US20130035029A1 - Supply Air Unit - Google Patents

Supply Air Unit Download PDF

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Publication number
US20130035029A1
US20130035029A1 US13/515,911 US201013515911A US2013035029A1 US 20130035029 A1 US20130035029 A1 US 20130035029A1 US 201013515911 A US201013515911 A US 201013515911A US 2013035029 A1 US2013035029 A1 US 2013035029A1
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US
United States
Prior art keywords
heat
supply air
unit
transfer
chamber
Prior art date
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Abandoned
Application number
US13/515,911
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English (en)
Inventor
Mika Ruponen
Panu Mustakallio
Risto Kosonen
Maija Virta
Harri Itkonen
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Halton Oy
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Halton Oy
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Assigned to HALTON OY reassignment HALTON OY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RUPONEN, MIKA, ITKONEN, HARRI, KOSONEN, RISTO, MUSTAKALLIO, PANU, VIRTA, MAIJA
Publication of US20130035029A1 publication Critical patent/US20130035029A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/12—Tube and panel arrangements for ceiling, wall, or underfloor heating
    • F24D3/16—Tube and panel arrangements for ceiling, wall, or underfloor heating mounted on, or adjacent to, a ceiling, wall or floor
    • F24D3/165—Suspended radiant heating ceiling
    • 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
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/00075—Indoor units, e.g. fan coil units receiving air from a central station
    • 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
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • 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
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0089—Systems using radiation from walls or panels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0089—Systems using radiation from walls or panels
    • F24F5/0092—Systems using radiation from walls or panels ceilings, e.g. cool ceilings
    • 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 invention concerns a supply air unit in accordance with the preamble to claim 1 .
  • Supply air units or air-conditioning beams usually comprise a supply air chamber, a mixing chamber and a heat exchanger.
  • a flow of fresh air is brought from the supply air chamber into the mixing chamber, in which the flow of fresh air is mixed together with a circulated airflow, whereupon the combined airflow is conducted into a room space.
  • the circulated airflow is conducted into the mixing chamber through a heat exchanger, in which the circulated airflow can be either heated or cooled.
  • the flow of fresh air induces the circulated airflow to flow from the room through the heat exchanger into the mixing chamber.
  • Patent application FI 20060035 presents a supply air unit and a method for controlling the airflow rate.
  • the supply air unit comprises a supply air chamber, a heat exchanger and a mixing chamber. From the supply air chamber the flow of fresh air is conducted through nozzles into the mixing chamber, in which the supply airflow induces a circulated airflow to flow from the room through the heat exchanger into the mixing chamber. In the mixing chamber, the combined fresh airflow and circulated airflow are conducted from the mixing chamber's outlet opening into the air-conditioned room space.
  • the supply air unit also comprises a separate additional air opening, which is equipped with a controller, which can be used for controlling the rate of fresh airflow supplied from the supply air chamber past the nozzles and into the room space. The additional air opening may lead from the supply air chamber either directly into the air-conditioned room space or into the mixing chamber.
  • Patent application FI 20075213 presents a supply and exhaust air unit, which comprises a supply air chamber and a mixing chamber.
  • the supply and exhaust air unit also comprises a separate additional air opening, which is equipped with a controller and which can be used for controlling the rate of fresh airflow supplied from the supply air chamber past the nozzles and into the room space.
  • the supply and exhaust air unit also comprises an exhaust air opening, which is equipped with a controller and which can be used for controlling the rate of air exhausted from the room space.
  • Patents FI 117682 B, 118236 B present supply air units, which comprise a supply air chamber, a heat exchanger and a mixing chamber.
  • a fresh airflow is conducted from the supply air chamber through nozzles into the mixing chamber, in which the supply airflow induces a circulated airflow to flow from the room through the heat exchanger and into the mixing chamber.
  • the combined fresh airflow and circulated airflow are conducted from the mixing chamber's outlet opening into the air-conditioned room space.
  • the publications present various systems for controlling the induction ratio and for controlling either the rate of fresh airflow supplied into the mixing chamber or the rate of circulated airflow conducted from the air-conditioned room space into the mixing chamber.
  • Patent EP 0 365 586 B1 presents a ventilation device, which comprises an elongated supply air chamber, which is located in connection with the ceiling surface in the air-conditioned room space, and located beside it an elongated panel.
  • the panel is heated or cooled by tubes, which are fitted in connection with the panel's top surface and in which a heat carrier flows.
  • a supply air passage In the supply air chamber there is a supply air passage, from which air is blown in the horizontal direction along the horizontal bottom surface of said panel, whereby the airflow blown inside is in thermal interaction with the panel.
  • On the panel's top surface there is a heat-insulating material, which also covers the tubes transporting the heat carrier.
  • the aim here is to boost the transfer of heat from the radiating surface into the air-conditioned room space by using forced convection, which is brought about by blowing the supply airflow along the panel's bottom surface, that is, the radiating surface. This again raises the temperature of the radiating surface and in this way reduces the radiation.
  • the increase in efficiency achieved by blowing is considerably smaller than the increase in efficiency achieved by heat exchangers.
  • the air In the air-conditioned room space the air is stratified in such a way that the lighter warm air rises up towards the room's ceiling surface, whereas the heavier cool air sinks down towards the room's floor surface.
  • heating and cooling take place through the air moving through the heat exchanger. Efficient heat transfer would thus require that the air circulates at a high velocity in the room space, but a high velocity again will cause draught.
  • heating and cooling take place as radiation between the heat transferring surface and the room surfaces. A person will feel both the temperature of the room surfaces and the temperature of the air in the room.
  • the supply air unit according to the invention is characterised by the features presented in the characterising part of claim 1 .
  • the supply air unit comprises a supply air chamber, at least one mixing chamber, which opens into the air-conditioned room space, nozzles or a nozzle gap, through which a fresh airflow is conducted from the supply air chamber into said at least one mixing chamber, a first heat transfer unit, which is formed by at least one heat exchanger, through which a circulated airflow is conducted from the air-conditioned room space into said at least one mixing chamber, and in which the circulated airflow is cooled or heated.
  • the combined airflow formed from said at least one mixing chamber by the fresh airflow and the circulated airflow is conducted into the air-conditioned room space.
  • the supply air unit also comprises a second heat transfer unit, which is located in its lower part and which is formed by at least one radiating element, which has a radiating surface, to which heat is transferred from the air-conditioned room space for cooling or from which heat is transferred into the air-conditioned room space for heating.
  • the radiating surface also comprises a perforation, which makes it sound-absorbing. The perforation reduces the reflection of sound taking place in the radiating surface, whereby the acoustic characteristics of the room space are improved.
  • the supply air unit has a first heat transfer unit transferring heat by convection and a second heat transfer unit transferring heat by radiation.
  • first heat transfer unit heat is transferred from a heat-carrying liquid travelling in tubing to the heat exchanger's heat transfer surfaces and further from these into a circulated airflow travelling between the heat transfer surfaces.
  • second heat transfer unit heat is transferred from a heat-carrying liquid travelling in tubing to the radiating surface and further from this as radiation to the room surfaces.
  • the tubes of the heat exchangers and the radiating element can be dimensioned in such a way that the flow characteristics in the tubes are different.
  • the flow is kept turbulent in the radiating element's tubing and laminar in the heat exchanger s' tubes.
  • a high turbulence of the flow in the radiating element's tubing leads to a high heat transfer coefficient between the heat-carrying liquid and the tube, whereby the heat transfer from the heat-carrying liquid to the tube becomes more efficient.
  • a laminar flow in the heat exchangers' tubes will for its part produce a low heat-transfer coefficient and thus lower heat transfer from the heat-carrying liquid to the tube.
  • a major part of the cooling power is thus obtained from the radiating element, whereby the sense of draught caused by the cool moving airflow can be minimized.
  • cooling capacity is delivered in a cooling situation into the air-conditioned room space both by convection and by radiation, whereby the thermal comfort can be improved in the room space as a result of reduced movement of air. Thanks to the radiation, the supply air unit also in a shorter time will affect the sense of warmth of a person staying in the air-conditioned room space.
  • FIG. 1 is a schematic cross-sectional view of a supply air unit according to the invention.
  • FIG. 2 is a schematic cross-sectional view of another supply air unit according to the invention.
  • FIG. 3 is a schematic cross-sectional view of a third supply air unit according to the invention.
  • FIG. 4 is a schematic cross-sectional view of a fourth supply air unit according to the invention.
  • FIG. 5 is a schematic cross-sectional view of a fifth supply air unit according to the invention.
  • FIG. 6 is a schematic cross-sectional view of a sixth supply air unit according to the invention.
  • FIG. 7 is a schematic cross-sectional view of a seventh supply air unit according to the invention.
  • FIG. 8 is a schematic view of a heat-transfer circuit suitable for the supply air unit shown in FIG. 1 .
  • FIG. 1 is a cross-sectional view of a supply air unit according to the invention.
  • the supply air unit 100 comprises a supply air chamber 10 , whose cross-section is essentially rectangular comprising in its lower part triangular bracket sections 10 a , 10 b .
  • a first row of nozzles 60 a or a nozzle gap In the roof surface of the right-hand bracket section 10 b there is a second row of nozzles 60 b or a nozzle gap.
  • a first heat exchanger 30 a At a distance from the supply air chamber's 10 left-hand vertical side wall 11 a there is a first heat exchanger 30 a with a rectangular cross-sectional shape.
  • a second heat exchanger 30 b with a rectangular cross-sectional shape.
  • a first mixing chamber 20 a is formed in a space between the supply air chamber's 10 left-hand vertical side wall 11 a and the first heat exchanger 30 a .
  • a second mixing chamber 20 b is formed in a space between the supply air chamber's 10 right-hand vertical side wall 11 b and the second heat exchanger 30 b.
  • first outlet opening 25 a is formed in the first mixing chamber's 20 a top part
  • second outlet opening 25 b is formed in the second mixing chamber's 20 b top part. Both outlet openings 25 a , 25 b are formed in such a way that the airflow LA leaving the supply air unit 100 is guided from the mixing chamber 20 a , 20 b in the air-conditioned room space to the side essentially in the direction of the room's ceiling surface K.
  • a first suction chamber 40 a is formed outside the outer surface of the first heat exchanger 30 a
  • a second suction chamber 40 b is formed outside the outer surface of the second heat exchanger.
  • the bottom surface of each suction chamber 40 a , 40 b has openings 41 a , 41 b , from which the circulated air L 2 taken from the room space can enter the suction chamber 40 a , 40 b .
  • Suction chambers 40 a , 40 b are not needed for the supply air unit's 100 operation, so they can also be omitted. Their function is mostly aesthetic. In a supply air unit 100 without suction chambers 40 a , 40 b , the circulated airflow L 2 arrives directly at the outer side surface of the heat exchangers 30 a , 30 b.
  • a fresh supply airflow L 1 is conducted by a blowing fan into the supply air chamber 10 , for example, by way of a tube fitting (not shown in the figure) located in its end surface, and further through the supply air chamber's 10 first row of nozzles 60 a into the first mixing chamber 20 a and through the second row of nozzles 60 b into the second mixing chamber 20 b .
  • a fresh airflow L 1 which is directed vertically upwards, induces the circulated airflow L 2 from the air-conditioned room space to travel through the suction chambers 40 a , 40 b and the heat exchanger 30 a , 30 b into the mixing chambers 20 a , 20 b .
  • the circulated airflow L 2 can be cooled or heated in the heat exchangers 30 a , 30 b .
  • the fresh airflow L 1 directed upwards travels tangentially in relation to the heat exchanger's 30 a , 30 b surface, which opens into the mixing chamber 20 a , 20 b.
  • the combined airflow LA formed of the fresh airflow L 1 and the circulated airflow L 2 in the first mixing chamber 20 a is conducted from the first outlet opening 25 a along ceiling surface K to the left in the figure, and the combined airflow LA formed in the second mixing chamber 20 b is conducted from the second outlet opening 25 b along ceiling surface K to the right in the figure.
  • the supply air unit 100 is symmetrical in relation to the vertical central axis Y-Y and it is preferably formed by an elongated body.
  • the supply air unit 100 is suspended at the supply air chamber's 10 roof wall 11 d with suitable suspension fasteners to the ceiling K of the air-conditioned room space in such a way that the supply air chamber's 10 roof wall 11 d remains at a distance from the ceiling surface K.
  • the heat exchangers 30 a , 30 b here form a first heat-transfer unit A, in which heat is transferred by convection into the circulated airflow L 2 flowing through the heat exchangers 30 a , 30 b.
  • a radiating element 50 which comprises a horizontal, planar radiating surface 51 , tubes 52 , which are located above radiating surface 51 in connection with it and in which a heat carrier circulates, and a heat insulation 53 , which prevents the heating or cooling effect of the heat carrier flowing in tubes 52 from being transferred upwards from the radiating element 50 to the supply air chamber's 10 bottom wall 11 c.
  • the radiating element 50 forms a second heat-transfer unit B, in which heat is transferred from the planar radiating surface 51 as radiation to the planar surfaces of the room space.
  • FIG. 2 shows a schematic cross-section of another supply air unit according to the invention.
  • the supply air unit comprises a supply air chamber 10 supported against the ceiling K, a first heat-transfer unit A supported against the bottom surface of supply air chamber 10 , and a second heat-transfer unit B located below the first heat-transfer unit A, at a distance from the first heat-transfer unit A.
  • the first heat-transfer unit A is formed by one heat exchanger 30 .
  • a fresh airflow L 1 is blown from the supply air chamber's 10 nozzles 60 a , 60 b in a horizontal direction to the sides and into the mixing chambers 20 a , 20 b .
  • a circulated airflow L 2 is conducted from the room space through a space between the second heat-transfer unit B and the heat exchanger 30 through heat exchanger 30 into mixing chambers 20 a , 20 b , from which the combined airflow LA is blown in a horizontal plane to the sides into the air-conditioned room space.
  • the second heat-transfer unit B is entirely similar to the second heat-transfer unit B shown in FIG. 1 .
  • FIG. 3 shows a schematic cross-section of a third supply air unit according to the invention.
  • This embodiment differs from the embodiment shown in FIG. 2 in that the supply air chamber 10 and the first heat-transfer unit A, that is, the heat exchanger 30 , are turned through 180 degrees.
  • Heat exchanger 30 is at a distance from ceiling K, and the second heat-transfer unit B is mounted to the supply air chamber's 10 bottom wall.
  • a circulated airflow L 2 is conducted from the room space through a space between the heat exchanger 30 and ceiling K through heat exchanger 30 and into mixing chambers 20 a , 20 b , from which the combined airflow LA is blown in a horizontal plane to the sides into the air-conditioned room space.
  • the second heat-transfer unit B is entirely similar to the second heat-transfer unit B shown in FIG. 1 .
  • FIG. 4 shows a schematic cross-section of a fourth supply air unit according to the invention.
  • This embodiment differs from the embodiment shown in FIG. 2 as regards the second heat-transfer unit B.
  • the second heat-transfer unit B is here formed by a radiating element 50 , the radiating surface 51 of which forms a broken line.
  • the second heat-transfer unit B is similar to the second heat-transfer unit B shown in FIG. 1 .
  • FIG. 5 shows a schematic cross-section of a fifth supply air unit according to the invention.
  • This embodiment differs from the embodiment shown in FIG. 2 as regards the second heat-transfer unit B.
  • the second heat-transfer unit B is here formed by a radiating element 50 , the radiating surface 51 of which forms a wave line.
  • the second heat-transfer unit B is similar to the second heat-transfer unit B shown in FIG. 1 .
  • FIG. 6 shows a schematic cross-section of a sixth supply air unit according to the invention.
  • This embodiment differs from the embodiment shown in FIG. 1 in that the first heat-transfer circuit A is here formed by one heat exchanger 30 only, whereby the structure becomes asymmetrical.
  • FIG. 7 shows a schematic cross-section of a seventh supply air unit according to the invention.
  • This embodiment differs from the embodiment shown in FIG. 6 in that the second heat-transfer unit B is here mounted at a certain angle ⁇ in relation to the horizontal plane.
  • the supply air unit may be mounted to the ceiling near a wall of the room or in a corner, whereby the radiating surface's 51 inclination will direct the radiation to the desired place in the air-conditioned room space, for example, towards the mid-point in the room space.
  • FIG. 8 is a schematic view of a heat-transfer circuit suitable for the supply air unit shown in FIG. 1 .
  • the heat-transfer circuit is here formed by the radiating element's 50 heat-transfer tubing 52 , by the first heat exchanger's 30 a heat-transfer tubing 32 a and by the second heat exchanger's 30 b heat-transfer tubing 32 b .
  • the radiating element's 50 heat-transfer tubing 52 is connected in series with the second heat exchanger's 30 b heat-transfer tubing 32 b .
  • the second heat exchanger's 30 b heat-transfer tubes 32 b are for their part connected in series with the first heat exchanger's 30 a heat-transfer tubing 32 a .
  • a control unit 60 located in the supply circuit is used to control the velocity of the heat-carrying liquid supplied into the heat-transfer circuit.
  • the radiating element's 50 heat-transfer tubing 52 and the heat exchangers' 30 a , 30 b heat-transfer tubes 32 a , 32 b can be dimensioned so that the flow characteristics in the heat-transfer tubes 52 , 32 a , 32 b are different.
  • the flow in the radiating element's 50 heat-transfer tubing 52 is turbulent, while in the heat exchangers' 30 a , 30 b heat-transfer tubes 32 a , 32 b the flow is laminar.
  • a high turbulence in the flow in the radiating element's 50 heat-transfer tubes 52 leads to a high heat-transfer coefficient between the heat-carrying liquid and the tube, whereby the heat transfer from the heat-carrying liquid to the tube becomes more efficient.
  • a laminar flow in the heat exchanger's 30 a , 30 b heat-transfer tubes 32 a , 32 b produces a low heat-transfer coefficient and thus a lower heat transfer from the heat-carrying liquid to the tube.
  • a major part of the cooling power is hereby obtained from the radiating element 50 .
  • Different turbulence in the radiating element's 50 tubing 52 and in the heat exchangers' 30 a , 30 b heat-transfer tubes 32 a , 32 b can be achieved, for example, by the choice of tube dimensions or by distributing the flow of the heat-carrying liquid into one or more circuits after the radiating element 50 .
  • the heat-carrying liquid is conducted into a tube having a larger flow cross-section area, its flow velocity will drop, and the other way round.
  • the circuit shown in FIG. 8 forms a simple control circuit.
  • the heat exchangers' 30 a , 30 b heat-transfer tubes 32 , 32 b and the radiating element's 50 heat-transfer tubing 52 can also be supplied by their own supply circuits and they can be controlled by separate control devices.
  • the second heat-transfer unit B is formed by one radiating element 50 , but when required the supply air unit 100 may of course comprise several radiating elements 50 .
  • the supply air unit 100 could, for example, comprise two or more parallel radiating elements 50 .
  • the radiating surface 51 of the radiating element 50 shown in the figures may be formed by a metal sheet, which has openings and which is made, for example, of aluminium or steel.
  • the cross-section of the openings in radiating surface 51 can be, for example, round, rectangular, polygonal, elliptic, oval, etc.
  • the radiating element's 50 heat insulation 53 may for its part be formed by mineral wool, glass wool, expanded polystyrene, polyurethane or by some other such material which insulates heat.
  • the radiating element 50 can also be constructed in such a way that radiating surface 51 , heat-transfer tubes 52 and heat insulation 53 are cast together to form a whole. Radiating surface 51 and heat-transfer tubes 52 are located in a mould and then, for example, fluid ceramics are poured on them. When the ceramics solidifies, a radiating element 50 will result which forms a whole.
  • the invention is not limited to the cross-sectional forms shown in the figure.
  • the cross-sectional forms of supply air chamber 10 , mixing chambers 20 a , 20 b and heat exchangers 30 a , 30 b may be rectangular but also, for example, triangular, polygonal, key-stone shapes or their combinations.
  • radiating element 50 is the supply air unit's lowest component, and no supply air flow L 1 is directed against the radiating element's 50 radiating surface 51 .
  • radiating surface 51 functions as a pure radiator, from which a cooling or heating effect is transferred to surfaces in the room space.
  • the air in between radiating surface 51 and the surfaces in the room space will hardly be cooled or heated at all by the radiating element's 50 effect.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
  • Duct Arrangements (AREA)
US13/515,911 2009-12-18 2010-12-16 Supply Air Unit Abandoned US20130035029A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FI20096350 2009-12-18
FI20096350A FI122953B (fi) 2009-12-18 2009-12-18 Tuloilmalaite
PCT/FI2010/051040 WO2011073525A1 (en) 2009-12-18 2010-12-16 Supply air unit

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US20130035029A1 true US20130035029A1 (en) 2013-02-07

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US (1) US20130035029A1 (fi)
EP (1) EP2513567B1 (fi)
FI (1) FI122953B (fi)
PL (1) PL2513567T3 (fi)
WO (1) WO2011073525A1 (fi)

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US20110124279A1 (en) * 2009-11-18 2011-05-26 Halton Oy Supply air unit
US20170146248A1 (en) * 2014-06-13 2017-05-25 Mitsubishi Electric Corporation Ceiling cassette air conditioner

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014009633A1 (de) 2014-06-27 2015-12-31 Schmid Janutin Ag Verfahren und Vorrichtung zur Belüftung und Temperierung von Räumen
CN111912068A (zh) * 2020-08-25 2020-11-10 无锡菲兰爱尔空气质量技术有限公司 不对称换能的辐射空调末端

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US4621592A (en) * 1984-11-29 1986-11-11 Vapor Corporation Boiler having improved heat absorption
US4727241A (en) * 1985-08-16 1988-02-23 Micropore International Ltd. Radiant electric heaters incorporating microporous thermal insulation
US20070164124A1 (en) * 2006-01-16 2007-07-19 Halton Oy Supply air terminal device and method for regulating the airflow rate
US20080200112A1 (en) * 2007-02-16 2008-08-21 Halton Oy Supply Air Terminal Device
US20100263829A1 (en) * 2009-04-13 2010-10-21 Keiichi Kimura Heating and cooling unit, and heating and cooling apparatus

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SE459447B (sv) * 1987-06-17 1989-07-03 Stefan Jacek Moszkowski Saett och anordning foer att ventilera ett rum genom inblaasning av luft horisontellt under en vaermevaexlande takmonterad panel
FI118236B (fi) 2000-11-24 2007-08-31 Halton Oy Tuloilmalaite
FI117682B (fi) 2000-11-24 2007-01-15 Halton Oy Tuloilmalaite
SE523648C2 (sv) * 2001-12-07 2004-05-04 Flaekt Woods Ab Tilluftbaffel för placering invid ett rumstak för tillförsel av luft till ett rum
FI122285B (fi) * 2007-03-30 2011-11-15 Halton Oy Tulo- ja poistoilmalaite

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US4621592A (en) * 1984-11-29 1986-11-11 Vapor Corporation Boiler having improved heat absorption
US4727241A (en) * 1985-08-16 1988-02-23 Micropore International Ltd. Radiant electric heaters incorporating microporous thermal insulation
US20070164124A1 (en) * 2006-01-16 2007-07-19 Halton Oy Supply air terminal device and method for regulating the airflow rate
US20080200112A1 (en) * 2007-02-16 2008-08-21 Halton Oy Supply Air Terminal Device
US20100263829A1 (en) * 2009-04-13 2010-10-21 Keiichi Kimura Heating and cooling unit, and heating and cooling apparatus

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110124279A1 (en) * 2009-11-18 2011-05-26 Halton Oy Supply air unit
US20140374063A1 (en) * 2009-11-18 2014-12-25 Halton Oy Supply air unit
US20170146248A1 (en) * 2014-06-13 2017-05-25 Mitsubishi Electric Corporation Ceiling cassette air conditioner

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WO2011073525A1 (en) 2011-06-23
FI122953B (fi) 2012-09-14
PL2513567T3 (pl) 2016-02-29
EP2513567A1 (en) 2012-10-24
FI20096350A0 (fi) 2009-12-18
FI20096350A (fi) 2011-06-19
EP2513567B1 (en) 2015-09-30

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