
14501.990.222.650.062.480.162.680.162.750.082.470.202.240.202.270.12
Distance of the fan from the door opening 2 m
The inclination angle of the fan impeller relative to the ground 18°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)503.740.093.540.173.020.512.840.323.050.403.610.373.450.263.290.43
1502.790.163.330.173.500.133.380.283.300.223.300.103.330.182.810.15
2502.640.173.130.103.080.063.080.093.050.053.140.183.100.112.550.23
3502.580.323.210.103.060.082.910.073.090.153.110.092.930.082.480.32
4502.830.203.200.092.870.082.820.082.660.102.780.132.860.122.070.30
5502.720.143.020.102.940.062.760.082.690.142.680.162.590.131.780.30
6502.490.193.020.042.970.122.800.082.730.092.800.172.360.131.700.33
7502.560.163.130.083.040.113.150.122.950.102.820.082.610.122.080.25
8502.110.253.180.093.110.093.410.283.010.183.000.092.730.102.190.11
9502.230.193.250.083.280.213.700.203.480.183.220.212.860.212.310.14
10502.220.133.230.163.220.093.500.273.540.163.160.112.850.102.380.17
11502.190.173.590.133.210.103.390.193.150.092.950.082.780.182.460.14
12501.740.203.030.093.240.153.410.263.140.073.200.142.750.102.610.14
13502.070.323.340.113.170.153.110.123.260.133.080.122.790.122.440.10
14502.60.133.010.083.230.213.240.073.230.212.850.503.050.322.910.25
Distance of the fan from the door opening 3 m
The inclination angle of the fan impeller relative to the ground 18°
Stage 5/5x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)503.730.344.180.153.110.343.530.373.790.304.390.274.000.393.640.58
1502.220.863.780.333.660.113.040.273.670.123.600.113.670.193.050.32
2502.520.613.290.293.540.063.420.103.410.193.690.123.690.333.110.16
3502.330.273.640.233.310.153.260.153.350.073.630.173.530.122.740.42
4502.480.343.230.083.230.133.140.123.320.203.280.133.190.163.350.11
5502.010.312.630.392.830.333.110.143.460.173.620.233.040.353.080.14
6502.030.363.030.373.320.183.240.273.080.363.290.153.310.162.980.26
7502.290.313.470.163.480.203.330.083.290.193.360.082.850.162.540.14
8502.240.263.300.183.630.183.460.253.410.163.340.142.990.242.570.17
9501.760.483.260.243.390.203.420.273.400.123.480.153.010.112.670.17
10501.400.273.100.203.330.553.540.183.740.283.570.142.810.192.900.14
11502.100.193.470.234.020.503.760.363.550.183.510.223.360.192.660.30
12501.840.343.260.193.340.093.370.173.330.123.640.163.220.222.770.30
13501.820.373.320.143.200.123.170.233.670.243.010.273.260.213.190.24
14502.460.243.100.223.550.123.740.323.420.323.350.343.160.282.890.22
Distance of the fan from the door opening 4 m
The inclination angle of the fan impeller relative to the ground 12°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)504.590.104.080.524.540.473.990.283.220.614.200.304.520.395.080.19
1503.250.203.900.054.090.084.620.253.870.174.070.094.080.153.310.31
2503.140.333.760.153.480.193.570.153.800.113.950.274.040.123.160.29
3503.380.233.600.163.660.093.560.113.770.263.890.183.750.122.740.18
4503.340.193.600.213.460.043.170.233.510.143.690.253.570.261.810.48
5503.010.393.670.083.280.093.500.143.220.173.380.173.200.171.690.21
6503.060.263.680.243.400.153.350.183.250.093.410.102.990.221.870.42
7502.680.373.630.253.600.123.470.253.680.123.440.082.990.222.850.18
8502.840.253.310.253.890.213.850.294.130.273.590.103.070.092.850.20
9502.720.293.800.233.690.444.210.273.890.543.710.203.010.262.760.12
10501.660.443.790.183.570.244.190.284.140.283.830.242.320.232.110.19
11501.500.503.330.393.460.423.530.363.890.252.430.623.630.173.290.15
12502.060.442.420.563.770.293.200.483.990.363.420.163.510.183.090.22
13502.250.443.630.173.730.113.820.093.780.103.930.173.630.313.360.34
14502.720.303.900.164.200.244.450.133.710.153.430.313.450.633.230.48
Distance of the fan from the door opening 5 m
The inclination angle of the fan impeller relative to the ground 6°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)504.400.074.200.124.220.174.250.284.090.074.130.244.360.284.580.22
1503.700.184.200.054.400.144.230.064.510.124.360.194.370.124.630.14
2503.380.324.060.074.080.103.950.074.090.094.100.184.320.193.050.26
3502.950.433.910.113.790.083.810.163.780.143.920.173.920.082.680.35
4502.310.543.090.133.200.153.550.083.500.103.300.243.210.262.370.20
5502.290.633.650.123.420.083.360.133.540.103.270.133.050.262.400.26
6503.470.213.780.093.830.133.590.063.630.133.310.113.240.172.520.26
7503.130.243.830.083.790.184.280.343.610.103.470.093.240.172.430.24
8502.480.643.500.314.000.264.090.253.850.093.870.163.480.232.880.16
9502.810.194.040.104.220.114.220.374.320.144.090.163.180.232.390.25
10502.590.334.310.224.300.134.220.164.330.204.080.13.530.213.220.13
11502.620.274.290.094.150.164.000.214.160.164.390.153.530.253.260.20
12502.410.333.850.173.930.123.870.123.910.123.690.122.380.393.470.18
13502.380.193.880.093.850.103.790.183.400.203.410.573.040.303.110.45
14502.980.113.720.183.980.113.910.203.940.323.540.363.660.363.350.11
Distance of the fan from the door opening 6 m
The inclination angle of the fan impeller relative to the ground 6°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)504.460.174.790.214.140.304.060.233.580.294.200.194.170.514.340.46
1503.100.343.950.094.000.084.180.094.060.094.050.124.130.133.510.11
2502.980.193.740.083.690.073.740.083.990.084.030.093.910.123.090.24
3503.020.253.700.103.710.073.470.113.500.133.730.213.820.092.670.38
4502.920.133.720.113.460.083.390.143.270.143.360.163.280.202.020.31
5503.040.173.670.093.510.093.320.143.220.143.230.153.010.141.750.49
6502.930.253.680.113.680.183.570.143.260.093.340.112.840.222.000.37
7502.740.203.690.123.630.093.460.143.380.093.380.113.240.212.690.14
8502.420.203.790.103.940.064.020.133.730.113.520.233.370.112.820.20
9502.630.383.870.123.950.154.270.244.070.213.890.113.330.232.620.20
10502.420.303.740.103.530.163.900.264.300.283.870.113.440.092.670.15
11502.120.243.690.143.770.103.780.133.690.093.610.123.540.103.120.15
12502.720.253.700.093.640.083.710.193.500.103.590.123.460.193.150.18
13502.870.323.740.103.580.123.690.053.750.113.740.063.560.073.270.22
14502.880.213.380.063.350.133.530.273.450.113.410.123.580.363.180.21
Distance of the fan from the door opening 7 m
The inclination angle of the fan impeller relative to the ground 6°
Stage 5/5
Full open		x (mm)
50150250350450550650750
AVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSDAVGSD
y (mm)504.220.094.340.124.050.203.860.233.070.243.960.173.930.324.310.49
1503.130.193.730.083.750.113.790.093.840.093.720.163.680.153.180.16
2502.870.193.450.113.390.113.420.073.500.123.740.153.600.132.560.23
3502.920.173.320.083.230.093.270.113.330.093.390.173.330.142.320.22
4502.770.253.320.083.160.093.010.163.150.163.040.273.170.211.740.21
5502.850.213.300.133.200.083.070.093.050.102.950.162.660.161.450.37
6502.710.283.340.103.220.073.250.123.000.072.870.122.660.202.130.24
7502.960.213.340.103.310.153.150.203.180.182.980.152.850.132.310.24
8502.580.263.440.113.530.153.550.133.270.183.200.112.900.172.220.27
9502.460.263.290.183.400.393.440.263.520.153.160.202.820.212.400.15
10502.250.333.290.123.390.113.500.213.850.233.280.112.970.132.590.14
11502.000.203.320.153.390.173.480.093.390.153.270.123.070.122.580.11
12501.920.213.260.073.360.103.230.103.240.163.350.093.200.092.700.12
13502.130.203.210.133.280.073.230.123.250.113.160.123.130.072.780.21
14503.210.163.180.173.330.173.180.33.050.263.350.213.090.192.540.25
Table
Table A3. The influence of the distance of the fan position from the door opening and the angle of the impeller on the volumetric airflow rate for ventilators 1 and 2 where AVG—arithmetic mean flow rate (m3/h), and confidence interval is (p = 0.05).
Table A3. The influence of the distance of the fan position from the door opening and the angle of the impeller on the volumetric airflow rate for ventilators 1 and 2 where AVG—arithmetic mean flow rate (m3/h), and confidence interval is (p = 0.05).
Positioning Parameters in Front of the Door Opening and Flow Rate Obtained—Ventilator 1Positioning Parameters in Front of the Door Opening and Flow Rate Obtained—Ventilator 2
Distance (m)Inclination Angle (°)AVGp = 0.05Distance (m)Inclination Angle (°)AVGp = 0.05
11714,02058511810,365504
21712,24764221812,643585
31710,82652331813,771843
41110,57656141214,895880
5610,3914715615,656698
6698224636615,011598
7685916037613,586591
Table
Table A4. The influence of the distance of the position of ventilator 1 from the door opening and the angle of the impeller on the values of static pressure (Pa) on floor I–IV inside the staircase, where: AVG—arithmetic mean of the flow rate, SD—standard deviation taken as measurement error.
Table A4. The influence of the distance of the position of ventilator 1 from the door opening and the angle of the impeller on the values of static pressure (Pa) on floor I–IV inside the staircase, where: AVG—arithmetic mean of the flow rate, SD—standard deviation taken as measurement error.
Distance (m) and Inclination Angle (°)Story
IIIIIIIV
AVGSDAVGSDAVGSDAVGSD
1 m, 17°28.152.2824.151.8017.531.6510.781.63
2 m, 17°22.812.3919.202.1114.281.929.191.98
3 m, 17°17.442.0814.431.6610.701.316.660.99
4 m, 11°13.011.8810.521.448.091.155.421.32
5 m, 6°16.172.0513.301.679.871.246.070.79
6 m, 6°13.062.6710.472.387.732.034.871.77
7 m, 6°7.802.455.562.163.511.781.471.18
Table
Table A5. The influence of the distance of the position of ventilator 2 from the door opening and the angle of the impeller on the values of static pressure (Pa) on floor I–IV inside the staircase, where: AVG—arithmetic mean of the flow rate, SD—standard deviation taken as measurement error.
Table A5. The influence of the distance of the position of ventilator 2 from the door opening and the angle of the impeller on the values of static pressure (Pa) on floor I–IV inside the staircase, where: AVG—arithmetic mean of the flow rate, SD—standard deviation taken as measurement error.
Distance (m) and Inclination Angle (°)Story
IIIIIIIV
AVGSDAVGSDAVGSDAVGSD
1 m, 18°12.802.1810.761.436.751.092.650.78
2 m, 18°17.532.6416.292.2910.911.965.141.59
3 m, 18°17.616.3516.355.7011.304.255.842.84
4 m, 12°28.775.4323.984.4916.043.777.813.16
5 m, 6°37.773.5131.372.8422.272.1912.731.46
6 m, 6°33.033.3627.762.7219.772.0911.421.40
7 m, 6°28.483.2723.802.5917.221.9310.061.24

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Figure 1. Configuration of the test system, where: 1—fan, 2—window opening (measuring plane with 120 points division), 3—measuring probe (TSI thermo anemometer), 4—test stand body and roller shutter modifying the size of the outlet opening, 5—guides for transporting the measuring probe.
Figure 1. Configuration of the test system, where: 1—fan, 2—window opening (measuring plane with 120 points division), 3—measuring probe (TSI thermo anemometer), 4—test stand body and roller shutter modifying the size of the outlet opening, 5—guides for transporting the measuring probe.
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Figure 2. Scheme of the tested system (a) 3D model, (b) schematic diagram, where: 1—PPV in the position of 7 m from the inlet, 2—PPV in the position 1 m from the inlet, 3—outlet from the building with the flow measurement system, 4—inlet to the building, P—pressure sensors on the story.
Figure 2. Scheme of the tested system (a) 3D model, (b) schematic diagram, where: 1—PPV in the position of 7 m from the inlet, 2—PPV in the position 1 m from the inlet, 3—outlet from the building with the flow measurement system, 4—inlet to the building, P—pressure sensors on the story.
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Figure 3. Air velocity in the outlet for positive pressure ventilator 1, positioned in front of the surface of the door opening, at a distance of (a) 1 m and the impeller axis angle to the ground of 17°, (b) 2 m impeller axis angle to the ground of 17°.
Figure 3. Air velocity in the outlet for positive pressure ventilator 1, positioned in front of the surface of the door opening, at a distance of (a) 1 m and the impeller axis angle to the ground of 17°, (b) 2 m impeller axis angle to the ground of 17°.
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Figure 4. Air velocity in the outlet for positive pressure ventilator 1, positioned in front of the surface of the door opening, at distances: (a) 3 m and rotor axis angle to the ground 17°, (b) 4 m rotor axis angle to the ground 11°.
Figure 4. Air velocity in the outlet for positive pressure ventilator 1, positioned in front of the surface of the door opening, at distances: (a) 3 m and rotor axis angle to the ground 17°, (b) 4 m rotor axis angle to the ground 11°.
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Figure 5. Air velocity in the outlet for positive pressure ventilator 1, positioned in front of the surface of the door opening, at distances: (a) 5 m and rotor axis angle to the ground 6°, (b) 6 m rotor axis angle to the ground 6°.
Figure 5. Air velocity in the outlet for positive pressure ventilator 1, positioned in front of the surface of the door opening, at distances: (a) 5 m and rotor axis angle to the ground 6°, (b) 6 m rotor axis angle to the ground 6°.
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Figure 6. Air velocity in the outlet for positive pressure ventilator 1, positioned in front of the surface of the door opening, at a distance: 7 m and the angle of the impeller axis with respect to the ground 6°.
Figure 6. Air velocity in the outlet for positive pressure ventilator 1, positioned in front of the surface of the door opening, at a distance: 7 m and the angle of the impeller axis with respect to the ground 6°.
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Figure 7. Air velocity in the outlet for positive pressure ventilator 2, positioned in front of the surface of the door opening, at distances: (a) 1 m and rotor axis angle to the ground 18°, (b) 2 m and rotor axis angle to the ground 18°.
Figure 7. Air velocity in the outlet for positive pressure ventilator 2, positioned in front of the surface of the door opening, at distances: (a) 1 m and rotor axis angle to the ground 18°, (b) 2 m and rotor axis angle to the ground 18°.
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Figure 8. Air velocity in the outlet for positive pressure ventilator 2, positioned in front of the surface of the door opening, at distances: (a) 3 m and rotor axis angle to the ground 18°, (b) 4 m and rotor axis angle to the ground 12°.
Figure 8. Air velocity in the outlet for positive pressure ventilator 2, positioned in front of the surface of the door opening, at distances: (a) 3 m and rotor axis angle to the ground 18°, (b) 4 m and rotor axis angle to the ground 12°.
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Figure 9. Air velocity in the outlet for positive pressure ventilator 2, positioned in front of the surface of the door opening, at distances: (a) 5 m and rotor axis angle to the ground 6°, (b) 6 m and rotor axis angle to the ground 6°.
Figure 9. Air velocity in the outlet for positive pressure ventilator 2, positioned in front of the surface of the door opening, at distances: (a) 5 m and rotor axis angle to the ground 6°, (b) 6 m and rotor axis angle to the ground 6°.
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Figure 10. Air velocity in the outlet for positive pressure ventilator 2, positioned in front of the surface of the door opening, at a distance of 7 m and an angle of the impeller axis to the ground of 6°.
Figure 10. Air velocity in the outlet for positive pressure ventilator 2, positioned in front of the surface of the door opening, at a distance of 7 m and an angle of the impeller axis to the ground of 6°.
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Figure 11. Flow characteristics of volumetric air flow and static pressure of mobile fan 1, depending on the distance of location in front of the door opening.
Figure 11. Flow characteristics of volumetric air flow and static pressure of mobile fan 1, depending on the distance of location in front of the door opening.
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Figure 12. Flow characteristics of volumetric air flow and static pressure of mobile fan 2, depending on the distance of location in front of the door opening.
Figure 12. Flow characteristics of volumetric air flow and static pressure of mobile fan 2, depending on the distance of location in front of the door opening.
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Table
Table 1. Characteristics of mobile rescue fans.
Table 1. Characteristics of mobile rescue fans.
Positive pressure ventilator 1
Combustion engineBriggs and Stratton 750
Maximum volumetric flow rate (declared)30,000 m3/h
Maximum power of the engine (at rotational speed 3600 rpm)4.4 kW
Displacement capacity163 cm3
Positive pressure ventilator 2
Combustion engineHonda GX 200
Maximum volumetric flow rate (declared)31,799 m3/h
Maximum power of the engine (at rotational speed 3600 rpm)4.1 kW
Displacement capacity196 cm3
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MDPI and ACS Style

Kaczmarzyk, P.; Warguła, Ł.; Krawiec, P.; Janik, P.; Noske, R.; Klapsa, W. Influence of the Positive Pressure Ventilator Setting Distance in Front of the Doorway on the Effectiveness of Tactical Mechanical Ventilation in a Multistory Building. Appl. Sci. 2023, 13, 5536. https://doi.org/10.3390/app13095536

AMA Style

Kaczmarzyk P, Warguła Ł, Krawiec P, Janik P, Noske R, Klapsa W. Influence of the Positive Pressure Ventilator Setting Distance in Front of the Doorway on the Effectiveness of Tactical Mechanical Ventilation in a Multistory Building. Applied Sciences. 2023; 13(9):5536. https://doi.org/10.3390/app13095536

Chicago/Turabian Style

Kaczmarzyk, Piotr, Łukasz Warguła, Piotr Krawiec, Paweł Janik, Rafał Noske, and Wojciech Klapsa. 2023. "Influence of the Positive Pressure Ventilator Setting Distance in Front of the Doorway on the Effectiveness of Tactical Mechanical Ventilation in a Multistory Building" Applied Sciences 13, no. 9: 5536. https://doi.org/10.3390/app13095536

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