MODELLING OF THE AIRFLOW IN THE PASSENGER COACH

Izabela SARNA; Agnieszka PALMOWSKA

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MODELLING OF THE AIRFLOW IN THE PASSENGER COACH

Izabela SARNA

Agnieszka PALMOWSKA

| 07 gen 2020

Architecture, Civil Engineering, Environment

Volume 12 (2019): Numero 4 (December 2019)

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Article Category: 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

Parole chiave
Airflow, Coach, CFD, Heat exchange, Ventilation

© 2019 Izabela SARNA et al., published by Sciendo

This work is licensed under the Creative Commons Attribution-NonCommercial-NoDerivatives 4.0 International License.

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

The discretization grid with inflated boundary – the crosssection

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

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 the distribution of air velocity in the vertical plane YZ, X = -11.63 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

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 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 = -11.63 m: a) theoretical distribution, b) numerical distribution for case 1, c) numerical distribution for case 2

The comparison of air velocity 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	$U = 1.6 \frac{w}{m^{2} \cdot K}, t_{s} = 53 ° C$
Interior wall; “Wall”	Adiabatic wall
North-west wall; “Wall” with heat tran sfer coefficient U and sol- air temperature	$U = 1.6 \frac{w}{m^{2} \cdot K}, t_{s} = 36.23 ° C$
North-east wall; “Wall” with heat transfer coefficient U and sol-air temperature	$U = 1.6 \frac{w}{m^{2} \cdot K}, t_{s} = 36.42 ° C$
South-east windows; “Wall” with heat tr ansfer coeffi cient U and sol-a ir temperature	$U = 1.6 \frac{w}{m^{2} \cdot K}, t_{s} = 297.5 ° C$
North-west windows; “Wall” with heat transfer coeffi cient U and sol-air temperature	$U = 1.6 \frac{w}{m^{2} \cdot K}, t_{s} = 64.31 ° C$
Roof; “Wall” with heat tr ansfer coefficient U and sol-air temperature	$U = 1.6 \frac{w}{m^{2} \cdot K}, t_{s} = 65 ° C$
Floorboard; “Wall” wi th heat transfer coefficient U and exterior temperature	$U = 1.6 \frac{w}{m^{2} \cdot K}, t_{s} = 35 ° C$
Lower diffusers; “Inlet” with mass flow rate of supply air and temperature of ventilation supply air	${\dot{m}}_{S 1} = 0.121 kg / s, t_{S 1 = 16.27 ° C}$
Upper diffusers; “Inlet” with mass flow rate of supply air and temperature of ventilation supply air	${\dot{m}}_{S 2} = 0.516 kg / s, t_{S 2 = 16.94 ° C}$
Exhaust diffusers; “Outlet” with mass flow rate of exhaust air	${\dot{m}}_{E} = 0.032 kg / s$

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	$U = 2 \frac{w}{m^{2} \cdot K}, t_{s} = 61.8 ° C$
Interior wall; “Wall”	Adiabatic wall
North-west wall; “Wail” with heat teansfer coefficient U and sol-air temperature	$U = 2 \frac{w}{m^{2} \cdot K}, t_{s} = 38.3 ° C$
North-east wall; “Wall” with heat transfer coefficient U and sol-air temperature	$U = 2 \frac{w}{m^{2} \cdot K}, t_{s} = 38.88 ° C$
South-east windows; “Wall” with heat transfer coefficient U and sol-air temperature	$U = 2 \frac{w}{m^{2} \cdot K}, t_{s} = 157.99 ° C$
North-west windows; “Wall” with drat transfer coefficient U and sol-ars temperature	$U = 2 \frac{w}{m^{2} \cdot K}, t_{s} = 48.71 ° C$
Roof; “Well” with heat transfer coefficienit U and sol-air temperature	$U = 1.2 \frac{w}{m^{2} \cdot K}, t_{s} = 53.1 ° C$
Floorboard; “Well” with heat transfer “coefficient U and exterior-temperature	$U = 1.2 \frac{w}{m^{2} \cdot K}, t_{s} = 35 ° C$
Lower diffusers; “Inlet” with mass flow rale of supply air and temperature of ventilation supply air	${\dot{m}}_{S 1} = 0.121 kg / s, t_{S 1 = 19.4 ° C}$
Upper diffusers; "Inlet” with mass flow rate of supply air and temperature of ventilation supply air	${\dot{m}}_{S 2} = 0.516 kg / s, t_{S 2 = 19.9 ° C}$
Exhaust diffusers; “Outlet” wish mass flow rate of exhaust air	${\dot{m}}_{E} = 0.032 kg / s$

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

eISSN:: 1899-0142
Lingua:: Inglese

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MODELLING OF THE AIRFLOW IN THE PASSENGER COACH

Article Category: 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

Parole chiave
Airflow, Coach, CFD, Heat exchange, Ventilation

© 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.

Figure 2.

Figure 3.

Figure 4.

Figure 5.

Figure 6.

Figure 7.

Figure 8.

Figure 9.

Figure 10.

Figure 11.

Figure 12.

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

Boundary condition for case 2

Parameters of outdoor air – winter conditions

Boundary conditions for case 1

Parameters of outdoor air – summer conditions

MODELLING OF THE AIRFLOW IN THE PASSENGER COACH

Article Category: 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

Parole chiaveAirflow, Coach, CFD, Heat exchange, Ventilation

© 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.

Figure 2.

Figure 3.

Figure 4.

Figure 5.

Figure 6.

Figure 7.

Figure 8.

Figure 9.

Figure 10.

Figure 11.

Figure 12.

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

Boundary condition for case 2

Parameters of outdoor air – winter conditions

Boundary conditions for case 1

Parameters of outdoor air – summer conditions

Parole chiave
Airflow, Coach, CFD, Heat exchange, Ventilation