WO2012147153A1 - Adsorption dehumidifier - Google Patents

Adsorption dehumidifier Download PDF

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Publication number
WO2012147153A1
WO2012147153A1 PCT/JP2011/060103 JP2011060103W WO2012147153A1 WO 2012147153 A1 WO2012147153 A1 WO 2012147153A1 JP 2011060103 W JP2011060103 W JP 2011060103W WO 2012147153 A1 WO2012147153 A1 WO 2012147153A1
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air
desorption
zone
adsorption
desorption zone
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PCT/JP2011/060103
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French (fr)
Japanese (ja)
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金　偉力
川上　由基人
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株式会社西部技研
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Priority to PCT/JP2011/060103 priority Critical patent/WO2012147153A1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/26—Drying gases or vapours
    • B01D53/261—Drying gases or vapours by adsorption
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/02—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols by adsorption, e.g. preparative gas chromatography
    • B01D53/06—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols by adsorption, e.g. preparative gas chromatography with moving adsorbents, e.g. rotating beds
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D2259/00—Type of treatment
    • B01D2259/40—Further details for adsorption processes and devices
    • B01D2259/40083—Regeneration of adsorbents in processes other than pressure or temperature swing adsorption
    • B01D2259/40088—Regeneration of adsorbents in processes other than pressure or temperature swing adsorption by heating
    • B01D2259/4009—Regeneration of adsorbents in processes other than pressure or temperature swing adsorption by heating using hot gas

Definitions

  • the present invention relates to an adsorption dehumidifier capable of supplying low dew point air with low temperature desorption air.
  • Low dew point air with an absolute humidity of 1.5 g / kg or less is required in lithium battery manufacturing factories and certain pharmaceutical factories, and refrigeration dehumidifiers are insufficient to create such an environment.
  • An adsorption dehumidifier having a rotor is used.
  • the refrigeration dehumidifier is more energy efficient than the adsorption dehumidifier, and it is necessary to take energy saving measures for the adsorption dehumidifier. If the temperature of the desorption air of the dehumidification rotor can be lowered in response to such a requirement, waste heat can be used as a heating energy source for the desorption air, and as a result, the energy saving effect is enhanced.
  • Patent Document 1 Such a requirement required solving the trade-off problem of lowering the desorption temperature while increasing the adsorption capacity of the dehumidifying rotor.
  • Patent Document 1 has two adsorption zones, the adsorption zone is advanced while removing the heat of adsorption, and the desorption zones are further divided into two stages, and a heater is provided in each desorption zone. It is provided.
  • Patent Document 2 branches a part of the dehumidified dry air and mixes it with the air that has exited the purge zone to form desorbed air.
  • the problem to be solved is to enable desorption at a lower temperature. It also simplifies the air line and reduces air resistance, thereby reducing the energy consumed by the fan.
  • the main feature of the present invention is to provide an adsorption type dehumidifier capable of supplying air having a low dew point even with low-temperature desorption air.
  • the adsorption type dehumidifier of the present invention is provided with two desorption zones, desorbing through the outside air in the first desorption zone containing a lot of moisture, and desorbing by flowing dry air into the desorption zone in the latter stage with low humidity. Therefore, in the first-stage desorption zone, the amount of desorbed water is large even when outside air is used, and in the latter-stage desorption zone, there is little moisture, but desorption is performed using dry air.Therefore, the desorption is sufficiently performed even at a low desorption temperature. is there.
  • the temperature of the desorption air may be low, waste heat can be used as a heat source for the heater.
  • dry air can be supplied with very little energy.
  • the cooling water of the engine of a diesel generator can be passed through a radiator, and this radiator can be used as a heater.
  • the discarded energy can be used as the main driving energy of the adsorption dehumidifier of the present invention, and the energy saving effect is high.
  • waste heat is always generated from the diesel generator, and the waste heat is thrown away, so there is a lot of energy wasted, but with the desorption air at low temperature like the adsorption dehumidifier of the present invention. Anything that can supply air with a low dew point can make use of such discarded energy.
  • FIG. 1 is a flowchart in Example 1 of an adsorption dehumidifier.
  • FIG. 2 is an air diagram in the embodiment of the adsorption type dehumidifier.
  • FIG. 3 is a flowchart in Example 2 of the adsorption type dehumidifier.
  • the adsorption type dehumidifier of the present invention cools and dehumidifies the outside air and passes it through the adsorption zone of the dehumidification rotor, and provides two desorption zones.
  • the first stage desorption zone containing a lot of moisture desorbs through the outside air, Since the desorption zone in the rear stage with a small amount of dry air is desorbed by flowing dry air, the purpose of supplying low dew point air with low temperature desorption air is realized with the minimum number of parts, and the energy saving effect is enhanced.
  • Numeral 1 is a dehumidifying rotor which carries an adsorbent such as silica gel or zeolite, and many techniques are already known.
  • the dehumidifying rotor 1 is rotationally driven by a geared motor (not shown) in the direction of the arrow in FIG.
  • the dehumidifying rotor 1 is divided into an adsorption zone 2, a first desorption zone 3, and a second desorption zone 4.
  • the area ratio of each zone of the adsorption zone 2, the first desorption zone 3, and the second desorption zone 4 is 5: 3: 1.
  • OA outside air
  • 6 is a cooler, for example, an evaporator connected to a refrigerator.
  • Reference numerals 7 and 8 denote a first heater and a second heater, respectively, for example, a condenser of a refrigerator connected to the cooler 6 or a radiator through which a coolant of a diesel generator flows.
  • the blower 5 sucks OA 1, and the air coming out of it passes through the cooler 6 and enters the adsorption zone 2 of the dehumidifying rotor 1.
  • Part of the air that has passed through the adsorption zone 2 of the dehumidifying rotor 1 is branched, and the remaining air is supplied as product air (hereinafter referred to as “DA”) to a dry room (not shown).
  • DA product air
  • the branched air passes through the second heater 8 and enters the second desorption zone 4, and the air that has passed through the second desorption zone 4 returns to the suction side of the blower 5.
  • OA 2 passes through the first heater 7, passes through the first desorption zone 3 of the dehumidifying rotor 1, is sucked into the suction side of the blower 9, and is discharged into the atmosphere as exhaust (hereinafter referred to as “EA”).
  • EA exhaust
  • the air volume ratio passing through each zone is the same as the area ratio of each zone 5: 3: 1. That is, the area of the second desorption zone 4 is smaller than the area of the first desorption zone 3.
  • the adsorption dehumidifier of the present invention has the above-described configuration, and the operation thereof will be described below.
  • all temperatures are expressed in degrees Celsius.
  • the air condition of OA was 35 degrees and relative humidity 53 percent (absolute humidity 18.6 g / kg).
  • This OA was sent to the cooler 6 by the blower 5 and dehumidified by condensation.
  • the air condition was 12 degrees and the absolute humidity was 8.3 g / kg.
  • the cooled air passes through the adsorption zone 2 of the dehumidifying rotor 1 and is further adsorbed and dehumidified. At this time, the temperature rose due to the heat of adsorption, and the air became 32 ° C. and the absolute humidity was 1.2 g / kg.
  • This dry air is supplied to the dry room as product air (hereinafter referred to as “DA”).
  • DA product air
  • the change in air conditions as it passes through the adsorption zone 2 is indicated by the line “Process” in FIG.
  • the OA2 is heated to 60 degrees by the first heater 7 and sent to the first desorption zone 3 of the dehumidifying rotor 1.
  • the first desorption zone 3 is the portion with the most moisture, and a large amount of moisture is desorbed even when the temperature of the desorption air is 60 degrees. That is, air with an absolute humidity of 18.6 g / kg is 25.1 g / kg.
  • the air condition passing through the first desorption zone 3 is represented by the line “Regeneration 1” in FIG.
  • the air leaving the first desorption zone 3 has a high moisture content and is released to the atmosphere as exhaust (hereinafter referred to as “EA”).
  • a part of the dry air that has passed through the adsorption zone 2 is branched, heated by the second heater 8, and sent to the second desorption zone 4.
  • the humidity of the dehumidifying rotor 1 is considerably reduced.
  • the absolute humidity of the air sent to the second desorption zone 4 is as extremely low as 1.2 g / kg, desorption proceeds further.
  • the air changes from a temperature of 60 degrees and an absolute humidity of 1.2 g / kg to a temperature of 23.6 degrees and an absolute humidity of 14.2 g / kg. This change is indicated by the line “Regeneration 2” in FIG.
  • the temperature of both the first heater 7 and the second heater 8 is 60 degrees, air having an absolute humidity of 1.2 g / kg can be supplied as DA. If it is 60 degrees, many waste heat sources can be used as waste heat. For example, the temperature of the coolant of a diesel generator engine is about 80 degrees, which is sufficiently usable. Also, there are refrigerators with a condenser of about 60 degrees. Furthermore, solar water heaters can supply hot water at 60 degrees even in spring and autumn, and such heat sources can also be used.
  • the second desorption zone 4 having a small remaining amount of moisture can be sufficiently desorbed even if the area is smaller than the area of the first desorption zone 3, thereby reducing the amount of air passing through the second desorption zone 4. It can be reduced and the energy saving effect is higher.
  • reference numeral 10 denotes a switching valve, which switches between the air that has exited the second desorption zone 4 of the dehumidifying rotor 1 flowing to the suction side of the blower 9 or the suction side of the blower 5.
  • the operation is exactly the same as in the first embodiment.
  • the absolute humidity of OA is lower than the absolute humidity of the air leaving the second desorption zone 4
  • the air leaving the second desorption zone 4 was released into the atmosphere as EA rather than being circulated to the adsorption zone 2.
  • the humidity of DA is lower. That is, the switching valve 10 can be switched according to the weather conditions to supply the air with the lowest humidity.
  • the adsorption type dehumidifier of the present invention can supply air with a low dew point even if low temperature waste heat is used, and can exhibit an extremely high energy saving effect.

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  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Drying Of Gases (AREA)

Abstract

The present invention is mainly characterized in providing an adsorption dehumidifier capable of supplying low-dew-point air even using low-temperature desorption air. This adsorption dehumidifier is configured to cool and dehumidify external air and channel the resulting air through an adsorption zone (2) of a dehumidifying rotor (1). The dehumidifying rotor (1) is provided with two desorption zones: a high-humidity first desorption zone (3) and a low-humidity second desorption zone (4). Outside air is heated and channeled through the upstream first desorption zone (3) and desorbed, and dry air exiting the adsorption zone (2) is channeled through the downstream second desorption zone (4) and desorbed. It is thus possible, using a minimal number of components, to supply low-dew-point air using low-temperature desorption air, and to conserve energy more effectively.

Description

吸着式除湿機Adsorption dehumidifier
　本発明は、低い温度の脱着空気で低露点の空気の供給が可能な吸着式除湿機に関するものである。 The present invention relates to an adsorption dehumidifier capable of supplying low dew point air with low temperature desorption air.
　リチウム電池の製造工場や、特定の製薬工場などで絶対湿度が１．５ｇ/ｋｇ以下の低露点空気が必要であり、このような環境を作るために冷凍式除湿機では不十分であり、除湿ロータを有する吸着式除湿機が用いられている。 Low dew point air with an absolute humidity of 1.5 g / kg or less is required in lithium battery manufacturing factories and certain pharmaceutical factories, and refrigeration dehumidifiers are insufficient to create such an environment. An adsorption dehumidifier having a rotor is used.
　しかし、一般には冷凍式除湿機の方が吸着式除湿機よりもエネルギー効率が高く、吸着式除湿機に省エネルギーの対策をする必要がある。このような要求に対して、除湿ロータの脱着空気の温度を低くする事ができれば、脱着空気の加熱エネルギー源として、廃熱を活用することができ、結果として省エネルギー効果が高くなる。 However, in general, the refrigeration dehumidifier is more energy efficient than the adsorption dehumidifier, and it is necessary to take energy saving measures for the adsorption dehumidifier. If the temperature of the desorption air of the dehumidification rotor can be lowered in response to such a requirement, waste heat can be used as a heating energy source for the desorption air, and as a result, the energy saving effect is enhanced.
　このような要求は、除湿ロータの吸着能力を高くしつつ脱着温度を下げるという二律背反の問題を解決する必要があった。この解決策として特許文献１に開示された技術がある。つまり特許文献１に開示された技術は、吸着ゾーンを２段にして後段の吸着ゾーンでは吸着熱を除去しながら吸着を進め、さらに脱着ゾーンも２段として、それぞれの脱着ゾーンに加熱用ヒータを設けたものである。 Such a requirement required solving the trade-off problem of lowering the desorption temperature while increasing the adsorption capacity of the dehumidifying rotor. As a solution to this problem, there is a technique disclosed in Patent Document 1. In other words, the technique disclosed in Patent Document 1 has two adsorption zones, the adsorption zone is advanced while removing the heat of adsorption, and the desorption zones are further divided into two stages, and a heater is provided in each desorption zone. It is provided.
　また特許文献２に開示されたものは、除湿後の乾燥空気の一部を分岐して、パージゾーンを出た空気とを混合して脱着空気としている。 Also, the one disclosed in Patent Document 2 branches a part of the dehumidified dry air and mixes it with the air that has exited the purge zone to form desorbed air.
特開平０１－１９９６２１号公報Japanese Patent Laid-Open No. 01-199621
特開２０１０－７５８１９号公報JP 2010-75819 A
　解決しようとする問題点は、さらに低温の温度で脱着できるようにする点である。また空気の管路をより簡単にして、空気抵抗を減らし、これによってファンの消費エネルギーも減らすものである。 The problem to be solved is to enable desorption at a lower temperature. It also simplifies the air line and reduces air resistance, thereby reducing the energy consumed by the fan.
　本発明は、低温の脱着空気でも低露点の空気を供給できる吸着式除湿機を提供することを最も主要な特徴とする。 The main feature of the present invention is to provide an adsorption type dehumidifier capable of supplying air having a low dew point even with low-temperature desorption air.
　本発明の吸着式除湿機は、脱着ゾーンを２つ設け、湿気を多く含む初段の脱着ゾーンには外気を通して脱着し、湿気の少ない後段の脱着ゾーンには乾燥空気を流して脱着するようにするため、初段の脱着ゾーンでは外気を用いても脱着水分量が多く、後段の脱着ゾーンでは水分が少ないが乾燥空気を使って脱着しているため、低い脱着温度でも脱着が十分行われるという利点がある。 The adsorption type dehumidifier of the present invention is provided with two desorption zones, desorbing through the outside air in the first desorption zone containing a lot of moisture, and desorbing by flowing dry air into the desorption zone in the latter stage with low humidity. Therefore, in the first-stage desorption zone, the amount of desorbed water is large even when outside air is used, and in the latter-stage desorption zone, there is little moisture, but desorption is performed using dry air.Therefore, the desorption is sufficiently performed even at a low desorption temperature. is there.
　また、脱着ゾーンの一方のみに乾燥空気を送るようにしているため、乾燥空気の脱着での使用量を抑えることができる。 Also, since dry air is sent to only one of the desorption zones, the amount of dry air used for desorption can be reduced.
　脱着ゾーンが２つあるものの、後段の脱着ゾーンを出た空気を吸着ゾーンへ入れるようにする事で、吸着用のブロアと前段の脱着ゾーン用ブロアの２つでよく、或いは２つの脱着ゾーンそれぞれの出口を１つにまとめ、共通のブロアで脱着ゾーンの空気を大気放出するようにする事で、脱着用のブロアが１つでよくコストの上昇を抑えることができる。 Although there are two desorption zones, it is possible to use either an adsorption blower or a front desorption zone blower by allowing the air exiting the latter desorption zone to enter the adsorption zone, or each of the two desorption zones. By combining the outlets of the two into one and releasing the air in the desorption zone to the atmosphere with a common blower, only one desorption blower is required, and the cost increase can be suppressed.
　そして脱着空気の温度が低くてもよいため、ヒータの熱源として廃熱を用いることができ、この場合には極めて少ないエネルギーで乾燥空気の供給を行う事ができる。例えばディーゼル発電機のエンジンの冷却水をラジエターに通し、このラジエターをヒータとして利用することができる。この場合には、捨てられるエネルギーで本発明の吸着式除湿機の主な駆動エネルギーとする事ができ、省エネルギー効果が高い。 Since the temperature of the desorption air may be low, waste heat can be used as a heat source for the heater. In this case, dry air can be supplied with very little energy. For example, the cooling water of the engine of a diesel generator can be passed through a radiator, and this radiator can be used as a heater. In this case, the discarded energy can be used as the main driving energy of the adsorption dehumidifier of the present invention, and the energy saving effect is high.
　工場などの非常用電源としてディーゼル発電機を用いる場合、停電を感知後短時間で非常用電源に切り替える必要がある。このような場合には、停電を感知してからディーゼル発電機を起動したのでは、非常用電源への切り替えに時間が掛かる。このためディーゼル発電機を常時運転しておき、停電の瞬間に商用電源から非常用電源へと切り替えを行うようにしている場合が多い。 When using a diesel generator as an emergency power source in a factory, etc., it is necessary to switch to an emergency power source in a short time after detecting a power failure. In such a case, if the diesel generator is started after detecting a power failure, it takes time to switch to the emergency power source. For this reason, in many cases, the diesel generator is always operated and switching from a commercial power source to an emergency power source is performed at the moment of a power failure.
　上記のような状況では、ディーゼル発電機から常時廃熱が発生し、その廃熱を捨てているため、エネルギーの無駄が多かったが、本発明の吸着式除湿機のように低温の脱着空気で低露点の空気を供給できるものでは、そのように捨てられているエネルギーを利用することが可能である。 In the above situation, waste heat is always generated from the diesel generator, and the waste heat is thrown away, so there is a lot of energy wasted, but with the desorption air at low temperature like the adsorption dehumidifier of the present invention. Anything that can supply air with a low dew point can make use of such discarded energy.
図１は吸着式除湿機の実施例１におけるフロー図である。FIG. 1 is a flowchart in Example 1 of an adsorption dehumidifier. 図２は吸着式除湿機の実施例における空気線図である。FIG. 2 is an air diagram in the embodiment of the adsorption type dehumidifier. 図３は吸着式除湿機の実施例２におけるフロー図である。FIG. 3 is a flowchart in Example 2 of the adsorption type dehumidifier.
　本発明の吸着式除湿機は、外気を冷却除湿して除湿ロータの吸着ゾーンに通すようにするとともに、脱着ゾーンを２つ設け、湿気を多く含む初段の脱着ゾーンには外気を通して脱着し、湿気の少ない後段の脱着ゾーンには乾燥空気を流して脱着するようにしたため、低い温度の脱着空気で低露点の空気を供給するという目的を、最小の部品点数で実現し、省エネルギー効果を高めた。 The adsorption type dehumidifier of the present invention cools and dehumidifies the outside air and passes it through the adsorption zone of the dehumidification rotor, and provides two desorption zones. The first stage desorption zone containing a lot of moisture desorbs through the outside air, Since the desorption zone in the rear stage with a small amount of dry air is desorbed by flowing dry air, the purpose of supplying low dew point air with low temperature desorption air is realized with the minimum number of parts, and the energy saving effect is enhanced.
　１は除湿ロータであり、シリカゲルやゼオライトなどの吸着剤の担持されたもので、既に多くの技術が公知である。この除湿ロータ１は、図１の矢印方向にギヤドモータ（図示せず）によって回転駆動される。そして除湿ロータ１は吸着ゾーン２、第１脱着ゾーン３、第２脱着ゾーン４に分割されている。この吸着ゾーン２、第１脱着ゾーン３、第２脱着ゾーン４の各ゾーンの面積比は５：３：１である。 Numeral 1 is a dehumidifying rotor which carries an adsorbent such as silica gel or zeolite, and many techniques are already known. The dehumidifying rotor 1 is rotationally driven by a geared motor (not shown) in the direction of the arrow in FIG. The dehumidifying rotor 1 is divided into an adsorption zone 2, a first desorption zone 3, and a second desorption zone 4. The area ratio of each zone of the adsorption zone 2, the first desorption zone 3, and the second desorption zone 4 is 5: 3: 1.
　５はブロアで外気（以下「ＯＡ」と書く）を除湿ロータ１の吸着ゾーン２へ送るものである。６は冷却器であり、例えば冷凍機に接続されたエバポレータである。７及び８はそれぞれ第１ヒータおよび第２ヒータであり、例えば冷却器６に接続された冷凍機のコンデンサ或いは、ディーゼル発電機の冷却液が流れるラジエターである。 5 is a blower that sends outside air (hereinafter referred to as “OA”) to the adsorption zone 2 of the dehumidifying rotor 1. 6 is a cooler, for example, an evaporator connected to a refrigerator. Reference numerals 7 and 8 denote a first heater and a second heater, respectively, for example, a condenser of a refrigerator connected to the cooler 6 or a radiator through which a coolant of a diesel generator flows.
　ブロア５はＯＡ１を吸い込み、そこから出た空気は冷却器６を通過して除湿ロータ１の吸着ゾーン２に入る。除湿ロータ１の吸着ゾーン２を通過した空気の一部は分岐され、残りの空気は製品空気（以下「ＤＡ」と書く）となってドライルーム（図示せず）に供給される。その分岐された空気は第２ヒータ８を通過して、第２脱着ゾーン４に入り、第２脱着ゾーン４を通過した空気はブロア５の吸い込み側に戻る。 The blower 5 sucks OA 1, and the air coming out of it passes through the cooler 6 and enters the adsorption zone 2 of the dehumidifying rotor 1. Part of the air that has passed through the adsorption zone 2 of the dehumidifying rotor 1 is branched, and the remaining air is supplied as product air (hereinafter referred to as “DA”) to a dry room (not shown). The branched air passes through the second heater 8 and enters the second desorption zone 4, and the air that has passed through the second desorption zone 4 returns to the suction side of the blower 5.
　ＯＡ２は第１ヒータ７を通過し、除湿ロータ１の第１脱着ゾーン３を通過してブロア９の吸い込み側に吸い込まれ、排気（以下「ＥＡ」と書く）となって大気放出される。除湿ロータ１の吸着ゾーン２、第１脱着ゾーン３、第２脱着ゾーン４各ゾーンを通過する空気の速度を一致させると、各ゾーンを通過する風量比は、各ゾーンの面積比と同じ５：３：１となる。つまり第２脱着ゾーン４の面積が第１脱着ゾーン３の面積よりも小さい。 OA 2 passes through the first heater 7, passes through the first desorption zone 3 of the dehumidifying rotor 1, is sucked into the suction side of the blower 9, and is discharged into the atmosphere as exhaust (hereinafter referred to as “EA”). When the velocity of the air passing through each of the adsorption zone 2, the first desorption zone 3, and the second desorption zone 4 of the dehumidifying rotor 1 is matched, the air volume ratio passing through each zone is the same as the area ratio of each zone 5: 3: 1. That is, the area of the second desorption zone 4 is smaller than the area of the first desorption zone 3.
　本発明の吸着式除湿機は以上のような構成であり、以下その動作を説明する。以下の説明で温度は全て摂氏で表す。低露点の空気を供給するのに、最も条件の厳しい盛夏の状態を想定する。この場合ＯＡの空気条件は、３５度で相対湿度５３パーセント（絶対湿度１８．６ｇ／ｋｇ）であった。 The adsorption dehumidifier of the present invention has the above-described configuration, and the operation thereof will be described below. In the following description, all temperatures are expressed in degrees Celsius. Assume the most severe midsummer conditions for supplying low dew point air. In this case, the air condition of OA was 35 degrees and relative humidity 53 percent (absolute humidity 18.6 g / kg).
　このＯＡがブロア５によって冷却器６に送られ、結露によって除湿され、空気条件は１２度で絶対湿度が８．３ｇ／ｋｇとなった。この冷却された空気は除湿ロータ１の吸着ゾーン２を通過し、さらに吸着除湿される。この際に、吸着熱によって温度が上昇し、３２度、絶対湿度１．２ｇ／ｋｇの空気となった。この乾燥空気を製品空気（以下「ＤＡ」と書く）としてドライルームに供給する。吸着ゾーン２を通過する際の空気条件の変化は、図２の線「処理」で示される。 This OA was sent to the cooler 6 by the blower 5 and dehumidified by condensation. The air condition was 12 degrees and the absolute humidity was 8.3 g / kg. The cooled air passes through the adsorption zone 2 of the dehumidifying rotor 1 and is further adsorbed and dehumidified. At this time, the temperature rose due to the heat of adsorption, and the air became 32 ° C. and the absolute humidity was 1.2 g / kg. This dry air is supplied to the dry room as product air (hereinafter referred to as “DA”). The change in air conditions as it passes through the adsorption zone 2 is indicated by the line “Process” in FIG.
　ＯＡ２は第１ヒータ７によって６０度まで加熱され、除湿ロータ１の第１脱着ゾーン３へ送られる。第１脱着ゾーン３は水分の最も多い部分であり、脱着空気の温度が６０度であっても多くの水分が脱着される。つまり絶対湿度１８．６ｇ/ｋｇの空気が２５．１ｇ/ｋｇとなる。第１脱着ゾーン３を通過する空気条件は、図２の線「再生１」で表される。第１脱着ゾーン３を出た空気は湿分が多く、排気（以下「ＥＡ」と書く）として大気へ放出される。 OA2 is heated to 60 degrees by the first heater 7 and sent to the first desorption zone 3 of the dehumidifying rotor 1. The first desorption zone 3 is the portion with the most moisture, and a large amount of moisture is desorbed even when the temperature of the desorption air is 60 degrees. That is, air with an absolute humidity of 18.6 g / kg is 25.1 g / kg. The air condition passing through the first desorption zone 3 is represented by the line “Regeneration 1” in FIG. The air leaving the first desorption zone 3 has a high moisture content and is released to the atmosphere as exhaust (hereinafter referred to as “EA”).
　吸着ゾーン２を通過した乾燥空気の一部は分岐され、第２ヒータ８で加熱されて第２脱着ゾーン４へ送られる。この第２脱着ゾーン４では除湿ロータ１の湿気はかなり減少している。しかし、第２脱着ゾーン４に送られる空気は絶対湿度が１．２ｇ／ｋｇと極めて低いため、さらに脱着が進む。第２脱着ゾーン４を通過することによって、空気は温度６０度、絶対湿度１．２ｇ／ｋｇから、温度２３．６度、絶対湿度１４．２ｇ／ｋｇになる。この変化は図２の線「再生２」で示される。 A part of the dry air that has passed through the adsorption zone 2 is branched, heated by the second heater 8, and sent to the second desorption zone 4. In the second desorption zone 4, the humidity of the dehumidifying rotor 1 is considerably reduced. However, since the absolute humidity of the air sent to the second desorption zone 4 is as extremely low as 1.2 g / kg, desorption proceeds further. By passing through the second desorption zone 4, the air changes from a temperature of 60 degrees and an absolute humidity of 1.2 g / kg to a temperature of 23.6 degrees and an absolute humidity of 14.2 g / kg. This change is indicated by the line “Regeneration 2” in FIG.
　第２脱着ゾーン４を出た空気の絶対湿度は１４．２ｇ/ｋｇであり、ＯＡの絶対湿度１８．６ｇ／ｋｇより低いため、この空気をブロア５の吸い込み側に供給し、ＯＡと混合する事によって除湿性能が確保される。 Since the absolute humidity of the air leaving the second desorption zone 4 is 14.2 g / kg, which is lower than the absolute humidity of OA 18.6 g / kg, this air is supplied to the suction side of the blower 5 and mixed with OA. Dehumidifying performance is ensured by this.
　このように第１ヒータ７、第２ヒータ８とも温度が６０度であっても、ＤＡとして絶対湿度１．２ｇ／ｋｇの空気を供給することができる。６０度であると、廃熱として多くの廃熱源が利用できる。例えばディーゼル発電機のエンジンの冷却液の温度は８０度程度であり、十分に利用可能である。また冷凍機のコンデンサも６０度程度のものがある。さらに太陽熱温水器は春季や秋季でも６０度の温水供給が可能であり、このような熱源も利用可能である。 Thus, even if the temperature of both the first heater 7 and the second heater 8 is 60 degrees, air having an absolute humidity of 1.2 g / kg can be supplied as DA. If it is 60 degrees, many waste heat sources can be used as waste heat. For example, the temperature of the coolant of a diesel generator engine is about 80 degrees, which is sufficiently usable. Also, there are refrigerators with a condenser of about 60 degrees. Furthermore, solar water heaters can supply hot water at 60 degrees even in spring and autumn, and such heat sources can also be used.
　特に湿気の残量の少ない第２脱着ゾーン４は面積が第１脱着ゾーン３の面積よりも小さくても十分に脱着を行う事ができ、これによって第２脱着ゾーン４を通過する空気の量を少なくすることができ、より省エネルギー効果が高い。 In particular, the second desorption zone 4 having a small remaining amount of moisture can be sufficiently desorbed even if the area is smaller than the area of the first desorption zone 3, thereby reducing the amount of air passing through the second desorption zone 4. It can be reduced and the energy saving effect is higher.
　本発明の実施例２のものは、実施例１のものと比較して次の点が相違している。それ以外については実施例１のものと同一であり、冗長性を避けるため重複した説明を行わない。図３において、１０は切り替えバルブであり、除湿ロータ１の第２脱着ゾーン４を出た空気をブロア９の吸い込み側へ流すか、ブロア５の吸い込み側に流すか、切り替えるものである。 The second embodiment of the present invention differs from the first embodiment in the following points. Other than that, it is the same as that of the first embodiment, and redundant description is not given to avoid redundancy. In FIG. 3, reference numeral 10 denotes a switching valve, which switches between the air that has exited the second desorption zone 4 of the dehumidifying rotor 1 flowing to the suction side of the blower 9 or the suction side of the blower 5.
　つまり図３の切り替えバルブ１０内の仕切り板が実線の状態であると、第２脱着ゾーン４を出た空気をブロア５の吸い込み側へ流れ、切り替えバルブ１０内の仕切り板が破線の状態であると、第２脱着ゾーン４を出た空気をブロア９の吸い込み側へ流れる。 That is, when the partition plate in the switching valve 10 in FIG. 3 is in a solid line state, the air that has exited the second desorption zone 4 flows to the suction side of the blower 5 and the partition plate in the switching valve 10 is in a broken line state. Then, the air leaving the second desorption zone 4 flows to the suction side of the blower 9.
　第２脱着ゾーン４を出た空気をブロア５の吸い込み側へ流れるようにすると、動作は上記の実施例１の状態と全く同一となる。ここで、ＯＡの絶対湿度が第２脱着ゾーン４を出た空気の絶対湿度よりも低くなった場合、第２脱着ゾーン４を出た空気を吸着ゾーン２へ循環させるよりもＥＡとして大気放出した方が、ＤＡの湿度が低くなる。つまり気象条件に合わせて切り替えバルブ１０を切り替え、最も湿度の低い空気を供給するようにする事ができる。 When the air leaving the second desorption zone 4 flows to the suction side of the blower 5, the operation is exactly the same as in the first embodiment. Here, when the absolute humidity of OA is lower than the absolute humidity of the air leaving the second desorption zone 4, the air leaving the second desorption zone 4 was released into the atmosphere as EA rather than being circulated to the adsorption zone 2. However, the humidity of DA is lower. That is, the switching valve 10 can be switched according to the weather conditions to supply the air with the lowest humidity.
　本発明の吸着式除湿機は、低温の廃熱を利用しても低露点の空気を供給でき、極めて高い省エネルギー効果を発揮できる。 The adsorption type dehumidifier of the present invention can supply air with a low dew point even if low temperature waste heat is used, and can exhibit an extremely high energy saving effect.
　１　　　除湿ロータ
　２　　　吸着ゾーン
　３　　　第１脱着ゾーン
　４　　　第２脱着ゾーン
　５　　　ブロア
　６　　　冷却器
　７　　　第１ヒータ
　８　　　第２ヒータ
　９　　　ブロア
　１０　　切り替えバルブ DESCRIPTION OF SYMBOLS 1 Dehumidification rotor 2 Adsorption zone 3 1st desorption zone 4 2nd desorption zone 5 Blower 6 Cooler 7 1st heater 8 2nd heater 9 Blower 10 Switching valve

Claims (4)

  1. 　外気を冷却除湿して除湿ロータの吸着ゾーンに通すようにするとともに、脱着ゾーンを２つ設け、湿気を多く含む初段の脱着ゾーンには外気を通して脱着し、湿気の少ない後段の脱着ゾーンには前記吸着ゾーンを出た乾燥空気を流して脱着するようにしたことを特徴とする吸着式除湿機。 The outside air is cooled and dehumidified to pass through the adsorption zone of the dehumidification rotor, and two desorption zones are provided. The desorption zone of the first stage containing a lot of moisture is desorbed through the outside air, and the desorption zone of the latter stage where the humidity is low An adsorptive dehumidifier characterized in that it is desorbed by flowing dry air that has exited the adsorption zone.
  2. 　後段の脱着ゾーンを前段の脱着ゾーンより面積を小さくしたことを特徴とする請求項１記載の吸着式除湿機。 2. The adsorption type dehumidifier according to claim 1, wherein the area of the subsequent desorption zone is smaller than that of the previous desorption zone.
  3. 　後段の脱着ゾーンを出た空気を、冷却除湿の前に戻すようにしたことを特徴とする請求項１記載の吸着式除湿機。 The adsorption type dehumidifier according to claim 1, wherein the air exiting the subsequent desorption zone is returned before cooling and dehumidification.
  4. 　後段の脱着ゾーンを出た空気を、冷却除湿の前に戻すか、大気放出するようにするか、切り替えるバルブを設けたことを特徴とする請求項１記載の吸着式除湿機。 The adsorption dehumidifier according to claim 1, further comprising a valve for switching whether the air leaving the desorption zone at the rear stage is returned to the air before cooling dehumidification or is released into the atmosphere.
PCT/JP2011/060103 2011-04-26 2011-04-26 Adsorption dehumidifier WO2012147153A1 (en)

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CN107970748A (en) * 2016-10-25 2018-05-01 阿特拉斯·科普柯空气动力股份有限公司 The method of compressor apparatus and dry compressed gas
CN111111382A (en) * 2018-10-30 2020-05-08 华懋科技股份有限公司 Runner system with high temperature desorption and method therefor
WO2021033101A1 (en) * 2019-08-16 2021-02-25 Atlas Copco Airpower N.V. Dryer for compressed gas, compressor installation provided with a dryer and a method for drying compressed gas
BE1027507B1 (en) * 2019-08-16 2021-03-17 Atlas Copco Airpower Nv Dryer for compressed gas, compressor installation equipped with dryer and method for drying compressed gas

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107970748A (en) * 2016-10-25 2018-05-01 阿特拉斯·科普柯空气动力股份有限公司 The method of compressor apparatus and dry compressed gas
JP2018069235A (en) * 2016-10-25 2018-05-10 アトラス コプコ エアーパワー，ナームローゼ フェンノ Compressor facility having dryer for compression gas and method of drying compression gas
EP3446770A1 (en) * 2016-10-25 2019-02-27 ATLAS COPCO AIRPOWER, naamloze vennootschap Compressor installation with drying device for compressed gas and method for drying compressed gas
US10576411B2 (en) 2016-10-25 2020-03-03 Atlas Copco Airpower, Naamloze Vennootschap Compressor installation with drying device for compressed gas and method for drying compressed gas
CN107970748B (en) * 2016-10-25 2021-07-27 阿特拉斯·科普柯空气动力股份有限公司 Compressor apparatus and method of drying compressed gas
CN113385002A (en) * 2016-10-25 2021-09-14 阿特拉斯·科普柯空气动力股份有限公司 Compressor installation and method for drying compressed gas
EP3915664A1 (en) * 2016-10-25 2021-12-01 Atlas Copco Airpower N.V. Compressor installation with drying device for compressed gas and method for drying compressed gas
US11247166B2 (en) 2016-10-25 2022-02-15 Atlas Copco Airpower, Naamloze Vennootschap Compressor installation with drying device for compressed gas and method for drying compressed gas
CN111111382A (en) * 2018-10-30 2020-05-08 华懋科技股份有限公司 Runner system with high temperature desorption and method therefor
WO2021033101A1 (en) * 2019-08-16 2021-02-25 Atlas Copco Airpower N.V. Dryer for compressed gas, compressor installation provided with a dryer and a method for drying compressed gas
BE1027507B1 (en) * 2019-08-16 2021-03-17 Atlas Copco Airpower Nv Dryer for compressed gas, compressor installation equipped with dryer and method for drying compressed gas

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