JP2651717B2 - Air cooling system - Google Patents
Air cooling systemInfo
- Publication number
- JP2651717B2 JP2651717B2 JP4101389A JP4101389A JP2651717B2 JP 2651717 B2 JP2651717 B2 JP 2651717B2 JP 4101389 A JP4101389 A JP 4101389A JP 4101389 A JP4101389 A JP 4101389A JP 2651717 B2 JP2651717 B2 JP 2651717B2
- Authority
- JP
- Japan
- Prior art keywords
- air
- cooling
- water
- evaporator
- cooled
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
- F28C1/00—Direct-contact trickle coolers, e.g. cooling towers
- F28C2001/006—Systems comprising cooling towers, e.g. for recooling a cooling medium
Landscapes
- Other Air-Conditioning Systems (AREA)
Description
【発明の詳細な説明】 [産業上の利用分野] 本発明は主にコンピュータ室や無塵室などの空気を調
和するための空気冷却装置に関し、特に消費電力量を少
なくした空気冷却装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention mainly relates to an air cooling device for conditioning air in a computer room or a dust-free room, and more particularly to an air cooling device with reduced power consumption.
[従来の技術] コンピュータ室や無塵室、無菌室などでは、四季を問
わずに、例えば28℃程度に上昇した空気を18℃程度に冷
却する必要がある。そのような室内の空気を調和するた
めの空気冷却装置としては、従来例えば第6図に示すも
のがあり、これは室内6の空気を送風機4によって蒸発
器14を通過させて冷却して室内6に戻し、圧縮機11、水
冷式凝縮器12、膨張弁13及び前記蒸発器14の順に冷媒を
循環させて蒸発器14において空気と熱交換をさせ、密閉
式冷却塔20と前記水冷式凝縮器12との間に冷却水を循環
させて水冷式凝縮器12において冷媒と熱交換をさせ、冷
却塔20より放熱をさせた冷却装置である。2. Description of the Related Art In a computer room, a dust-free room, a sterile room, and the like, it is necessary to cool air that has risen to about 28 ° C. to about 18 ° C. regardless of the four seasons. FIG. 6 shows an example of a conventional air cooling device for harmony of the indoor air. The air cooling device cools the air in the indoor 6 by passing it through an evaporator 14 by a blower 4 to cool the indoor air. The refrigerant is circulated in the order of the compressor 11, the water-cooled condenser 12, the expansion valve 13, and the evaporator 14 to exchange heat with air in the evaporator 14, and the sealed cooling tower 20 and the water-cooled condenser A cooling device in which cooling water is circulated between the cooling tower 12 and the water-cooled condenser 12 to exchange heat with the refrigerant and radiate heat from the cooling tower 20.
[発明が解決しようとする課題] 上記従来の空気冷却装置では、冷却塔20として例えば
空冷式冷却塔を使用する場合には、夏期には外気温が高
いため空冷式冷却塔による冷却水の冷却は30℃程度まで
が限度であり、この冷却水温度を条件として冷却装置と
しての各仕様が決定される。しかるに冬期外気温度が下
がったときには、冷媒循環量の過度の低下を防ぐため
に、冷却塔20出口の冷却水の温度を20℃程度以上に保つ
必要があり、そのために例えば冷却塔20を迂回する室外
機バイパス弁44などを使用し、冷却塔20出口の冷却水配
管41に取付けたサーモスタット43と組合わせて冷却塔20
が出口水温を所定の温度にコントロールする等の方法が
取られていた。[Problems to be Solved by the Invention] In the above-mentioned conventional air cooling device, when an air-cooling type cooling tower is used as the cooling tower 20, for example, cooling of the cooling water by the air-cooling type cooling tower because the outside air temperature is high in summer. Is limited to about 30 ° C., and the specifications of the cooling device are determined on the condition of the cooling water temperature. However, when the outside air temperature in winter falls, it is necessary to maintain the temperature of the cooling water at the outlet of the cooling tower 20 at about 20 ° C. or higher in order to prevent the refrigerant circulation amount from excessively decreasing. The cooling tower 20 is used in combination with a thermostat 43 attached to the cooling water pipe 41 at the
Has been used to control the outlet water temperature to a predetermined temperature.
したがって圧縮機11は年間を通して作動することにな
り、その動力費は莫大なものとなってしまうという欠点
があり、冷却塔20を密閉蒸発式冷却塔としても事情は同
じである。Therefore, the compressor 11 operates all year round, and has a drawback that the power cost is enormous, and the situation is the same even if the cooling tower 20 is a closed evaporative cooling tower.
また上記と同様に室内に圧縮式冷凍機を、室外に冷却
塔を設置し、圧縮式冷凍機の圧縮機の起動・停止による
室温の急変を回避するために圧縮機を常時稼働させ、電
熱などによって空気を再熱して室温の調整を行うもの
や、室外の冷凍機によって得た冷水を室内に送り、室内
側で該冷水の通過量を制御することによって室温の調整
を行うものなどもあるが、これらも年間を通じて圧縮機
を運転しているために、消費動力が大きくなるという欠
点があった。In the same manner as above, a compression refrigerator is installed indoors, and a cooling tower is installed outside the room.The compressor is always operated to avoid sudden changes in room temperature due to starting and stopping of the compressor of the compression refrigerator, and electric heating etc. There are those that re-heat the air to adjust the room temperature, those that send cold water obtained by an outdoor refrigerator to the room, and adjust the room temperature by controlling the amount of the cold water that passes through the room, and the like. However, since these compressors are operated throughout the year, power consumption is increased.
本発明は、上記欠点に鑑みてなされたもので、消費電
力量を低減した空気冷却装置を提供することを目的とす
るものである。The present invention has been made in view of the above-described drawbacks, and has as its object to provide an air cooling device with reduced power consumption.
[課題を解決するための手段] 通常の空気調和設備では除湿を必要とするために、快
適室内空気条件、例えば温度25℃相対湿度55%程度にす
るには、装置露点温度を15℃以下とする必要があり、こ
のためには空気を冷却するための冷熱源温度として10℃
程度が要求される。[Means for Solving the Problems] Since dehumidification is required in ordinary air conditioning equipment, the dew point temperature of the device should be 15 ° C or less to achieve comfortable indoor air conditions, for example, a temperature of 25 ° C and a relative humidity of about 55%. It is necessary to use a cold source temperature of 10 ° C to cool the air.
Degree is required.
これに対してコンピュータ室の空気調和設備では、コ
ンピュータ本体や周辺機器の動力消費量に比べて在室者
数が少なく外気取入量もわずかなため、除湿負荷がきわ
めて低い。また無塵室や無菌室などでは、清浄度を保つ
上から大風量が必要となり、その結果冷却して下げるべ
き空気温度の幅は小さい。したがって両者とも装置露点
温度は17℃以上で十分であり、このためには空気を冷却
するための冷熱源温度は15℃以上で済むこととなる。On the other hand, in the air conditioning equipment in the computer room, the dehumidification load is extremely low because the number of occupants is small and the amount of outside air intake is small compared to the power consumption of the computer body and peripheral devices. In a dust-free room, a sterile room, or the like, a large air volume is required in order to maintain cleanliness. As a result, the range of the air temperature to be cooled and lowered is small. Therefore, in both cases, a device dew point temperature of 17 ° C. or more is sufficient, and for this purpose, a cooling source temperature for cooling air needs to be 15 ° C. or more.
しかして10℃の冷水を得るには冷凍機によるしかない
が、15℃程度の冷水で済むとなれば、少なくとも冬期に
は冷却塔で十分に該冷水を得ることができる。Thus, the only way to obtain 10 ° C. cold water is with a refrigerator, but if it is sufficient to use about 15 ° C. cold water, the cooling tower can sufficiently obtain the cold water at least in winter.
本発明はこのことに着目してなされたものであり、す
なわち冷却すべき空気を空気冷却器及び蒸発器の順に通
過させ、圧縮機、水冷式凝縮器、膨張弁及び前記蒸発器
の順に冷媒を循環させ(以降においてこの系統を中間サ
イクルと称する。)、密閉式冷却塔、圧縮式チラー、前
記空気冷却器及び前記水冷式凝縮器の順に冷却水を循環
させた空気冷却装置である。密閉式冷却塔としては、密
閉空冷式冷却塔であると密閉蒸発式冷却塔であるとを問
わない。The present invention has been made by paying attention to this fact, that is, the air to be cooled is passed through the air cooler and the evaporator in order, and the refrigerant is cooled in the order of the compressor, the water-cooled condenser, the expansion valve, and the evaporator. An air cooling device that circulates (hereinafter, this system is referred to as an intermediate cycle), and circulates cooling water in the order of a closed cooling tower, a compression chiller, the air cooler, and the water-cooled condenser. The closed cooling tower may be a closed air-cooled cooling tower or a closed evaporative cooling tower.
ここで水冷式凝縮器の出口もしくは入口の冷却水配管
に直列に、又は水冷式凝縮器の冷却水配管と並列に空気
再熱器を配置し、冷却すべき空気を前記蒸発器の後、更
にこの空気再熱器に通過させることができる。Here, an air reheater is disposed in series with the cooling water pipe at the outlet or inlet of the water-cooled condenser, or in parallel with the cooling water pipe of the water-cooled condenser, and the air to be cooled is further cooled after the evaporator. It can be passed through this air reheater.
以上において中間サイクルの圧縮機と水冷式凝縮器と
の少なくともいずれか一方を、空気冷却器及び蒸発器、
並びに空気再熱器を配置したときはその空気再熱器と離
隔して配置することができ、また中間サイクルの圧縮
機、水冷式凝縮器及び圧縮式チラーを密閉式冷却塔の内
部に組み込むことも、空気冷却器及び中間サイクルの蒸
発器を複数台配置することもできる。In the above, at least one of the intermediate cycle compressor and the water-cooled condenser, an air cooler and an evaporator,
In addition, when an air reheater is installed, it can be installed at a distance from the air reheater, and the compressor, water-cooled condenser and compression chiller of the intermediate cycle must be incorporated inside the closed cooling tower. Alternatively, a plurality of air coolers and intermediate cycle evaporators may be arranged.
[作用] 冬期に外気温度が低いときは、必要装置露点温度まで
空気を冷却することができる冷却水の温度、すなわち概
ね15℃以下に該冷却水を冷却するには、冷却塔のみの運
転で十分である。したがって圧縮式チラーと中間サイク
ルの圧縮機との運転は停止し、冷却塔のみを運転して冷
却水を空気冷却器に送ると、空気の熱は空気冷却器にお
いて冷却水に伝達され、冷却水の熱は冷却塔において外
気に放熱され、こうして空気を所定の温度まで冷却する
ことができる。[Action] When the outside air temperature is low in winter, the temperature of the cooling water that can cool the air to the required device dew point temperature, that is, to cool the cooling water to approximately 15 ° C. or less, requires only the operation of the cooling tower. It is enough. Therefore, when the operation of the compression chiller and the compressor of the intermediate cycle is stopped and only the cooling tower is operated to send the cooling water to the air cooler, the heat of the air is transmitted to the cooling water in the air cooler, and the cooling water is cooled. Is radiated to the outside air in the cooling tower, and thus the air can be cooled to a predetermined temperature.
春秋期に外気の温度が上昇して、冷却塔のみの運転で
は前記概ね15℃の冷却水が得られなくなったときは、圧
縮式チラーの運転は停止したまま、冷却塔の他更に中間
サイクルの圧縮機を運転すると、空気の熱は空気冷却器
において冷却水に伝達され更に中間サイクルの蒸発器に
おいて冷媒に伝達され、冷媒の熱は中間サイクルの水冷
式凝縮器において冷却水に伝達され、冷却水の熱は冷却
塔において外気に放熱され、こうして空気を所定の温度
まで冷却することができる。When the temperature of the outside air rises in the spring and autumn, and the cooling water of about 15 ° C. cannot be obtained by the operation of only the cooling tower, the operation of the compression chiller is stopped, and the cooling tower and other intermediate cycles are further stopped. When the compressor is operated, the heat of the air is transmitted to the cooling water in the air cooler, and further transmitted to the refrigerant in the evaporator of the intermediate cycle, and the heat of the refrigerant is transmitted to the cooling water in the water-cooled condenser of the intermediate cycle. The heat of the water is radiated to the outside air in the cooling tower, so that the air can be cooled to a predetermined temperature.
なお春秋期において中間サイクルの圧縮機の運転は停
止し、冷却塔と圧縮式チラーを運転することにより、空
気の熱を空気冷却器において冷却水に伝達し、冷却水の
熱を冷却塔と圧縮式チラーにおいて外気に放熱すること
もできる。During the spring and fall seasons, the operation of the compressor in the intermediate cycle was stopped, and by operating the cooling tower and the compression chiller, the heat of the air was transmitted to the cooling water in the air cooler, and the heat of the cooling water was compressed by the cooling tower. In the chiller, heat can be radiated to the outside air.
夏期に至り冷却塔と中間サイクルの圧縮器との運転、
又は冷却塔と圧縮式チラーとの運転によっては空気を十
分に冷却できないときは、冷却塔と圧縮式チラーと中間
サイクルとのすべてを運転すると、空気の熱は空気冷却
器において冷却水に伝達され更に中間サイクルの蒸発器
において冷媒に伝達され、冷媒の熱は中間サイクルの水
冷式凝縮器のおいて冷却水に伝達され、冷却水の熱は冷
却塔と圧縮式チラーとにおいて外気に放熱され、こうし
て空気を所定の温度まで冷却することができる。In summer, operation of the cooling tower and the compressor of the intermediate cycle,
Or, when the air cannot be sufficiently cooled by the operation of the cooling tower and the compression chiller, when the cooling tower, the compression chiller and the intermediate cycle are all operated, the heat of the air is transferred to the cooling water in the air cooler. Further, the refrigerant is transmitted to the refrigerant in the evaporator of the intermediate cycle, the heat of the refrigerant is transmitted to the cooling water in the water-cooled condenser of the intermediate cycle, and the heat of the cooling water is radiated to the outside air in the cooling tower and the compression chiller, Thus, the air can be cooled to a predetermined temperature.
[実施例] 以下本発明の実施例を図面に基づき説明する。第1図
は、本発明の一実施例を示す空気冷却装置の系統図であ
り、室内機1内には、空気濾過器2、空気冷却器3、送
風機4が設けられており、更に中間サイクル10の圧縮機
11、水冷式凝縮器12、膨張弁13及び蒸発器14が設けられ
ており、室内6の空気は空気濾過器2、空気冷却器3、
中間サイクルの蒸発器14を通過して送風機4によってダ
クト5を経由して室内6に戻るように構成されている。Embodiment An embodiment of the present invention will be described below with reference to the drawings. FIG. 1 is a system diagram of an air cooling device showing one embodiment of the present invention. In an indoor unit 1, an air filter 2, an air cooler 3, and a blower 4 are provided. 10 compressors
11, a water-cooled condenser 12, an expansion valve 13, and an evaporator 14 are provided, and the air in the room 6 is supplied with an air filter 2, an air cooler 3,
It is configured to return to the room 6 through the duct 5 by the blower 4 after passing through the evaporator 14 of the intermediate cycle.
中間サイクル10の圧縮機11、水冷式凝縮器12、膨張弁
13及び蒸発器14にはその順に冷媒が循環するように構成
されており、冷媒は膨張弁13を介して蒸発器14内で蒸発
して吸熱し、圧縮機11において圧縮されて高温となり、
水冷式凝縮器12において液化して放熱するサイクルを繰
り返す。Intermediate cycle 10 compressor 11, water-cooled condenser 12, expansion valve
The refrigerant is circulated in the evaporator 14 and the evaporator 14 in that order, the refrigerant evaporates and absorbs heat in the evaporator 14 via the expansion valve 13, and is compressed in the compressor 11 to have a high temperature,
The cycle of liquefaction and heat release in the water-cooled condenser 12 is repeated.
20は密閉式冷却塔であり、本実施例では該冷却塔20は
密閉蒸発式冷却塔によって構成されており、ファン22に
よって空気吸入口より外気を吸入して蒸発式冷却コイル
21に送風し、且つ散水ポンプ24によって散水槽23内の水
を散水ヘッダー25から冷却コイル21に散布して、冷却コ
イル21内の冷却水を冷却している。Reference numeral 20 denotes a closed cooling tower. In this embodiment, the cooling tower 20 is constituted by a closed evaporative cooling tower.
The cooling water in the cooling coil 21 is cooled by blowing air to the cooling coil 21 and spraying the water in the water spray tank 23 from the watering header 25 to the cooling coil 21 by the watering pump 24.
30は圧縮式チラーであり、該圧縮式チラー30は圧縮機
31、凝縮器32、膨張弁33及び蒸発器34とこれらを循環す
る冷媒とを有し、冷媒は膨張弁33を介して蒸発器34内で
蒸発して冷却水を冷却し、圧縮機31において圧縮されて
高温となり、凝縮器32において液化して放熱するサイク
ルを繰り返す。Reference numeral 30 denotes a compression chiller, and the compression chiller 30 is a compressor.
31, a condenser 32, an expansion valve 33, an evaporator 34 and a refrigerant circulating through the refrigerant, the refrigerant evaporates in the evaporator 34 via the expansion valve 33 to cool the cooling water, and in the compressor 31 The cycle of compression to high temperature, liquefaction and heat release in the condenser 32 is repeated.
圧縮式チラー30の蒸発器34出口の冷却水は、ポンプ40
によって昇圧され、入口管41を通ってっ室内機1に至
り、空気冷却器3と中間サイクルの水冷式凝縮器12を通
過し、出口管42を通って室外に至り、冷却塔の冷却コイ
ル21を通過して圧縮式チラーの蒸発器34に戻る。The cooling water at the evaporator 34 outlet of the compression chiller 30 is
The air is cooled by the cooling pipe 21 through the inlet pipe 41, reaches the indoor unit 1, passes through the air cooler 3 and the water-cooled condenser 12 of the intermediate cycle, passes through the outlet pipe 42, and reaches the outdoor. And returns to the evaporator 34 of the compression chiller.
次にこの実施例の作用について説明すると冬期におい
ては、外気温度が10℃程度の場合に、通常冷却塔20のみ
の能力で15℃程度の冷却水が取り出せるから、中間サイ
クル10と圧縮式チラー30は停止し、冷却塔20のみを作動
させる。このとき室内6の28℃程度の空気は、空気冷却
器3を通過することによって18℃程度に冷却されて室内
6に戻る。他方入口管41の15℃程度の冷却水は、空気冷
却器3を通過することによって26℃程度に加熱されて出
口管42に入り、冷却塔20を通過することによって15℃程
度に冷却されて入口管41に戻る。Next, the operation of this embodiment will be described. In the winter season, when the outside air temperature is about 10 ° C., the cooling water of about 15 ° C. can be taken out only by the capacity of the cooling tower 20 alone. Is stopped, and only the cooling tower 20 is operated. At this time, the air at about 28 ° C. in the room 6 is cooled to about 18 ° C. by passing through the air cooler 3 and returns to the room 6. On the other hand, the cooling water of about 15 ° C. in the inlet pipe 41 is heated to about 26 ° C. by passing through the air cooler 3, enters the outlet pipe 42, and cooled to about 15 ° C. by passing through the cooling tower 20. Return to the inlet pipe 41.
冷却負荷又は外気温度の変動に関する調整については
次のようにして行う。すなわち各室毎の冷却能力の調整
については、各室毎に設けたサーモスタット7による検
出温度に基づいて、電動混合3方弁で構成した空気冷却
器バイパス弁8の開度を調節する。外気温度の変動に伴
う装置全体の冷却能力の調整については、入口管41に設
けたサーモスタット43による検出温度に基づいて、冷却
塔のファン22もしくは散水流量又はその両方を調節す
る。但し装置全体の冷却能力は、入口管41と出口管42と
を連絡する室外機バイパス弁44の開度調節を併せて行っ
てもよく、またこれのみによって行ってもよい。The adjustment relating to the fluctuation of the cooling load or the outside air temperature is performed as follows. That is, for the adjustment of the cooling capacity of each chamber, the opening of the air cooler bypass valve 8 composed of the electric mixing three-way valve is adjusted based on the temperature detected by the thermostat 7 provided for each chamber. As for the adjustment of the cooling capacity of the entire apparatus in accordance with the fluctuation of the outside air temperature, the cooling tower fan 22 and / or the water spray flow rate are adjusted based on the temperature detected by the thermostat 43 provided in the inlet pipe 41. However, the cooling capacity of the entire apparatus may be adjusted by adjusting the opening degree of the outdoor unit bypass valve 44 that connects the inlet pipe 41 and the outlet pipe 42, or may be adjusted only by this.
以上によって冬期には消費電力量の大きな中間サイク
ル10と圧縮式チラー30を停止したまま、必要な冷却効果
を得ることができる。As described above, in the winter season, the required cooling effect can be obtained while the intermediate cycle 10 and the compression chiller 30 consuming a large amount of power are stopped.
次に春秋期において、空気冷却器バイパス弁8を全閉
とし冷却塔20を全出力運転としても、いずれかの室内6
においてなお十分な冷却効果を得られないときは、当該
室内6の中間サイクル10を稼働させると、室内6の28℃
程度の空気は、空気冷却器3を通過することによって23
℃程度に冷却され、中間サイクルの蒸発器14を通過する
ことによって更に18℃程度に冷却されて室内6に戻る。
中間サイクル10では蒸発器14で吸熱した熱を水冷式凝縮
器12で放熱する。他方入口管41の21℃程度の冷却水は、
空気冷却器3を通過することによって25℃程度に加熱さ
れ、中間サイクルの水冷式凝縮器12を通過することによ
って更に29℃程度に加熱されて出口管42に至り、冷却塔
20を通過することによって21℃程度に冷却されて入口管
41に戻る。Next, during the spring and autumn seasons, even if the air cooler bypass valve 8 is fully closed and the cooling tower 20 is operated at full output,
When the sufficient cooling effect cannot be obtained in the room 6, the intermediate cycle 10 in the room 6 is operated,
Degree of air is passed through the air cooler 3
After cooling to about 18 ° C., it is further cooled to about 18 ° C. by passing through the evaporator 14 of the intermediate cycle and returns to the room 6.
In the intermediate cycle 10, the heat absorbed by the evaporator 14 is radiated by the water-cooled condenser 12. On the other hand, the cooling water of about 21 ° C. of the inlet pipe 41 is
It is heated to about 25 ° C. by passing through the air cooler 3 and further heated to about 29 ° C. by passing through the water-cooled condenser 12 of the intermediate cycle, and reaches the outlet pipe 42,
Inlet pipe cooled to about 21 ° C by passing through 20
Return to 41.
この場合冷却負荷又は外気温度の変動に関する調整に
ついては、冬期のときと同様の調整のほか、中間サイク
ル10の冷却能力の調整を行うこともできる。また空気冷
却器3と中間サイクルの蒸発器14との2段によって空気
の冷却を行っているから、中間サイクル10の起動・停止
による影響度が小さく、すなわち該起動・停止に伴う空
気温度の過度変化は従来の冷却装置と比べて小さい。更
に該過渡変化の緩和については、中間サイクル10の起動
時にはこれと同期させて空気冷却器バイパス弁8を調節
して空気冷却器3への冷却水の流量を若干絞り込み、中
間サイクル10の停止時にはこれと同期させて空気冷却器
バイパス弁8を調節して空気冷却器3への冷却水の流量
を若干増すことよって容易に行うことができる。In this case, as for the adjustment relating to the fluctuation of the cooling load or the outside air temperature, the adjustment of the cooling capacity of the intermediate cycle 10 can be performed in addition to the adjustment in the winter. Further, since the air is cooled by the two stages of the air cooler 3 and the evaporator 14 of the intermediate cycle, the influence of the start / stop of the intermediate cycle 10 is small, that is, the excessive air temperature accompanying the start / stop. The change is small compared to a conventional cooling device. Further, with regard to the mitigation of the transient change, the air cooler bypass valve 8 is adjusted in synchronism with the start of the intermediate cycle 10 to slightly reduce the flow rate of the cooling water to the air cooler 3. This can be easily performed by adjusting the air cooler bypass valve 8 in synchronism with this to slightly increase the flow rate of the cooling water to the air cooler 3.
なお室内機1が1台のとき、又は各室6毎の冷却負荷
に大きな相違がないときには、春秋期における運転方法
として、中間サイクル10の運転を停止して、冷却塔20と
圧縮式チラー30を運転することもできる。この場合冷却
塔10と圧縮式チラー30との2段によって冷却水の冷却を
行っているから、圧縮式チラー30の起動・停止に伴う冷
却水温度の過渡変化は小さい。また該過渡変化の緩和に
ついては、圧縮式チラー30の起動時にはこれと同期させ
て冷却塔20の送風量又は散水量を若干減少させ、圧縮式
チラー30の停止時にはこれと同期させて冷却塔20の送風
量又は散水量を若干増大させることによって容易に行う
ことができる。また圧縮式チラー30の起動・停止に伴う
過渡変化の緩和については、これと同期させた室外機バ
イパス弁44の開度調整を併せて行ってもよいし、これの
みによって行うこともできる。When the number of the indoor units 1 is one, or when there is no significant difference in the cooling load of each room 6, the operation of the intermediate cycle 10 is stopped as the operation method in the spring and autumn, and the cooling tower 20 and the compression chiller 30 are stopped. You can also drive. In this case, since the cooling water is cooled by the two stages of the cooling tower 10 and the compression chiller 30, the transient change of the cooling water temperature due to the start / stop of the compression chiller 30 is small. Regarding the mitigation of the transient change, when the compression chiller 30 is started, the amount of air blown or sprayed from the cooling tower 20 is slightly reduced in synchronization therewith, and when the compression chiller 30 is stopped, the cooling tower 20 is synchronized therewith. This can be easily performed by slightly increasing the amount of air blown or the amount of water sprayed. In addition, the transient change caused by the start / stop of the compression chiller 30 may be alleviated by adjusting the opening degree of the outdoor unit bypass valve 44 in synchronization with this or by using only this.
次に夏期において冷却塔20と中間サイクル10との運
転、又は冷却塔20と圧縮式チラー30との運転によっては
十分な冷却効果が得られないときは、冷却塔20と中間サ
イクル10と圧縮式チラー30とのすべてを稼働させると、
室内6の28℃程度の空気は、空気冷却器3を通過するこ
とによって23℃程度に冷却され、中間サイクルの蒸発器
14を通過することによって更に18℃程度に冷却されて室
内6に戻る。中間サイクル10では蒸発器14で吸熱した熱
を水冷式凝縮器12で放熱する。他方入口管41の21℃程度
の冷却水は、空気冷却器3を通過することによって26℃
程度に加熱され、中間サイクルの水冷式凝縮器12を通過
することによって更に32℃程度に加熱されて出口管42に
至る。次いで冷却塔20において湿球温度26℃程度の外気
をファン22によって送風し、散水温度28℃程度の散布水
を散水ヘッダー25から散水すると、冷却水は冷却塔20の
冷却コイル21を通過することによって28℃程度に冷却さ
れ、更に圧縮式チラー20を通過することによって21℃程
度に冷却されて入口管41に戻る。Next, when a sufficient cooling effect cannot be obtained by the operation of the cooling tower 20 and the intermediate cycle 10 or the operation of the cooling tower 20 and the compression chiller 30 in summer, the cooling tower 20 and the intermediate cycle 10 When you run everything with the chiller 30,
The air at about 28 ° C. in the room 6 is cooled down to about 23 ° C. by passing through the air cooler 3, and the evaporator of the intermediate cycle is
By passing through, it is further cooled to about 18 ° C. and returns to the room 6. In the intermediate cycle 10, the heat absorbed by the evaporator 14 is radiated by the water-cooled condenser 12. On the other hand, the cooling water of about 21 ° C. of the inlet pipe 41 passes through the air cooler 3 to be cooled to 26 ° C.
After passing through the water-cooled condenser 12 of the intermediate cycle, it is further heated to about 32 ° C. and reaches the outlet pipe 42. Next, in the cooling tower 20, outside air having a wet bulb temperature of about 26 ° C. is blown by the fan 22, and spray water having a spray temperature of about 28 ° C. is sprayed from the spray header 25.The cooling water passes through the cooling coil 21 of the cooling tower 20. Is cooled to about 28 ° C., and further cooled to about 21 ° C. by passing through the compression chiller 20, and returns to the inlet pipe 41.
冷却負荷又は外気温度の変動に関する調整について
は、冬期又は春秋期のときと同様の調整が行え、更に圧
縮式チラーの冷却能力調整を行うこともできる。圧縮式
チラーの起動・停止を伴う過渡変化の緩和は、これと同
期させた冷却塔の送風量又は散水量の調節によって、又
は室外機バイパス弁の開度調整によって行うことがで
き、中間サイクル10の起動・停止に伴う過渡変化の緩和
は、これと同期させた空気冷却器バイパス弁の開度調整
によって行うことができる。The adjustment relating to the fluctuation of the cooling load or the outside air temperature can be performed in the same manner as in winter or spring and autumn, and the cooling capacity of the compression chiller can also be adjusted. The transient change accompanying the start / stop of the compression chiller can be mitigated by adjusting the amount of air blown or sprinkled by the cooling tower in synchronization with this, or by adjusting the opening of the outdoor unit bypass valve. The transient change caused by the start / stop of the air cooler can be mitigated by adjusting the opening of the air cooler bypass valve in synchronization with the start / stop.
以上のように消費電力量の大きな中間サイクル10と圧
縮式チラー30とを共に作動させるのは夏期のみとなり、
春秋期には中間サイクルと圧縮式チラーとのいずれかを
運転する必要がなくなり、冬期には中間サイクルも圧縮
式チラーも運転する必要がなくなる。また冷却水は空気
冷却器3と中間サイクル水冷式凝縮器12とで加熱される
から、冷却塔20の熱効率が高まり、その結果圧縮式チラ
ーを運転させる必要が低くなる。これらの結果として年
間を通しての冷却装置の消費電力量を、従来方式に比べ
て約50%程度低減することができる。As described above, it is only in summer that the intermediate cycle 10 having a large power consumption and the compression chiller 30 are operated together,
There is no need to operate either the intermediate cycle or the compression chiller during spring and autumn, and there is no need to operate both the intermediate cycle and the compression chiller during winter. Further, since the cooling water is heated by the air cooler 3 and the intermediate cycle water-cooled condenser 12, the thermal efficiency of the cooling tower 20 is increased, and as a result, the necessity of operating the compression chiller is reduced. As a result, the power consumption of the cooling device throughout the year can be reduced by about 50% compared to the conventional method.
また空気の冷却も冷却水の冷却も2段によって行って
いるから、中間サイクル10又は圧縮式チラー30の起動・
停止による影響度は小さく、且つ該起動・停止による過
渡変化を容易に緩和することができる。更に複数の室内
6の各々に対して空気冷却器3と中間サイクル10とを設
ければ、各室6毎の熱負荷の相違に容易に対処すること
ができるし、上記のように冷却塔10の熱効率が高くなっ
ているから、冷却水配管41,42の口径を小さくすること
ができ、循環ポンプ40の動力の節約や配管工事費の節減
なども図ることができる。In addition, since both air cooling and cooling water cooling are performed in two stages, the start-up of the intermediate cycle 10 or the compression chiller 30
The degree of influence due to the stop is small, and the transient change due to the start / stop can be easily mitigated. Further, if the air cooler 3 and the intermediate cycle 10 are provided for each of the plurality of chambers 6, it is possible to easily cope with the difference in heat load between the respective chambers 6, and as described above, the cooling tower 10 Since the heat efficiency of the cooling water pipes 41 and 42 is high, the diameters of the cooling water pipes 41 and 42 can be reduced, so that the power of the circulating pump 40 can be saved and the cost of piping work can be reduced.
次に第2図から第4図は本発明の空気冷却装置の別の
実施例の要部系統図であり、空気冷却器3で若しくは中
間サイクルの蒸発器14で、又はその両方で除湿した後、
空気を所定温度まで再加熱するためのレヒート装置に関
し、中間サイクルの蒸発器14の空気流後段に空気再熱器
50を設けたものである。このうち第2図は中間サイクル
の水冷式凝縮器12出口の冷却水を空気再熱器50を介して
出口管42に導き、かつ空気再熱器50を迂回する空気再熱
器バイパス弁51を設けたものであり、本装置の冷却水と
して利用できる最も高い温度を熱源とし、かつその熱源
の量を調整自在としたものである。Next, FIGS. 2 to 4 are main part system diagrams of another embodiment of the air cooling device of the present invention, after dehumidification by the air cooler 3 or the intermediate cycle evaporator 14 or both. ,
Regarding a reheat device for reheating air to a predetermined temperature, an air reheater is provided after the air flow of the evaporator 14 in the intermediate cycle.
50 is provided. 2 shows the cooling water at the outlet of the water-cooled condenser 12 of the intermediate cycle through the air reheater 50 to the outlet pipe 42, and the air reheater bypass valve 51 that bypasses the air reheater 50. The highest temperature that can be used as cooling water of the present apparatus is used as a heat source, and the amount of the heat source is adjustable.
また第3図は空気冷却器3出口の冷却水を空気再熱器
50を介して水冷式凝縮器12に導き、かつ空気再熱器バイ
パス弁51を設けたものであり、夏期・春秋期の中間サイ
クル10稼働時に、上記第2図の構成における熱源ほど高
温の熱源を要しない場合には、この第3図の構成とする
ことができる。Fig. 3 shows the cooling water at the outlet of the air cooler 3
The heat source is guided to the water-cooled condenser 12 through the air inlet 50, and an air reheater bypass valve 51 is provided. During the operation of the intermediate cycle 10 in the summer / spring / autumn season, the heat source in the configuration of FIG. In the case where is not required, the configuration shown in FIG. 3 can be adopted.
第4図は空気冷却器3出口の冷却水を分岐させて空気
再熱器50に導き、調整弁52を介して出口管42に合流させ
たものであり、冬期に中間サイクル10を運転しないとき
にのみ除湿が必要である場合には、このような構成によ
って水冷式凝縮器12を通過することによる圧力損失を回
避することができる。なおこの第4図の構成は水冷式凝
縮器12と空気再熱器50とを並列に配置しているから、前
者の圧力損失が後者の圧力損失よりも十分に大きいとき
には、上記調整弁52に代えて、空気再熱器50に直列に流
量制御弁を配置してもよい。FIG. 4 shows the case where the cooling water at the outlet of the air cooler 3 is branched, guided to the air reheater 50, and joined to the outlet pipe 42 via the regulating valve 52, and when the intermediate cycle 10 is not operated in winter. When dehumidification is necessary only for such a case, the pressure loss caused by passing through the water-cooled condenser 12 can be avoided by such a configuration. In the configuration of FIG. 4, since the water-cooled condenser 12 and the air reheater 50 are arranged in parallel, when the former pressure loss is sufficiently larger than the latter, the regulating valve 52 Alternatively, a flow control valve may be arranged in series with the air reheater 50.
以上のように空気再熱器50を配置したときには、各室
毎の冷却能力の調整や、中間サイクル10の起動・停止に
伴う過渡変化の緩和は、空気冷却器バイパス弁8の開度
調整に代えて、又はそれと共に、上記空気再熱器バイパ
ス弁51又は調整弁52の開度調整によって行うこともでき
る。When the air reheater 50 is arranged as described above, the adjustment of the cooling capacity of each room and the mitigation of the transient change caused by the start / stop of the intermediate cycle 10 are performed by adjusting the opening of the air cooler bypass valve 8. Alternatively, or together with this, the opening degree of the air reheater bypass valve 51 or the regulating valve 52 may be adjusted.
また空気再熱器50の熱源については上記の他に、入口
管41の冷却水を調整弁を介して空気再熱器50に導き、出
口管42に合流させることもできる。また春秋期又は夏期
において中間サイクルの圧縮機11が運転している場合
に、従来と同様圧縮機11出口の冷媒を調整弁を介して空
気再熱器50に導き、水冷式凝縮器12出口の冷媒に合流さ
せることもできるし、更に空気再熱器50の熱源として電
熱を用いることもできる。As for the heat source of the air reheater 50, in addition to the above, the cooling water of the inlet pipe 41 can be guided to the air reheater 50 via the regulating valve and merged with the outlet pipe 42. In addition, when the compressor 11 of the intermediate cycle is operating in the spring or autumn or summer, the refrigerant at the outlet of the compressor 11 is guided to the air reheater 50 through the regulating valve as in the related art, and the water at the outlet of the water-cooled condenser 12 is provided. The heat can be combined with the refrigerant, and electric heat can also be used as a heat source of the air reheater 50.
以上において本冷却装置の配置については、中間サイ
クルの圧縮機11を室外に配置すれば、室内機1の運転音
を減少させることができ、水冷式凝縮器12を室外に配置
すれば、室内機1がコンパクトとなる。また冷却塔20の
中に圧縮式チラー30を組み込めば、室外機の設置面積を
減少させることができる。これらの例として第5図に、
冷却塔20の中に圧縮式チラー30と中間サイクルの圧縮機
11及び水冷式凝縮器12を組み込んだものを示す。With respect to the arrangement of the present cooling device, the operation noise of the indoor unit 1 can be reduced by arranging the compressor 11 of the intermediate cycle outdoors, and the indoor unit can be reduced by arranging the water-cooled condenser 12 outdoors. 1 becomes compact. If the compression chiller 30 is incorporated in the cooling tower 20, the installation area of the outdoor unit can be reduced. As an example of these, FIG.
Compression chiller 30 in cooling tower 20 and intermediate cycle compressor
1 shows a structure incorporating a water-cooled condenser 11 and 11.
また以上説明した各系統のいずれか又はすべての系統
を複数とすることができる。例えば室内機1について
は、各室6毎に空気冷却器3と中間サイクルの蒸発器14
を及び必要により空気再熱器50を配置することができる
し、室外機については、冷却塔20と圧縮式チラー30との
いずれか又は双方を複数台配置することができる。Further, any or all of the above-described systems may be provided in plural. For example, for the indoor unit 1, the air cooler 3 and the evaporator
In addition, the air reheater 50 can be disposed if necessary, and as for the outdoor unit, one or both of the cooling tower 20 and the compression chiller 30 can be disposed.
[発明の効果] 本発明は、以上説明のごとく冷却塔によって中間サイ
クルの水冷式凝縮器の冷却のほか空気冷却器をも冷却
し、また冷却塔に圧縮式チラーを附設してあるから、中
間サイクルと圧縮式チラーとの運転時間を大幅に減らす
ことができ、年間当たりの冷却装置の消費電力を大幅に
低減できるものである。[Effect of the Invention] As described above, the present invention cools not only the water-cooled condenser of the intermediate cycle but also the air cooler by the cooling tower, and the cooling tower is provided with a compression chiller. The operation time of the cycle and the compression chiller can be greatly reduced, and the power consumption of the cooling device per year can be significantly reduced.
第1図と第5図は本発明の一実施例を示す系統図、第2
図から第4図は本発明の別の実施例の要部を示す系統
図、第6図は従来の冷却システムの系統図である。 1……室内機、2……空気濾過器、3……空気冷却器 4……送風機、5……ダクト、6……室内 7……サーモスタット、8……空気冷却器バイパス弁 10……中間サイクル、11……圧縮機 12……水冷式凝縮器、13……膨張弁、14……蒸発器 20……密閉式冷却塔、21……冷却コイル、22……ファン 23……散水槽、24……散水ポンプ、25……散水ヘッダー 30……圧縮式チラー、31……圧縮機、32……凝縮器 33……膨張弁、34……蒸発器、40……循環ポンプ 41……入口管、42……出口管、43……サーモスタット 44……室外機バイパス弁、50……空気再熱器 51……空気再熱器バイパス弁、52……調整弁FIGS. 1 and 5 are system diagrams showing one embodiment of the present invention, and FIG.
FIG. 4 to FIG. 4 are system diagrams showing main parts of another embodiment of the present invention, and FIG. 6 is a system diagram of a conventional cooling system. 1 ... indoor unit, 2 ... air filter, 3 ... air cooler 4 ... blower, 5 ... duct, 6 ... indoor 7 ... thermostat, 8 ... air cooler bypass valve 10 ... intermediate Cycle, 11 Compressor 12 Water-cooled condenser 13 Expansion valve 14 Evaporator 20 Closed cooling tower 21 Cooling coil 22 Fan 23 Sprinkler tank 24 ... watering pump, 25 ... watering header 30 ... compression chiller, 31 ... compressor, 32 ... condenser 33 ... expansion valve, 34 ... evaporator, 40 ... circulation pump 41 ... inlet Pipe, 42… Outlet pipe, 43… Thermostat 44… Outdoor unit bypass valve, 50… Air reheater 51… Air reheater bypass valve, 52… Adjustment valve
Claims (7)
の順に冷媒を循環させて前記蒸発器で空気と熱交換をさ
せて該空気を冷却する空気冷却装置において、前記蒸発
器を通過する空気流の前段側に空気冷却器を附設し、密
閉式冷却塔、圧縮式チラー、前記空気冷却器及び前記水
冷式凝縮器の順に冷却水を循環させて前記空気冷却器で
前記空気と熱交換をさせると共に前記水冷式凝縮器で前
記冷媒と熱交換をさせ、前記密閉式冷却塔及び前記圧縮
式チラーにおいて放熱をさせたことを特徴とする空気冷
却装置。1. An air cooling device for circulating a refrigerant in the order of a compressor, a water-cooled condenser, an expansion valve and an evaporator to exchange heat with air in the evaporator to cool the air. An air cooler is attached to the upstream side of the passing air flow, and cooling water is circulated in the order of a closed cooling tower, a compression chiller, the air cooler, and the water-cooled condenser, and the air is cooled by the air cooler. An air cooling device, wherein heat is exchanged, heat exchange is performed with the refrigerant in the water-cooled condenser, and heat is radiated in the closed cooling tower and the compression chiller.
流の後段側に空気再熱器を附設し、前記水冷式凝縮器出
口の前記冷却水を前記空気再熱器を介して前記密閉式冷
却塔に導いた請求項1記載の空気冷却装置。2. An air reheater is provided on a downstream side of an air flow passing through the air cooler and the evaporator, and the cooling water at the outlet of the water-cooled condenser is supplied to the air reheater via the air reheater. The air cooling device according to claim 1, wherein the air cooling device is led to a closed cooling tower.
流の後段側に空気再熱器を附設し、前記空気冷却器出口
の前記冷却水を前記空気再熱器を介して前記水冷式凝縮
器に導いた請求項1記載の空気冷却装置。3. An air reheater is provided on a downstream side of an air flow passing through the air cooler and the evaporator, and the cooling water at the outlet of the air cooler is cooled by the water cooling through the air reheater. 2. The air cooling device according to claim 1, wherein the air cooling device is led to a condenser.
流の後段側に空気再熱器を附設し、前記空気冷却器出口
より分岐させた前記冷却水を前記空気再熱器に通過させ
た後前記水冷式凝縮器出口の前記冷却水に合流させた請
求項1記載の空気冷却装置。4. An air reheater is provided on the downstream side of an air flow passing through the air cooler and the evaporator, and the cooling water branched from the air cooler outlet passes through the air reheater. The air cooling device according to claim 1, wherein the cooling water is joined to the cooling water at the outlet of the water-cooled condenser after the cooling.
いずれか一方を前記空気冷却器及び蒸発器より離隔して
配置した請求項1、2、3又は4記載の空気冷却装置。5. The air cooling device according to claim 1, wherein at least one of the compressor and the water-cooled condenser is disposed apart from the air cooler and the evaporator.
チラーを前記密閉式冷却塔の内部に組み込んだ請求項
1、2、3又は4記載の空気冷却装置。6. The air cooling device according to claim 1, wherein the compressor, the water-cooled condenser and the compression chiller are incorporated in the closed cooling tower.
た請求項1から6のいずれかに記載の空気冷却装置。7. The air cooling device according to claim 1, wherein a plurality of the air coolers and the evaporators are arranged.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP4101389A JP2651717B2 (en) | 1988-12-28 | 1989-02-21 | Air cooling system |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63-332157 | 1988-12-28 | ||
JP33215788 | 1988-12-28 | ||
JP4101389A JP2651717B2 (en) | 1988-12-28 | 1989-02-21 | Air cooling system |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH02259367A JPH02259367A (en) | 1990-10-22 |
JP2651717B2 true JP2651717B2 (en) | 1997-09-10 |
Family
ID=26380538
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP4101389A Expired - Lifetime JP2651717B2 (en) | 1988-12-28 | 1989-02-21 | Air cooling system |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2651717B2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101239360B1 (en) | 2010-11-24 | 2013-03-05 | 유도썬스(주) | Injection Molding of Cooling System |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8411439B1 (en) * | 2007-09-28 | 2013-04-02 | Exaflop Llc | Cooling diversity in data centers |
JP5843630B2 (en) * | 2012-01-25 | 2016-01-13 | 三菱電機株式会社 | Cooling system |
-
1989
- 1989-02-21 JP JP4101389A patent/JP2651717B2/en not_active Expired - Lifetime
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101239360B1 (en) | 2010-11-24 | 2013-03-05 | 유도썬스(주) | Injection Molding of Cooling System |
Also Published As
Publication number | Publication date |
---|---|
JPH02259367A (en) | 1990-10-22 |
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