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MODELLING OF THE AIRFLOW IN THE PASSENGER COACH

Izabela SARNA

Izabela SARNA

Faculty of Energy and Environmental Engineering, The Silesian University of TechnologyGliwice, Poland
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SARNA, Izabela
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Agnieszka PALMOWSKA

Agnieszka PALMOWSKA

Faculty of Energy and Environmental Engineering, The Silesian University of TechnologyGliwice, Poland
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PALMOWSKA, Agnieszka
  
07 gen 2020
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Categoria dell'articolo: research-article
Pubblicato online: 07 gen 2020
Pagine: 125 - 133
Ricevuto: 07 ago 2019
Accettato: 02 ott 2019
DOI: https://doi.org/10.21307/acee-2019-058
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© 2019 Izabela SARNA et al., published by Sciendo
This work is licensed under the Creative Commons Attribution-NonCommercial-NoDerivatives 4.0 International License.

Figure 1.

The numerical coach model – geometry
The numerical coach model – geometry

Figure 2.

The discretization grid on the side of the exterior partitions of the coach
The discretization grid on the side of the exterior partitions of the coach

Figure 3.

The discretization grid with inflated boundary – the crosssection
The discretization grid with inflated boundary – the crosssection

Figure 4.

a) Localization of diffusers, b) scheme of air distribution in the coach, m ˙ S – mass flow rate of air supply m ˙ S 1 – mass flow rate of air supply by lower air diffusers, m ˙ S 2 – mass flow rate of air supply by window air diffusers, m E ˙ – mass flow rate of air exhaust
a) Localization of diffusers, b) scheme of air distribution in the coach, m ˙ S – mass flow rate of air supply m ˙ S 1 – mass flow rate of air supply by lower air diffusers, m ˙ S 2 – mass flow rate of air supply by window air diffusers, m E ˙ – mass flow rate of air exhaust

Figure 5.

The comparison of distribution of air velocity in the vertical plane XY, Z = 1.804 m: a) case 1, b) case 2
The comparison of distribution of air velocity in the vertical plane XY, Z = 1.804 m: a) case 1, b) case 2

Figure 6.

The comparison of the distribution of air velocity in the vertical plane YZ, X = -11.63 m: a) case 1, b) case 2
The comparison of the distribution of air velocity in the vertical plane YZ, X = -11.63 m: a) case 1, b) case 2

Figure 7.

The comparison of the comfort zone in the vertical plane YZ, X= -9.55 m: a) case 1, b) case 2
The comparison of the comfort zone in the vertical plane YZ, X= -9.55 m: a) case 1, b) case 2

Figure 8.

The comparison of the distribution of air temperature in the vertical plane XY, Z = 1.804 m: a) case 1, b) case 2
The comparison of the distribution of air temperature in the vertical plane XY, Z = 1.804 m: a) case 1, b) case 2

Figure 9.

The comparison of the distribution of air velocity in the vertical plane YZ, X = -9.55 m: a) case 1, b) case 2
The comparison of the distribution of air velocity in the vertical plane YZ, X = -9.55 m: a) case 1, b) case 2

Figure 10.

The comparison of the distribution of air velocity in the vertical plane YZ, X = -11.63 m: a) theoretical distribution, b) numerical distribution for case 1, c) numerical distribution for case 2
The comparison of the distribution of air velocity in the vertical plane YZ, X = -11.63 m: a) theoretical distribution, b) numerical distribution for case 1, c) numerical distribution for case 2

Figure 11.

The comparison of air velocity in monitoring points for case 1 and case 2
The comparison of air velocity in monitoring points for case 1 and case 2

Figure 12.

The comparison of air temperature in monitoring points for case 1 and case 2
The comparison of air temperature in monitoring points for case 1 and case 2

The minimum total volume flow of fresh air for railway vehicles with air conditioning device

Exterior temperature (t em ) Minimum fresh air rate equivalent to +20°C and 50% rel. hum, normal atmospheric pressure
t em < -15°C 10m3/h /passenger
-15°C ≤ t em ≤ -5°C 15m3/h /passenger
-5°C ≤ t em ≤ +26°C 20m3/h /passenger
t em > 26°C 15m3/h /passenger

Boundary condition for case 2

The element of model and kind of boundary conditions Value of case 2
South-east wall; “Wall” with heat transfer coefficient U and sol-a ir temperature U = 1.6 w m 2 · K , t s = 53 ° C
Interior wall; “Wall” Adiabatic wall
North-west wall; “Wall” with heat tran sfer coefficient U and sol- air temperature U = 1.6 w m 2 · K , t s = 36.23 ° C
North-east wall; “Wall” with heat transfer coefficient U and sol-air temperature U = 1.6 w m 2 · K , t s = 36.42 ° C
South-east windows; “Wall” with heat tr ansfer coeffi cient U and sol-a ir temperature U = 1.6 w m 2 · K , t s = 297.5 ° C
North-west windows; “Wall” with heat transfer coeffi cient U and sol-air temperature U = 1.6 w m 2 · K , t s = 64.31 ° C
Roof; “Wall” with heat tr ansfer coefficient U and sol-air temperature U = 1.6 w m 2 · K , t s = 65 ° C
Floorboard; “Wall” wi th heat transfer coefficient U and exterior temperature U = 1.6 w m 2 · K , t s = 35 ° C
Lower diffusers; “Inlet” with mass flow rate of supply air and temperature of ventilation supply air m ˙ S 1 = 0.121 kg / s , t S 1 = 16.27 ° C
Upper diffusers; “Inlet” with mass flow rate of supply air and temperature of ventilation supply air m ˙ S 2 = 0.516 kg / s , t S 2 = 16.94 ° C
Exhaust diffusers; “Outlet” with mass flow rate of exhaust air m ˙ E = 0.032 kg / s

Parameters of outdoor air – winter conditions

Climatic zone Minimal temperature
I -10°C
II -20°C
III -40°C

Boundary conditions for case 1

The element of model and kind of boundary conditions Value of case 1
South-east wall; “Wall” with heat transfer coefficient U and sol-air temperature U = 2 w m 2 · K , t s = 61.8 ° C
Interior wall; “Wall” Adiabatic wall
North-west wall; “Wail” with heat teansfer coefficient U and sol-air temperature U = 2 w m 2 · K , t s = 38.3 ° C
North-east wall; “Wall” with heat transfer coefficient U and sol-air temperature U = 2 w m 2 · K , t s = 38.88 ° C
South-east windows; “Wall” with heat transfer coefficient U and sol-air temperature U = 2 w m 2 · K , t s = 157.99 ° C
North-west windows; “Wall” with drat transfer coefficient U and sol-ars temperature U = 2 w m 2 · K , t s = 48.71 ° C
Roof; “Well” with heat transfer coefficienit U and sol-air temperature U = 1.2 w m 2 · K , t s = 53.1 ° C
Floorboard; “Well” with heat transfer “coefficient U and exterior-temperature U = 1.2 w m 2 · K , t s = 35 ° C
Lower diffusers; “Inlet” with mass flow rale of supply air and temperature of ventilation supply air m ˙ S 1 = 0.121 kg / s , t S 1 = 19.4 ° C
Upper diffusers; "Inlet” with mass flow rate of supply air and temperature of ventilation supply air m ˙ S 2 = 0.516 kg / s , t S 2 = 19.9 ° C
Exhaust diffusers; “Outlet” wish mass flow rate of exhaust air m ˙ E = 0.032 kg / s

Parameters of outdoor air – summer conditions

Climatic zone Maximum temperature, relative humidity, equivalent solar load
I 40°C, 40%, 800W/m2
II 35°C, 50%, 700 W/m2
III 28°C, 45%, 600W/m2
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