EP2965021B1 - Klimaanlage - Google Patents

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Publication number
EP2965021B1
EP2965021B1 EP14710207.3A EP14710207A EP2965021B1 EP 2965021 B1 EP2965021 B1 EP 2965021B1 EP 14710207 A EP14710207 A EP 14710207A EP 2965021 B1 EP2965021 B1 EP 2965021B1
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Prior art keywords
air
venturi
secondary air
chamber
mixing
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EP14710207.3A
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English (en)
French (fr)
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EP2965021A1 (de
Inventor
Dan Alexandru BUNIS
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Modulair SA
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Modulair SA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/26—Arrangements for air-circulation by means of induction, e.g. by fluid coupling or thermal effect
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/01—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station in which secondary air is induced by injector action of the primary air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/02—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing
    • F24F1/022—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing comprising a compressor cycle
    • F24F1/027—Self-contained room units for air-conditioning, i.e. with all apparatus for treatment installed in a common casing comprising a compressor cycle mounted in wall openings, e.g. in windows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/24—Means for preventing or suppressing noise

Definitions

  • the present invention relates to an air conditioning device, and to a method of air conditioning air in a confined environment.
  • Air conditioning devices integrated into the ceiling of confined rooms are well known.
  • a first type relates to cold beams of the static type, in which the air passes through a cooled exchanger, the air flow being generated by simple convection.
  • a second type of cold beam relates to dynamic type cold beams in which a flow of cool air coming from outside the confined space is mixed with secondary air coming from the room to be conditioned.
  • the primary air is injected at high pressure into nozzles, inducing a suction of secondary air by the venturi effect.
  • This type of device has many advantages.
  • a first advantage is that the injection of fresh air allows renewal of the air in the confined environment.
  • the primary fresh air can also be dried so as to avoid condensation phenomena.
  • the secondary air passes through a cooled heat exchanger before mixing, which increases the cooling capacity of the complete device.
  • these dynamic cold beams have other drawbacks that the present invention will seek to reduce.
  • this type of device is generally noisy. Indeed, for optimum operation, the ratio between the primary fresh air supply and the secondary air recirculation should be around 1: 7.
  • the pressure of the primary air, and its speed in the nozzles induce noise that is difficult to bear continuously.
  • these dynamic beams generally operate with a primary air / secondary air ratio lower than the optimum, generally between 1: 2 and 1: 6. This low ratio implies a renewal of air in the medium greater than what is necessary, implying an energy consumption higher than what is strictly necessary.
  • the European patent application EP1319901 discloses a device comprising two Venturi type devices arranged in series making it possible to mix so-called primary fresh air with said secondary recirculated air. Nevertheless, the pressure at the inlet of the second Venturi device is largely insufficient, and does not allow sufficient secondary air suction to be achieved, and the ratio between secondary air and primary air is still insufficient.
  • the present invention aims to provide an air conditioning device with a dynamic cold beam, exhibiting reduced noise while offering an improved primary air / secondary (recirculated) air ratio.
  • it also aims to improve the thermal comfort associated with the use of the device of the invention.
  • the object of the invention is achieved by an air conditioning device according to claim 1.
  • the present invention relates to an air conditioning device comprising a primary air intake duct (chamber) connected to the inlet. of a first venturi-type device (inductor) the suction of which communicates with a first duct (chamber) for the admission of secondary air, the outlet of the first venturi-type device communicating with the inlet of a second control device venturi type (inductor) the suction of which is connected to a second duct (chamber) for the admission of secondary air comprising a first heat exchanger.
  • a primary air intake duct chamber
  • a first venturi-type device the suction of which communicates with a first duct (chamber) for the admission of secondary air
  • the outlet of the first venturi-type device communicating with the inlet of a second control device venturi type (inductor) the suction of which is connected to a second duct (chamber) for the admission of secondary air comprising a first heat exchanger.
  • the output of this device communicates directly or indirectly with the room to be conditioned.
  • the first device of the venturi type comprises a primary air inlet nozzle comprising a diameter restriction at its free end, said free end opening into a suction chamber communicating with the first inlet duct. secondary air, said suction chamber comprising an outlet opening facing the outlet of said inlet nozzle, said outlet opening communicating with the inlet of the second device of the venturi type.
  • the second venturi-type device comprises an intake (or mixing) chamber, the intake chamber having a cross section at least twice as large as the outlet opening of the suction chamber of the first venturi-type device.
  • the second device of the venturi type comprises a plate pierced with orifices, said plate separating the intake chamber communicating with the outlet of the first mixing device and a mixing chamber communicating with the second secondary air intake duct, said orifices producing, in use, a venturi effect drawing secondary air from the second secondary air intake duct.
  • the device of the invention comprises an adjustable valve or valve making it possible to inject primary air directly at the inlet of the second venturi type device, downstream of the first venturi device, so as to be able to regulate the ratio of total mixture between primary air and secondary air.
  • the first secondary air intake duct comprises a second heat exchanger making it possible, in use, to cool the secondary air.
  • the heat exchanger (s) comprise vertical fins, and a condensation discharge device at the bottom thereof.
  • a second aspect of the invention relates to a facade, a facade element or an element allowing access to the facade of a building comprising an air conditioning device according to any one of claims 1-5.
  • the facade of the invention comprises two walls separated by a ventilation space, the first and second secondary air intake ducts communicating with said ventilation space.
  • the second wall may be of the curtain or helioscreen type, or, preferably, the facade will be of the active facade type.
  • a third aspect of the invention relates to a method of air conditioning the air of a confined space according to claim 8.
  • the present invention relates to an air conditioning device 10 of the dynamic chilled beam type comprising a double module for inducing secondary air, making it possible, in use, to increase the ratio between the primary air flow 18,22 outside injected into the room to be conditioned, and the secondary air flow recirculated 16,17.
  • the use of two Venturi type induction modules, arranged in series, makes it possible to reduce noise, without increasing the necessary primary air pressure, while allowing the secondary air flow to be increased for an air flow. primary given.
  • venturi-type device or induction device
  • This is typically a device of the ejector or eductor type, either in the form of nozzles, diaphragms, or more complex devices comprising an inlet nozzle, a suction chamber and an outlet nozzle.
  • inlet of a venturi device is meant the inlet of the first air flow.
  • the first venturi device into which air conditioning 18 from an external air conditioning coil is injected, comprises an injection nozzle 3 comprising a restriction at its free end.
  • This nozzle opens into a suction chamber 2 communicating with a secondary air duct 9 (coming from the room to be conditioned).
  • the suction chamber 2 also comprises an outlet orifice 15 facing the outlet of the injection nozzle 3. This orifice 15 will advantageously be extended by a profiled ejection nozzle, so as to reduce turbulence and the noise generated by this turbulence.
  • the first venturi device is dimensioned such that the flow rate ratio between the primary air 18 and the air induced 17 by the first venturi device is between 0.7 and 1.5.
  • the second venturi-type device comprises an inlet chamber, the inlet chamber having a section at least twice as large as the outlet orifice of the suction chamber.
  • the increased section of the intake chamber allows compression of the first mixture air, which considerably improves the air induction by the second Venturi type device.
  • the temperature of the primary air 18 will preferably be between 14 and 18 ° C depending on the cooling power required. This primary air 18 will also have a controlled humidity rate so as to reduce the relative humidity of the room, so as to avoid any condensation phenomenon. Finally, the pressure of the primary air 18 will preferably be between 300 and 500 Pa, ideally around 400 Pa.
  • the pressures included in this description are of course relative pressures with respect to the ambient atmospheric pressure (pressure difference with respect to the environment).
  • the second induction device will preferably be in the form of a wall 14 (plate) separating the inlet or mixing chamber 4 into which the outlet 15 of the first venturi device emerges from a second mixing chamber 6. into which opens a second secondary air intake duct 11.
  • This second intake duct comprises a main heat exchanger 8 making it possible to effectively cool the secondary air flow 16 induced by the second venturi device.
  • the wall 14 will include orifices 5 communicating between the first mixing chamber 4 and the second mixing chamber 6. These orifices 5 will either be in the form of simple diaphragms, or in the form of nozzles inducing an increase in the speed of the air. , and by this fact, a venturi effect sucking the secondary air 16 through the main heat exchanger 8.
  • the pressure in the first mixing chamber 4 is preferably between 50 and 100 Pa, so as to reduce the noise generated by the device.
  • the flow rate ratio between the secondary air intake 16 of the second venturi device and the outlet 19 of the first induction device is preferably between 2 and 4, bringing the total ratio between primary air and air induced by the two devices. venturi to a value greater than around 4, preferably greater than 6, and even advantageously greater than 7.
  • the figure 4 represents the operation of the device when the valve 21 is in position opened.
  • a primary air flow 22 is admitted directly into the inlet chamber 4.
  • the first secondary air inlet duct will comprise a non-return device (not shown), for example in the form of a valve preventing a reverse flow of primary air.
  • a secondary heat exchanger 7 can advantageously be placed on the fluid path of the secondary air flow 17 upstream of the suction of the first venturi-type device. This secondary heat exchanger 7 makes it possible on the one hand to increase the total power of the device, and on the other hand to regulate the humidity of the mixture in the first mixing chamber 4.
  • the setpoint temperature of the heat exchangers 7,8 will be maintained at a temperature of between 14 and 20 ° C., so as to avoid condensation while providing sufficient cooling power.
  • This setpoint temperature will be adapted according to the power required and the relative humidity of the secondary air.
  • the air conditioning module (device) of the invention is integrated in the facade, above the windows, so as to induce a secondary air flow in front of the hot zone induced by the glazing of the building.
  • This hot zone could advantageously be optimized by the use of devices simulating an active facade, such as curtains or helioscreens.
  • the air conditioning module of the invention is integrated into an active facade comprising a ventilated void included between two walls, the secondary air intake ducts 9,11 being connected to said ventilated void.
  • the circulation of conditioned secondary air between the two walls makes it possible to cool the internal wall, and thereby improve the comfort of the air-conditioned room, the walls of the room having a lowered temperature, which improves the comfort.
  • the front arrangement allows the use of vertical exchangers, which allows easy collection and evacuation of any condensation on the fins of these exchangers.
  • the integration of the air conditioning module of the invention in the facade also makes it possible to reduce the bulk, the primary air and cold water pipes can easily be integrated into said facade, avoiding having to integrate the beams into the ceilings, posing installation and maintenance difficulties.
  • the device of the invention may advantageously integrate one or more carbon filters.
  • the internal surfaces of the mixing chambers and the venturis may be covered with catalytic paint comprising Ag ions or titanium oxide photocatalytic paints which, through the use of UV light sources, reduce the volatile organic compounds present in the room.
  • the primary fresh air can also be taken directly from the facade by means of a fan, the humidity is then regulated directly along the heat exchangers, by means of a condensate pan placed under the heat exchangers.
  • FIG. 1 An exemplary embodiment of a device 10 according to the invention is shown in figures 1 to 4 .
  • This device is integrated into an active facade in which the air is heated by the action of the sun in a ventilated space between 2 panes.
  • the air in the ventilated vacuum communicates with the room to be conditioned through the bottom of the active window, so as to increase the natural convection through the device, thus further improving the secondary air flow.
  • a distribution duct 12 placed on the front provides conditioned primary air.
  • the air in this duct is maintained at a pressure of 410 Pa and a temperature of about 14 ° C.
  • the humidity of this primary air is around 90%.
  • This air is conditioned by means of a first centralized battery for the entire building.
  • the energy consumption of this first battery, per air conditioning module, is around 283W for an outside temperature of 32 ° C and a relative humidity of 50%.
  • This air-conditioned primary air 18 is brought by a distribution chamber 1 to a nozzle 3 opening into the first suction chamber 2.
  • the air-conditioned primary air flow rate in each facade module is 25 m 3 / h.
  • the air-conditioned primary air flow at the outlet of the nozzle 3 draws secondary air 17 through an orifice 13.
  • This secondary air coming from the intake duct 9 passes into a heat exchanger 7 before being mixed with the primary air 18 in the suction chamber 2.
  • the temperature of the cooling water in this exchanger is 12 ° C at the inlet and 14 ° C at the outlet.
  • the power consumed by this battery is around 146W.
  • the secondary air 17 comes from an active facade, and enters the heat exchanger at a temperature of 34 ° C and 36% relative humidity.
  • the secondary air flow 17 in this first heat exchanger 7, induced by the primary air flow, is 25 m 3 / h.
  • the mixture 19 of primary 18 and secondary 17 air induced by the first venturi is injected into a chamber 4 delimited by a wall 14 pierced with orifices 5 opening onto a second suction chamber 6.
  • Secondary air 16 enters this second suction chamber 6 through a second heat exchanger 8.
  • the secondary air drawn in through the duct 11 again comes from the active facade and has the same inlet characteristics as the air admitted by the duct 9.
  • the secondary air flow induced in this second venturi is around 150m 3 / h.
  • An air flow rate of 200m 3 / h is therefore obtained at the outlet of the device, for a primary air flow rate of 25m 3 / h, ie a multiplying factor of 8 (or a ratio of 1: 7).
  • the outlet air in this example is 18 ° C, for an ambient temperature of 26 ° C. This conditioned air is ejected through port 23.
  • a valve 20, 21 allows the need to bypass the first inductor (venturi), if necessary, so as to increase and reduce the multiplicative factor of the device.
  • the primary air despite increases to 50m 3 / h, while the secondary air flow induced in the second inductor remains constant at 150m 3 / h, passing by a multiplying factor of 8 to 4.
  • Forcing the secondary air into the ventilated space of the active facade prevents an exaggerated increase in the temperature of the interior walls of the room, which improves the sensory comfort of the occupants.
  • the two heat exchangers 7,8 being contiguous, in practice, a single exchanger can be used with a wall separating the two conduits. Nevertheless, it may be advantageous to regulate these two heat exchangers separately, so as to avoid any condensation in the first mixing chamber.
  • the dimensions of the module of the example are compatible with the dimensions of windows usually used in the building, in this case, in this example, the width of the second heat exchanger is 1m, and 25cm for the first exchanger.
  • the height of the first and second heat exchangers is 29cm, while the total height of the module (including the primary air distribution duct 12) is 60cm.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Central Air Conditioning (AREA)
  • Duct Arrangements (AREA)
  • Jet Pumps And Other Pumps (AREA)

Claims (14)

  1. Klimatisierungsvorrichtung (10) der Luft, umfassend eine Primärluft-Einlassleitung (1), die mit dem Eingang einer ersten Vorrichtung vom Venturityp verbunden ist, deren Ansaugung mit einer ersten Sekundärluft-Einlassleitung (9) kommuniziert, wobei der Ausgang der ersten Vorrichtung vom Venturityp mit dem Eingang einer zweiten Vorrichtung vom Venturityp kommuniziert, deren Ansaugung mit einer zweiten Sekundärluft-Einlassleitung (11) kommuniziert, die einen Hauptwärmetauscher (8) umfasst, wobei die erste Vorrichtung vom Venturityp eine Primärluft-Eingangsdüse (3) umfasst, die eine Durchmesserverengung an ihren freien Ende umfasst, wobei das freie Ende in eine Ansaugkammer (2) ausmündet, die mit der ersten Sekundärluft-Einlassleitung (9) kommuniziert, wobei die Ansaugkammer (2) eine Ausgangsöffnung (15) gegenüber dem Ausgang der besagten Eingangsdüse umfasst, wobei die besagte Ausgangsöffnung (15) mit dem Eingang der zweiten Vorrichtung vom Venturityp kommuniziert, dadurch gekennzeichnet, dass die zweite Vorrichtung vom Venturityp eine Einlasskammer (4) umfasst, wobei die besagte Einlasskammer (4) einen Querschnitt aufweist, der mindestens zweimal größer als die Ausgangsöffnung (15) der Ansaugkammer (2) ist.
  2. Klimatisierungsvorrichtung (10) nach Anspruch 1, wobei die zweite Vorrichtung vom Venturityp eine von Öffnungen (5) durchbrochene Platte (14) umfasst, wobei die besagte Platte die Einlasskammer (4), die mit dem Ausgang (15) der ersten Mischvorrichtung kommuniziert, und eine Mischkammer (6), die mit der zweiten Sekundärluft-Einlassleitung (11) kommuniziert, trennt, wobei die besagte Öffnungen (5) bei Verwendung einen Venturieffekt erzeugen, bei dem die Sekundärluft angesaugt wird.
  3. Klimatisierungsvorrichtung (10) nach irgendeinem der vorangehenden Ansprüche, wobei die erste Sekundärluft-Einlassleitung (9) einen sekundären Wärmetauscher (7) umfasst.
  4. Klimatisierungsvorrichtung (10) nach irgendeinem der vorangehenden Ansprüche, wobei der oder die Wärmetauscher vertikale Flügel und eine Ableitungsvorrichtung der Kondensation am unteren Ende derselben umfassen.
  5. Klimatisierungsvorrichtung (10) nach irgendeinem der vorangehenden Ansprüche, wobei ein einstellbares Ventil erlaubt, Primärluft direkt in den Eingang der zweiten Vorrichtung vom Venturityp der ersten Venturi-Vorrichtung nachgelagert einzuleiten, so dass das Gesamtmischverhältnis zwischen der Primärluft und der Sekundärluft eingestellt werden kann.
  6. Fassade, die eine Klimatisierungsvorrichtung (10) nach irgendeinem der vorangehenden Ansprüche umfasst.
  7. Fassade nach Anspruch 6, umfassend zwei durch einen Lüftungsbereich getrennte Wände, wobei die erste und zweite Sekundärluft-Einlassleitung mit dem besagten Lüftungsbereich verbunden sind.
  8. Methode zur Klimatisierung der Luft an einem eingeschlossenen Ort, die die folgenden Schritte umfasst:
    a. Entnehmen von Außenluft (18), bezeichnet als Primärluft, und Bringen auf einen vorher festgelegten Druck;
    b. Einleiten der Primärluft (18) in eine Vorrichtung vom Venturityp, die von einer Ansaugkammer (2) ansaugt und Luft des eingeschlossenen Orts, bezeichnet als Sekundärluft (17), mit der Primärluft mischt, wobei die Sekundärluft vor dem Mischen in einen ersten Wärmetauscher (7) strömt, der auf eine Solltemperatur eingestellt ist, wodurch ein erstes Luftgemisch (19) erhalten wird;
    c. Einleiten des ersten Luftgemischs (19) in eine zweite Vorrichtung vom Venturityp, die Sekundärluft (16) ansaugt und mit dem besagten ersten Luftgemisch (19) mischt, wobei die Sekundärluft vor dem Mischen in einen zweiten Wärmetauscher (8) strömt, der auf eine Solltemperatur eingestellt ist;
    d. Wiedereinleiten des erhaltenen Luftgemischs in den eingeschlossenen Ort;
    dadurch gekennzeichnet, dass das erste Luftgemisch (19) in einer Einlasskammer (4) komprimiert wird, die mit der Ausgangsöffnung (15) der Ansaugkammer (2) kommuniziert, wobei die besagte Einlasskammer (4) einen Querschnitt aufweist, der mindestens zweimal größer als die Ausgangsöffnung (15) der Ansaugkammer (2) ist, so dass eine Kompression des ersten Luftgemischs (19) herbeigeführt wird.
  9. Methode nach Anspruch 8, wobei der besagte vorher festgelegte Druck zwischen 100 und 1000 Pa liegt.
  10. Methode nach irgendeinem der Ansprüche 8 oder 9, wobei das Verhältnis zwischen dem Einlass von Primärluft und von Sekundärluft in die erste Mischvorrichtung zwischen 0,7 und 2,5 liegt.
  11. Methode nach irgendeinem der Ansprüche 8 bis 10, wobei das Durchsatzverhältnis zwischen dem Einlass des ersten Luftgemischs und von Sekundärluft in die zweite Mischvorrichtung zwischen 2 und 4 liegt.
  12. Methode nach irgendeinem der Ansprüche 8 bis 11, wobei der Druck des ersten Luftgemischs am Eingang der zweiten Venturi-Vorrichtung zwischen 50 und 100 Pa liegt.
  13. Methode nach irgendeinem der Ansprüche 8 bis 12, wobei die Sekundärluft in einem belüfteten Bereich zwischen zwei Wänden einer aktiven Fassade zirkuliert, bevor sie durch die Wärmetauscher (7, 8) angesaugt wird.
  14. Methode nach irgendeinem der Ansprüche 8 bis 13, wobei die in Schritt (a) entnommene Primärluft auf eine vorher festgelegte Temperatur gebracht wird, bevor sie in die besagte erste Vorrichtung vom Venturityp eingeleitet wird.
EP14710207.3A 2013-03-05 2014-02-26 Klimaanlage Active EP2965021B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
BE2013/0144A BE1021395B1 (fr) 2013-03-05 2013-03-05 Climatiseur
PCT/EP2014/053677 WO2014135406A1 (fr) 2013-03-05 2014-02-26 Climatiseur

Publications (2)

Publication Number Publication Date
EP2965021A1 EP2965021A1 (de) 2016-01-13
EP2965021B1 true EP2965021B1 (de) 2021-02-24

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EP14710207.3A Active EP2965021B1 (de) 2013-03-05 2014-02-26 Klimaanlage

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US (1) US20160018128A1 (de)
EP (1) EP2965021B1 (de)
JP (1) JP6521869B2 (de)
CN (1) CN105026850B (de)
BE (1) BE1021395B1 (de)
CA (1) CA2903915A1 (de)
EA (1) EA201591633A1 (de)
IN (1) IN2015DN09035A (de)
PH (1) PH12015501923A1 (de)
SG (1) SG11201507095YA (de)
WO (1) WO2014135406A1 (de)
ZA (1) ZA201507299B (de)

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Publication number Publication date
PH12015501923A1 (en) 2016-01-04
WO2014135406A1 (fr) 2014-09-12
CA2903915A1 (fr) 2014-09-12
EP2965021A1 (de) 2016-01-13
IN2015DN09035A (de) 2015-10-23
JP6521869B2 (ja) 2019-05-29
US20160018128A1 (en) 2016-01-21
BE1021395B1 (fr) 2015-11-16
EA201591633A1 (ru) 2016-02-29
SG11201507095YA (en) 2015-10-29
ZA201507299B (en) 2017-02-22
CN105026850A (zh) 2015-11-04
CN105026850B (zh) 2019-02-12
JP2016509195A (ja) 2016-03-24

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