WO2013021817A1 - Dispositif de traitement d'air extérieur - Google Patents

Dispositif de traitement d'air extérieur Download PDF

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Publication number
WO2013021817A1
WO2013021817A1 PCT/JP2012/068785 JP2012068785W WO2013021817A1 WO 2013021817 A1 WO2013021817 A1 WO 2013021817A1 JP 2012068785 W JP2012068785 W JP 2012068785W WO 2013021817 A1 WO2013021817 A1 WO 2013021817A1
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WIPO (PCT)
Prior art keywords
air
sensible heat
temperature
outside air
path
Prior art date
Application number
PCT/JP2012/068785
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English (en)
Japanese (ja)
Inventor
和成 北隅
康晴 中野
ヤロスラワ ポルトワ
永江　公二
遼一 関矢
久樹 山脇
宗浩 趙
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株式会社イーズ
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Publication of WO2013021817A1 publication Critical patent/WO2013021817A1/fr

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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
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/147—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with both heat and humidity transfer between supplied and exhausted air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
    • F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
    • F24F12/006—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an air-to-air heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F2003/144—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only
    • F24F2003/1446—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only by condensing
    • F24F2003/1452—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only by condensing heat extracted from the humid air for condensing is returned to the dried air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F2003/1458—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification using regenerators
    • F24F2003/1464—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification using regenerators using rotating regenerators
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/56—Heat recovery units

Definitions

  • the present invention relates to an outside air processing apparatus that dehumidifies and cools outside air and supplies it to the room.
  • building facilities such as offices and hospitals are provided with an outside air processing device that dehumidifies and cools the outside air to supply it to the room in order to assist indoor cooling.
  • an air supply passage that communicates between the outdoor suction port and the indoor discharge port, a total heat exchanger that can exchange temperature and humidity, and adsorption and desorption of moisture in the air
  • the air flowing through the passage passes through the total heat exchanger, the dehumidification rotor, the sensible heat exchanger, and the air supply side cooler sequentially from the outdoor suction port, and is dehumidified and cooled and supplied to the room. It is known (see, for example, Patent Document 1).
  • the air supply side cooler is disposed in the air supply ventilation path between the sensible heat exchanger and the indoor outlet, and is a spray type that cools the air by using the latent heat of evaporation of water. Or since it is a vaporization type humidification means, while the temperature of the supplied air falls, there exists a problem that absolute humidity becomes high and it is not suitable for the air conditioning of summer.
  • the present invention has been made in view of the above-described circumstances, and an object of the present invention is to provide an outside air processing apparatus that can supply air having a lower temperature and lower humidity than outside air into a room with a simple configuration.
  • the present invention provides an air supply path for sucking outside air and supplying it to the room, dehumidifying means for dehumidifying the air flowing through the air supply path, and dehumidified air as outside air or room air.
  • the distribution means includes a blower fan provided in at least one of an air supply port of the air supply path and an exhaust port for discharging the one air to the outside of the air, and each of the second sensible heat exchange means.
  • Control means for controlling the air flow rate of the blower fan based on the outlet temperature may be provided.
  • the distribution unit includes a blower fan disposed in an opening that communicates the path through which the one air flows and the air supply path upstream of the humidification unit, and the second sensible heat exchange.
  • Control means for controlling the air flow rate of the blower fan based on each outlet temperature of the means may be provided.
  • the distribution means includes a damper provided on each of the path through which the one air flows and the air supply path on the upstream side of the humidification means, and each outlet of the second sensible heat exchange means.
  • Control means for controlling the opening degree of the damper based on the temperature may be provided.
  • the distribution means may set the distribution amount of the one air and the other air substantially equally.
  • the second sensible heat exchange means for sensible heat exchange between one humidified air and the other dehumidified air to cool the other air is provided. Air that has been cooled by utilizing the latent heat of water can be supplied to the room without increasing.
  • FIG. 1 is a conceptual diagram showing an outside air processing device 1 according to the first embodiment.
  • This outside air processing device 1 is intended to reduce the cooling load in the summer of a separately installed air conditioner by supplying outside air after dehumidifying and cooling the outside air.
  • the outside air processing apparatus 1 includes a main body box (housing) 10 formed in a box shape, and the main body box 10 is partitioned by a partition plate 11 and a plurality of paths through which air flows. Is formed.
  • the main body box 10 includes an air supply path 13 that sucks outside air OA and supplies the air supply SA into the room, a first exhaust path 15 that sucks outside air OA and discharges the exhaust EA to the outside again, A second exhaust path (a path through which one air flows) 17 is provided that discharges a part of the air that flows in the air path 13 and flows through the air supply path 13 to the outside as exhaust EA.
  • An outside air introduction fan 21 is provided at the suction port 13A of the air supply path 13, and most of the outside air OA sucked into the air supply path 13 through the suction port 13A by the operation of the outside air introduction fan 21 is a discharge port (air supply port).
  • a regeneration air introduction fan 23 is provided at the suction port 15A of the first exhaust path 15, and by the operation of the regeneration air introduction fan 23, outside air (regeneration) that is sucked into the first exhaust path 15 through the suction port 15A. Air) OA is discharged to the outside through the discharge port 15B.
  • the air supply path 13 and the first exhaust path 15 are configured such that air flows in opposition to each other, and the air supply path 13 and the first exhaust path 15 are arranged in order from the side closer to the suction port 13A of the air supply path 13 and the discharge port 15B of the first exhaust path 15.
  • a disc-shaped desiccant rotor (dehumidifying means) 25 and a first sensible heat exchanger (first sensible heat exchange means) 27 are disposed across the air supply path 13 and the first exhaust path 15.
  • a heater (heating regeneration means) 29 that heats the flowing air is disposed between the desiccant rotor 25 and the first sensible heat exchanger 27.
  • the heater 29 is formed of, for example, a hot water coil, and is supplied with hot water heated by heat obtained from natural energy such as exhaust heat when burning fuel such as gas or petroleum, or solar heat or geothermal heat. It is like that.
  • the desiccant rotor 25 is formed by forming a honeycomb-like non-woven fabric impregnated with a dehumidifying agent such as lithium chloride or silica gel into a rotor shape, and is driven to rotate at a low speed around the rotary shaft 25A.
  • the desiccant rotor 25 moves between the air supply path 13 and the first exhaust path 15 while rotating in a direction orthogonal to the air flow in the air supply path 13 and the first exhaust path 15.
  • the desiccant rotor 25 contacts the outside air OA taken from the suction port 13A in the air supply path 13 and dehumidifies the outside air OA.
  • the desiccant rotor 25 includes a dehumidifying region 25B that dehumidifies the outside air OA in the air supply path 13, and a regeneration region 25C that is heated and regenerated in contact with the regeneration air heated in the first exhaust path 15.
  • the first sensible heat exchanger 27 cools the dehumidified air by performing sensible heat exchange between the air dehumidified by the desiccant rotor 25 and the outside air sucked into the first exhaust passage 15.
  • the first sensible heat exchanger 27 is not shown, the aluminum foil or the synthetic resin film formed in a wave shape and the flat aluminum foil or the synthetic resin film are alternately alternated, and the wave directions are alternated.
  • the two flow paths 27A and 27B are orthogonal to each other, and the flow paths 27A and 27B communicate with the air supply path 13 or the first exhaust path 15, respectively.
  • gases passing through the two flow paths are not mixed, and sensible heat is exchanged through an aluminum foil or a synthetic resin film.
  • the air supply path 13 includes a distribution unit (distribution means) 31 that distributes the air flowing through the air supply path 13 to the downstream side of the first sensible heat exchanger 27, and the second exhaust path 17 is provided in the distribution unit 31. Is connected.
  • a humidifier (humidifying means) 33 and a second sensible heat exchanger (second sensible heat exchange means) 35 are arranged in this order from the distributor 31 toward the discharge port 17A.
  • the humidifier 33 is impregnated with water supplied to a non-woven fabric formed in a honeycomb shape. The air is passed through the non-woven fabric to humidify the air by containing moisture.
  • the second sensible heat exchanger 35 cools the other air by sensible heat exchange between one of the air distributed by the distributor 31 and humidified by the humidifier 33 and the other distributed air. It is. Similarly to the first sensible heat exchanger 27, the second sensible heat exchanger 35 has two flow paths 35A and 35B that are orthogonal to each other. Since the other configuration is the same as that of the first sensible heat exchanger 27, the description thereof is omitted. In the second sensible heat exchanger 35, since the humidified air flowing through the second exhaust path 17 and the dehumidified air flowing through the air supply path 13 exchange sensible heat, the dehumidified air has the latent heat of water. And is supplied into the room through the discharge port 13B. In this case, the second sensible heat exchanger 35 does not mix the gas passing through the two flow paths, so that moisture does not move into the dehumidified air and can prevent an increase in humidity.
  • the distribution ratio by the distribution unit 31, that is, one air amount flowing through the second exhaust path 17 (flow path 35A) and the other air amount flowing through the air supply path 13 (flow path 35A).
  • a configuration for controlling the ratio is provided.
  • the outside air processing apparatus 1 includes temperature sensors 37A and 37B that measure the air temperature disposed at the outlets of the flow paths 35A and 35B of the second sensible heat exchanger, and the discharge port 13B of the air supply path 13.
  • the blower fan 39 is provided with an inverter 41 for setting the rotational speed of the blower fan 39, and a controller (control means) 43 for controlling the rotational speed of the blower fan 39 via the inverter 41.
  • the blower fan 39 and the controller 43 constitute a distribution unit including the distribution unit 31.
  • the temperature sensors 37A and 37B described above are connected to the controller 43, and the controller 43 controls the rotational speed of the blower fan 39 based on the measured temperatures of the temperature sensors 37A and 37B.
  • FIG. 2 is a diagram showing the relationship between the ratio of the supply air SA amount to the sucked outside air OA amount and the cooling capacity.
  • the exhaust (EA) temperature Td is the air temperature at the discharge port 17A (point F) of the second exhaust passage 17
  • the supply (SA) temperature Ts is the discharge port 13B (point) of the supply passage 13.
  • the air temperature in E) and the air temperature after humidification are the air temperature (point D) between the humidifier 33 and the second sensible heat exchanger 35, respectively, and the amount of supplied SA relative to the amount of outside air OA sucked The value when the ratio is changed between 10% and 90% is measured.
  • the exhaust temperature Td is measured by the temperature sensor 37B
  • the supply air temperature Ts is measured by the temperature sensor 37A.
  • the cooling capacity is a value obtained by multiplying the amount of supplied air supplied indoors by the temperature difference between the outside air temperature and the supplied air temperature Ts.
  • the supply air temperature Ts remains unchanged at a value lower than 25 ° C. until the ratio of the supply air SA amount to the sucked outside air OA amount is 50%, but suddenly exceeds 50%. It can be seen that it rises.
  • the ratio of the supply air SA amount to the sucked outside air OA amount is set low, a large amount of the external air OA is sucked in order to secure the supply air SA amount.
  • the cost for driving 21 increases.
  • the ratio of the supply air SA amount to the intake outside air OA amount is 45 to 50%, that is, approximately. It turned out to be evenly distributed.
  • the desiccant rotor 25 is an operation in which moisture in the air is adsorbed by the dehumidifying agent and in which the humidity is released from the dehumidifying agent without any enthalpy change, and the relative humidity after release and the relative humidity after adsorption are the same have.
  • the temperature of each fluid rises or falls to 90% of the temperature difference between the high temperature fluid and the low temperature fluid.
  • the humidifier 33 has a humidification efficiency of up to 90% relative humidity.
  • a dry bulb temperature of 35 ° C. and a wet bulb temperature of 24 ° C. which are ISO and JIS rated cooling conditions in the air conditioner, are described as an example.
  • the relative humidity at points A and G is 40.3%.
  • the dry bulb temperature indicated by point B is 44.3 ° C./wet bulb temperature 24.1 ° C./relative humidity 18.3%.
  • the dry-bulb temperature is rising because it is heated when passing through the desiccant rotor 25.
  • the dehumidified air is subjected to sensible heat exchange with the outside air OA in the first sensible heat exchanger 27, as indicated by a point C, the dry bulb temperature is 35.9 ° C./the wet bulb temperature is 21.7 ° C./relative.
  • the humidity is 28.6%, and it is slightly cooled by the outside air.
  • the air that has passed through the first sensible heat exchanger 27 is distributed into two by the distributor 31.
  • one air amount flowing through the second exhaust path 17 and the other air amount flowing through the air supply path 13 are distributed substantially evenly (50%: 50%).
  • the dry bulb temperature is 23.0 ° C./the wet bulb temperature is 21.7 ° C./the relative humidity is 90.0%.
  • the dry air that has passed through the desiccant rotor 25 and the first sensible heat exchanger 27 is distributed into two, and the distributed air is humidified and used to cool the other air.
  • the outside air at points A and G is humidified as it is (for example, point K: dry bulb temperature 25.5 ° C./humidity). (Bulb temperature 24.0 ° C./relative humidity 90.0%), the wet bulb temperature after humidification can be reduced by 2.5 ° C. and wet bulb temperature 3.3 ° C.
  • the relative humidity at point E appears to be 55.6%, which is higher than the relative humidity at 40.3% of outside air (point A)
  • the absolute humidity at point A is 0.01423 kg / Since the absolute humidity at point E is reduced to 0.01055 kg / kg (DA) while it is kg (DA), air having a lower temperature and lower humidity than the outside air can be supplied indoors. .
  • the dry air that has passed through the desiccant rotor 25 and the first sensible heat exchanger 27 is distributed into two, and this distributed air is humidified and used to cool the other air. Therefore, the cooling efficiency of the other air can be increased by causing the second sensible heat exchanger 35 to perform sensible heat exchange between the one air having a low dry bulb temperature and a low wet bulb temperature and the other air. it can.
  • the point F one air passing through the second sensible heat exchanger 35 becomes dry bulb temperature 34.6 ° C./wet bulb temperature 24.9 ° C./relative humidity 46.0% and is discharged outside the room. Is done.
  • the outside air that has passed through the first sensible heat exchanger 27 rises to a dry bulb temperature of 43.4 ° C./wet bulb temperature of 26.2 ° C./relative humidity of 25.6% as indicated by point H, Heated by the heater 29, the dry bulb temperature shown at point I is 50.0 ° C./wet bulb temperature 27.7 ° C./relative humidity 18.4%.
  • the heated air passes through the regeneration region 25C of the desiccant rotor 25, and as indicated by point J, the dry bulb temperature is 41.0 ° C./the wet bulb temperature is 27.6 ° C./the relative humidity is 36.6%. It is discharged outside.
  • the air supply path 13 that sucks outside air and supplies the air into the room
  • the desiccant rotor 25 that dehumidifies the air flowing through the air supply path 13, and the dehumidified air as the outside air.
  • the first sensible heat exchanger 27 that exchanges heat
  • the distribution unit 31 that distributes the sensible heat-exchanged air into two
  • the humidifier 33 that humidifies one of the distributed air
  • the outside air can be dehumidified and cooled with a simple configuration including the second sensible heat exchanger 35 that performs sensible heat exchange with the other air and cools the other air.
  • the outside air can be continuously dehumidified and cooled. Furthermore, the power for operating the outside air introduction fan 21 by using exhaust heat generated by burning fuel such as gas or oil as a heating source of the heater 29 or heat obtained by natural energy such as solar heat or geothermal heat. As long as there is water supplied to the humidifier 33, air having a lower temperature and lower absolute humidity than the outside air can be obtained. Further, in the second sensible heat exchanger 35, the other air supplied to the room and the humidified air are not mixed. For this reason, the germs mixed in the water for humidification are not mixed in the air supplied indoors, and clean and safe air can be supplied indoors.
  • the amount of one air flowing through the second exhaust path 17 and the other air amount flowing through the air supply path 13 in the distribution unit 31 are substantially equal (50%). : 50%) is important.
  • the supply air temperature Ts remains flat at a value lower than 25 ° C. until the ratio of the supply air SA amount to the sucked outside air OA amount is 50%, but exceeds 50%. And rises rapidly.
  • the exhaust temperature Td of one of the humidified air that contributes to the cooling of the supply air contrary to the supply air temperature Ts, rapidly increases until the ratio of the supply air SA amount to the sucked outside air OA amount is 50%.
  • the controller 43 controls the number of revolutions of the blower fan 39 based on the temperature of each path outlet of the second sensible heat exchanger 35 based on the above-described tendency.
  • the controller 43 obtains the maximum temperature difference ⁇ Tmax of the exhaust gas temperature difference ⁇ T between the exhaust gas temperature Td and the supply air temperature Ts in the initial operation when the operation of the outside air processing device 1 is started.
  • the controller 43 operates the blower fan 39 at the reference rotation speed Rf while the outside air introduction fan 21 is operating at a predetermined rotation speed, and measures the supply air temperature Ts 1 by the temperature sensor 37A.
  • the exhaust gas temperature Td 1 is measured by the temperature sensor 37B.
  • a temperature difference ⁇ T 1 between the measured exhaust temperature Td 1 and the supply air temperature Ts 1 is calculated.
  • the controller 43 causes the blower fan 39 to operate at a predetermined rotational speed Rf + ⁇ R that is larger than the reference rotational speed Rf by a predetermined rotational speed ⁇ R.
  • the supply air temperature Ts 2 and the exhaust gas temperature Td 2 at this time are measured.
  • the controller 43 calculates a temperature difference ⁇ T 2 between the measured exhaust gas temperature Td 2 and the supply air temperature Ts 2 , and a difference ( ⁇ T 2 ⁇ T) between the current temperature difference ⁇ T 2 and the previous temperature difference ⁇ T 1. It is determined whether 1 ) is positive, that is, greater than 0.
  • the controller 43 determines, as described above.
  • the rotational speed of the blower fan 39 is operated at a predetermined rotational speed Rf + n ⁇ R (n is 2, 3,... N) that is further increased by the rotational speed ⁇ R, and the temperature difference ⁇ T n at this time is The process is continued until the difference from the previously calculated temperature difference ⁇ T n ⁇ 1 is negative, that is, smaller than 0.
  • the temperature difference ⁇ T n at this time is set as the maximum temperature difference ⁇ Tmax, and the setting operation for the maximum temperature difference is completed.
  • the rotation speed of the blower fan 39 is set using the set maximum temperature difference ⁇ Tmax.
  • the controller 43 operates the blower fan 39 at the reference rotation speed Rf while the outside air introduction fan 21 is operating at a predetermined rotation speed, and measures the supply air temperature Ts 1 by the temperature sensor 37A. Then, the exhaust gas temperature Td 1 is measured by the temperature sensor 37B. Then, a temperature difference ⁇ T 1 between the measured exhaust temperature Td 1 and the supply air temperature Ts 1 is calculated.
  • the controller 43 calculates an additional rotation number ⁇ R 1 calculated by multiplying a difference ( ⁇ Tmax ⁇ T 1 ) between the set maximum temperature difference ⁇ Tmax and the calculated temperature difference ⁇ T 1 by a predetermined coefficient K,
  • the blower fan 39 is operated at a rotational speed Rf 1 (Rf + ⁇ R 1 ) obtained by adding the additional rotational speed ⁇ R 1 to the reference rotational speed Rf.
  • a predetermined time 5 minutes in the present embodiment
  • the controller 43 adds a predetermined coefficient K to the difference ( ⁇ Tmax ⁇ T 2 ) between the set maximum temperature difference ⁇ Tmax and the calculated temperature difference ⁇ T 2 , the current temperature difference ⁇ T 2 and the previous temperature difference ⁇ T 1 .
  • the blower fan 39 provided at the discharge port 13B of the air supply path 13 and the exhaust temperature Td and the supply air temperature Ts, which are outlet temperatures of the second sensible heat exchanger 35, are used.
  • the controller 43 that controls the amount of air blown by the blower fan 39, the distribution amount of air flowing through each path of the second sensible heat exchanger 35 can be simplified without actually measuring the amount of air supplied to the room. Can be adjusted.
  • the other air is The second sensible heat exchanger 35 can be cooled to the maximum.
  • FIG. 4 is a schematic diagram of the outside air processing apparatus 100 according to the second embodiment.
  • the same components as those in the outside air processing device 1 according to the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
  • the outside air processing device 100 has a distribution ratio by the distribution unit 31, that is, one air amount flowing through the second exhaust path 17 (flow path 35A) and the other air amount flowing through the air supply path 13 (flow path 35A). A configuration for controlling the ratio is provided.
  • the outside air processing apparatus 100 is arranged on the upstream side of the humidifier 33, and the blower fan 113 disposed in the opening 110 that communicates the second exhaust path 17 and the air supply path 13, and the rotation of the blower fan 113.
  • An inverter 141 for setting the number and a controller (control means) 143 for controlling the rotation speed of the blower fan 113 via the inverter 141 are provided.
  • the blower fan 113 and the controller 143 constitute a distribution unit including the distribution unit 31.
  • the blower fan 113 is configured to be able to change the blowing direction between the second exhaust path 17 and the air supply path 13 according to the rotation direction.
  • the temperature sensors 37A and 37B described above are connected to the controller 143, and the controller 143 controls the rotational speed of the blower fan 113 based on the measured temperatures of the temperature sensors 37A and 37B.
  • the controller 143 sets the maximum temperature difference ⁇ Tmax of the exhaust gas temperature difference ⁇ T between the exhaust gas temperature Td and the supply air temperature Ts at the initial operation time when the operation of the outside air processing device 100 is started. Ask. Since the calculation method of the maximum temperature difference ⁇ Tmax of the exhaust air temperature difference ⁇ T is the same as that in the first embodiment, the description thereof is omitted.
  • the rotation speed of the blower fan 113 is set using the set maximum temperature difference ⁇ Tmax.
  • the controller 143 causes the air to flow from the second exhaust path 17 to the air supply path 13 at the reference rotation speed Rf while the outside air introduction fan 21 is operating at a predetermined rotation speed.
  • the temperature sensor 37A measures the supply air temperature Ts 1 and the temperature sensor 37B measures the exhaust gas temperature Td 1 . Then, a temperature difference ⁇ T 1 between the measured exhaust temperature Td 1 and the supply air temperature Ts 1 is calculated.
  • the controller 143 calculates an additional rotation number ⁇ R 1 calculated by multiplying a difference ( ⁇ Tmax ⁇ T 1 ) between the set maximum temperature difference ⁇ Tmax and the calculated temperature difference ⁇ T 1 by a predetermined coefficient K,
  • the blower fan 113 is operated at a rotational speed Rf 1 (Rf + ⁇ R 1 ) obtained by adding the additional rotational speed ⁇ R 1 to the reference rotational speed Rf.
  • a predetermined time 5 minutes in the present embodiment
  • the controller 143 adds a predetermined coefficient K to the difference ( ⁇ Tmax ⁇ T 2 ) between the set maximum temperature difference ⁇ Tmax and the calculated temperature difference ⁇ T 2 , the current temperature difference ⁇ T 2, and the previous temperature difference ⁇ T 1 .
  • the rotational direction and the rotational speed (air flow rate) of the blower fan 113 can be finely adjusted, and the amount of one air flowing through the second exhaust path 17
  • the amount of distribution between the (exhaust air EA) and the other amount of air flowing through the air supply path 13 (supply air SA) can be kept substantially equal (50%: 50%), and thus the second sensible heat exchanger.
  • the cooling capacity at 35 can be maximized.
  • the blower fan 113 disposed in the opening 110 communicating the second exhaust path 17 and the air supply path 13, and the second sensible heat exchanger 35 Since the controller 143 for controlling the rotational speed of the blower fan 113 is provided based on the exhaust temperature Td and the supply air temperature Ts, which are outlet temperatures, it is possible to perform the first measurement without measuring the amount of air actually supplied into the room. 2 The distribution amount of the air flowing through each path of the sensible heat exchanger 35 can be easily adjusted.
  • FIG. 5 is a schematic diagram of an outside air processing apparatus 200 according to the third embodiment.
  • the same components as those in the outside air processing apparatus 1 according to the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
  • the outside air processing device 200 has a distribution ratio by the distribution unit 31, that is, one air amount flowing through the second exhaust path 17 (flow path 35A) and the other air amount flowing through the air supply path 13 (flow path 35A). A configuration for controlling the ratio is provided.
  • the outside air processing apparatus 200 includes an exhaust damper 210 provided in the second exhaust path 17, an air supply damper 211 provided in the air supply path 13, the exhaust damper 210, and the air supply A damper operating motor 213 that operates the damper 211, an inverter 241 that sets the rotational speed of the damper operating motor 213, and a controller (control means) 243 that controls the rotational speed of the damper operating motor 213 via the inverter 241.
  • the exhaust damper 210 and the air supply damper 211 are operated by a single damper operation motor 213, and the exhaust damper 210 and the air supply damper 211 perform the reverse operations. That is, when the exhaust damper 210 operates in the opening direction, the air supply damper 211 operates in the closing direction, and the distribution ratio of the air flowing through the second exhaust path 17 and the air supply path 13 is controlled. Is done.
  • the controller 243 obtains the maximum temperature difference ⁇ Tmax of the exhaust gas supply temperature difference ⁇ T between the exhaust temperature Td and the supply air temperature Ts in the initial operation when the operation of the outside air processing device 1 is started. First, the controller 243 sets the exhaust damper 210 and the air supply damper 211 to the reference opening position Dv while the outside air introduction fan 21 is operating at a predetermined rotational speed, and supplies the temperature by the temperature sensor 37A. The air temperature Ts 1 is measured, and the exhaust temperature Td 1 is measured by the temperature sensor 37B. Then, a temperature difference ⁇ T 1 between the measured exhaust temperature Td 1 and the supply air temperature Ts 1 is calculated.
  • the reference opening position Dv of the exhaust damper 210 and the air supply damper 211 refers to a position set to an opening of 70% with respect to the opening areas of the second exhaust path 17 and the air supply path 13. .
  • the controller 243 operates the damper operating motor 213 so that the air supply damper 211 has a predetermined opening (for example, a reference opening position Dv). 5%) a predetermined opening Dv + ⁇ D opened by ⁇ D, and a predetermined opening Dv ⁇ D in which the exhaust damper 210 is closed by a predetermined opening (5%) ⁇ D from the reference opening position Dv.
  • the supply air temperature Ts 2 and the exhaust gas temperature Td 2 are respectively measured. Then, the controller 243 calculates a temperature difference ⁇ T 2 between the measured exhaust temperature Td 2 and the supply air temperature Ts 2 , and a difference ( ⁇ T 2 ⁇ T) between the current temperature difference ⁇ T 2 and the previous temperature difference ⁇ T 1. It is determined whether 1 ) is positive, that is, greater than 0.
  • the opening degree of the air supply damper 211 is further set to a predetermined opening degree Dv + n ⁇ D (n is 2, 3,... N) opened by a predetermined opening degree ⁇ D, and the exhaust damper
  • the opening 210 is further closed by a predetermined opening ⁇ D, which is a predetermined opening Dv ⁇ n ⁇ D (n is 2, 3,...
  • the temperature difference ⁇ T n at this time is set as the maximum temperature difference ⁇ Tmax, and the setting operation for the maximum temperature difference is completed.
  • the opening degree of the supply damper 211 and the exhaust damper 210 is set using the set maximum temperature difference ⁇ Tmax.
  • the opening degree of the air supply damper 211 will be described.
  • the controller 243 sets the supply damper 211 to the reference opening position Dv while the outside air introduction fan 21 is operating at a predetermined rotation speed, and sets the supply air temperature Ts 1 by the temperature sensor 37A.
  • the exhaust temperature Td 1 is measured by the temperature sensor 37B. Then, a temperature difference ⁇ T 1 between the measured exhaust temperature Td 1 and the supply air temperature Ts 1 is calculated.
  • the controller 243 calculates a damper operation amount ⁇ D 1 calculated by multiplying a difference ( ⁇ Tmax ⁇ T 1 ) between the set maximum temperature difference ⁇ Tmax and the calculated temperature difference ⁇ T 1 by a predetermined coefficient K, and this damper operation Let the amount ⁇ D 1 be the opening degree Dv 1 (Dv + ⁇ D 1 ) obtained by adding the amount ⁇ D 1 to the reference opening position Dv of the supply damper 211. Subsequently, when a predetermined time (5 minutes in the present embodiment) elapses from the previous measurement, the supply air temperature Ts 2 and the exhaust gas temperature Td 2 at this time are measured, and the measured exhaust gas temperature Td 2 and supply air temperature Ts are measured.
  • the controller 243 adds a predetermined coefficient K to the difference between the set maximum temperature difference ⁇ Tmax and the calculated temperature difference ⁇ T 2 ( ⁇ Tmax ⁇ T 2 ), the current temperature difference ⁇ T 2 and the previous temperature difference ⁇ T 1 .
  • a damper operation amount ⁇ D 2 calculated by multiplying the difference ( ⁇ T 2 ⁇ T 1 ) by a positive / negative sign is calculated, and the damper operation amount ⁇ D 2 is added to the previous opening Dv 1 to obtain an opening Dv 2 (Dv
  • the damper operation motor 213 is operated so that 1 + ⁇ D 2 ).
  • the calculated damper operation amount ⁇ D n is used as the previous opening degree Dv. Subtract from n-1 . Also, when [Delta] T n calculated is larger than the .DELTA.Tmax that is set, it sets the [Delta] T n as a new maximum temperature difference .DELTA.Tmax. By performing such control at predetermined time intervals (5 minutes), the opening degree (air flow rate) of the supply damper 211 and the exhaust damper 210 can be finely adjusted and flows through the second exhaust path 17. The distribution amount of one air amount (exhaust EA) and the other air amount (supply air SA) flowing through the air supply path 13 can be kept substantially equal (50%: 50%). The cooling capacity of the sensible heat exchanger 35 can be maximized.
  • the exhaust damper 210 provided in the second exhaust path 17, the supply damper 211 provided in the supply path 13, and the outlet temperatures of the second sensible heat exchanger 35 Since the controller 243 for controlling the opening degree of the exhaust damper 210 and the supply damper 211 is provided based on the exhaust temperature Td and the supply air temperature Ts, the amount of air actually supplied into the room is not measured. In both cases, the distribution amount of the air flowing through each path of the second sensible heat exchanger 35 can be easily adjusted.
  • FIG. 6 is a schematic diagram of an outside air processing device 300 according to the fourth embodiment.
  • the same components as those in the outside air processing device 1 according to the above-described embodiment are denoted by the same reference numerals and description thereof is omitted.
  • the outside air processing apparatus 300 has a distribution ratio by the distribution unit 31, that is, one air amount flowing through the second exhaust path 17 (flow path 35A) and the other air amount flowing through the air supply path 13 (flow path 35A).
  • a configuration for controlling the ratio is provided.
  • the outside air processing apparatus 300 includes a shielding plate 310 that is provided in the second exhaust path 17 and the air supply path 13 and shields the paths, and the shielding plate 310 communicates with the second exhaust path 17.
  • An exhaust side passage window 311 and an air supply side passage window 313 communicating with the air supply path 13 are provided in parallel.
  • the opening area of each passing window is set to an area in which the amount of air flowing through the air supply path 13 is 45 to 50% of the amount of outside air that has been inspected in advance.
  • the area of the passage window cannot be changed following the change in the outside air temperature, but the air that has been dehumidified and cooled can be supplied indoors with a simple configuration.
  • the first exhaust path 15 is configured to suck outside air as regeneration air, but may be configured to suck indoor air instead.
  • the first sensible heat exchanger 27 performs sensible heat exchange between the room air and the dehumidified air. The temperature of the dehumidified air can be further reduced, and as a result, the supply air temperature can be reduced.
  • the desiccant rotor is employed as the dehumidifying means, but other configurations may be employed as long as the sucked outside air can be dehumidified.
  • the orthogonal sensible heat exchanger is adopted as the first sensible heat exchange means and the second sensible heat exchange means, but a sensible heat rotor may be adopted instead.
  • the heater 29 that is heated with warm water is used as the heating means, but it may be heated with electricity, steam, or the like.

Abstract

L'invention vise à procurer un dispositif de traitement d'air extérieur avec lequel de l'air ayant une température inférieure et une humidité inférieure à celles de l'air extérieur peut être fourni à l'intérieur d'une pièce à l'aide d'une configuration simple. A cet effet, l'invention porte sur un dispositif de traitement d'air extérieur, lequel dispositif comporte : un passage d'alimentation en air (13) qui aspire de l'air extérieur et qui fournit l'air extérieur à l'intérieur d'une pièce; un rotor de déshydratation (25), qui retire de l'humidité à partir de l'air s'écoulant dans ce passage d'alimentation en air (13); un premier échangeur de chaleur sensible (27) qui effectue un échange de chaleur sensible entre l'air déshydraté et l'air extérieur; une unité de diviseur (31) qui divise l'air qui a subi un échange de chaleur sensible en deux courants; un humidificateur (33) qui humidifie l'un des courants d'air divisés; et un second échangeur de chaleur sensible (35) qui refroidit l'autre courant d'air divisé en effectuant un échange de chaleur sensible entre l'air humidifié et cet autre courant d'air. L'air qui est refroidi par le second échangeur de chaleur sensible (35) est fourni à l'intérieur de la pièce.
PCT/JP2012/068785 2011-08-10 2012-07-25 Dispositif de traitement d'air extérieur WO2013021817A1 (fr)

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JP2011174649A JP2013036705A (ja) 2011-08-10 2011-08-10 外気処理装置
JP2011-174649 2011-08-10

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CN107940621A (zh) * 2017-12-22 2018-04-20 广东美的制冷设备有限公司 除湿机
CN109922893A (zh) * 2016-12-14 2019-06-21 株式会社大气社 涂装用干燥设备
US10458603B2 (en) 2013-11-05 2019-10-29 Signify Holding B.V. Tubular lighting assembly with elastic elongated substrate and method of manufacturing a tubular lighting assembly with elastic elongated substrate
EP3936772A4 (fr) * 2019-03-05 2022-03-23 Mitsubishi Electric Corporation Dispositif de traitement de l'air
CN107940621B (zh) * 2017-12-22 2024-04-26 广东美的制冷设备有限公司 除湿机

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KR101573759B1 (ko) * 2014-04-18 2015-12-02 주식회사 경동나비엔 제습 냉방 장치

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US10458603B2 (en) 2013-11-05 2019-10-29 Signify Holding B.V. Tubular lighting assembly with elastic elongated substrate and method of manufacturing a tubular lighting assembly with elastic elongated substrate
CN109922893A (zh) * 2016-12-14 2019-06-21 株式会社大气社 涂装用干燥设备
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CN109922893B (zh) * 2016-12-14 2021-06-08 株式会社大气社 涂装用干燥设备
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CN107940621A (zh) * 2017-12-22 2018-04-20 广东美的制冷设备有限公司 除湿机
CN107940621B (zh) * 2017-12-22 2024-04-26 广东美的制冷设备有限公司 除湿机
EP3936772A4 (fr) * 2019-03-05 2022-03-23 Mitsubishi Electric Corporation Dispositif de traitement de l'air

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