JP3467407B2 - Refrigeration equipment - Google Patents
Refrigeration equipmentInfo
- Publication number
- JP3467407B2 JP3467407B2 JP12710998A JP12710998A JP3467407B2 JP 3467407 B2 JP3467407 B2 JP 3467407B2 JP 12710998 A JP12710998 A JP 12710998A JP 12710998 A JP12710998 A JP 12710998A JP 3467407 B2 JP3467407 B2 JP 3467407B2
- Authority
- JP
- Japan
- Prior art keywords
- evaporator
- refrigerant
- plate
- pipe
- liquid
- 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 - Fee Related
Links
Landscapes
- Other Air-Conditioning Systems (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、冷凍装置に係り、
特に一般空調産業や低冷水温度の必要な工業の分野で使
用する冷凍装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration system,
In particular, the present invention relates to a refrigerating device used in the general air conditioning industry and the industrial field requiring low cold water temperature.
【０００２】[0002]
【従来の技術】近年、地球温暖化に伴う温室効果ガス発
生量の削減が論議されている状況下において、省エネル
ギーに伴う各種の検討、技術開発が活発化する趨勢にあ
る。例えば、空調産業においても、深夜電力を利用した
氷蓄熱システムが注目されているものの、初期設備投資
に必要とするコストが問題となることがある。一般的な
水蓄熱システムのチューブプレート式の蓄氷部では、凍
結という技術的課題があり、従来、凍結事故を配慮して
冷水温度は４℃前後が限度として運用されてきた。例え
ば、日本冷凍協会発行第５版「冷凍空調便覧，２巻，機
器編」Ｐ．２８６に記載されているとおり、一般には冷
水温度は５℃や７℃の仕様となつている。2. Description of the Related Art In recent years, under the circumstances where reduction of greenhouse gas generation amount due to global warming is being discussed, various studies and technological developments associated with energy saving are becoming active. For example, even in the air conditioning industry, although an ice heat storage system that uses late-night power is drawing attention, the cost required for initial capital investment may become a problem. The tube plate type ice storage unit of a general water heat storage system has a technical problem of freezing, and conventionally, the cold water temperature has been limited to around 4 ° C in consideration of a freezing accident. For example, P.P. As described in 286, the cold water temperature is generally specified as 5 ° C. or 7 ° C.
【０００３】一方、最近では、既設の水蓄熱設備を流用
して、さらに低温域の冷水温度製造の需要が高まってい
る。既に小容量領域では、レシプロ形圧縮機を用いプレ
ート式熱交換器を用いた冷凍装置で０℃に近い低温冷水
を得ている。On the other hand, recently, there is an increasing demand for manufacturing cold water temperature in a low temperature region by utilizing existing water heat storage equipment. In the small-capacity region, low-temperature cold water close to 0 ° C. has already been obtained with a refrigerating apparatus using a plate heat exchanger using a reciprocating compressor.
【０００４】また、中大容量になると、プレート式蒸発
器で１００％の冷凍容量を満足させようとするとプレー
ト式熱交換器が大型になり設置スペースの増大、コスト
の増加等の問題がある。また、従来の満液式蒸発器を有
する冷凍装置で低温水取り出しを行うには、安定した負
荷パターンの場合を除き、冷水量の変動あるいは経年的
なチューブの汚れによる伝熱性能低下で、凍結によるチ
ューブ破裂、機内浸水の恐れがあるため、実用上冷水出
口温度には限界があった。When the plate type evaporator has a medium capacity and a large capacity, the plate type heat exchanger has a large size in order to satisfy 100% of the refrigerating capacity, resulting in problems such as an increase in installation space and an increase in cost. In addition, in order to take out low temperature water with a conventional freezer with a full-fill type evaporator, unless the load pattern is stable, fluctuations in the amount of cold water or deterioration in heat transfer performance due to aging tube fouling will cause freezing. Due to the risk of tube rupture due to water leakage and in-machine flooding, there was a practical limit to the cold water outlet temperature.
【０００５】一般に、低温冷水を得るためには、冷水を
流通させる冷水管、すなわちチューブ内の冷水が凍結し
ないようにする必要がある。満液式蒸発器で０℃付近ま
で冷却すると、冷水量の変動や、スケール付着によるチ
ューブの熱伝達率が低下する場合には、チューブ出口パ
ス側で凍結する恐れがある。一方、プレート式熱交換器
では、プレート内に形成される通路を冷媒が流通し、プ
レート外表面に冷水を自然流下させる構造であるため、
表面に結氷しても氷の膨脹等による異常荷重の発生はな
く、損傷の恐れはない。In general, in order to obtain low-temperature cold water, it is necessary to prevent the cold water in the cold water pipe, that is, the cold water in the tube, from freezing. Cooling to around 0 ° C. in a full-fill type evaporator may cause freezing on the tube exit path side when the amount of cold water fluctuates and the heat transfer coefficient of the tube decreases due to scale adhesion. On the other hand, in the plate heat exchanger, since the refrigerant flows through the passage formed in the plate, the cold water naturally flows down to the outer surface of the plate.
Even if the surface freezes, no abnormal load is generated due to the expansion of ice, and there is no risk of damage.
【０００６】ところで、プレート式熱交換器の場合、容
量増加に対応するには、規格寸法で成形されるプレート
の枚数を増やす手段が考えられる。しかし、冷水の流下
によるプレート間の影響をなくすためにある程度のプレ
ート間隔が必要であり、密集した伝熱管群の構成で小形
化が可能な満液式蒸発器の場合のようには対応できな
い。このため、装置が大形化し設置面積の確保およびコ
スト面の増加という不具合がある。By the way, in the case of the plate type heat exchanger, in order to cope with the increase in capacity, a means of increasing the number of plates formed with standard dimensions can be considered. However, in order to eliminate the influence between the plates due to the flow of cold water, it is necessary to have a certain plate interval, and it is not possible to cope with it in the case of a full-fill type evaporator that can be miniaturized by the configuration of dense heat transfer tube groups. As a result, the size of the device becomes large, and there is a problem that the installation area is secured and the cost is increased.
【０００７】このため、満液式蒸発器による小形化、プ
レート式熱交換器による凍結に対する信頼性の各メリツ
トを有効利用し、満液式蒸発器にできるだけ多くの容量
を受け持たせて、可能な範囲の低い冷水温度まで冷却
し、さらに残りの容量をプレート式熱交換器で分担して
冷水温度を０℃付近まで冷却するシリーズフローの方式
が開発された。For this reason, it is possible to make full use of the capacity of the full-fill type evaporator by effectively utilizing the advantages of downsizing by the full-fill type evaporator and reliability of freezing by the plate heat exchanger. A series flow system has been developed in which the cold water temperature is cooled to a low range, and the remaining capacity is shared by the plate heat exchanger to cool the cold water temperature to around 0 ° C.
【０００８】[0008]
【発明が解決しようとする課題】上記方式における実用
上の課題として、飽和温度が０℃以下となるプレート式
蒸発器のプレート外表面に付着する氷の影響がある。氷
が付着すると、プレート式蒸発器の熱伝達性能が低下
し、性能不足を起こすおそれがある。このため、解氷手
段が必要となる。As a practical problem in the above method, there is an influence of ice adhering to the outer surface of the plate of the plate evaporator having a saturation temperature of 0 ° C. or lower. If ice adheres, the heat transfer performance of the plate-type evaporator may be deteriorated and the performance may be insufficient. For this reason, a means for thawing ice is required.
【０００９】本発明は、上記従来技術の課題を解決する
ためになされたもので、中大容量の低温冷水を製造し、
コスト的に安価で、かつ凍結に対して信頼性の高い冷凍
装置を提供することを、その目的とするものである。The present invention has been made to solve the above-mentioned problems of the prior art, and produces low temperature cold water of medium and large capacity,
It is an object of the present invention to provide a refrigerating device which is inexpensive in cost and has high reliability against freezing.
【００１０】[0010]
【課題を解決するための手段】上記目的を達成するため
に、本発明に係る冷凍装置の第１の構成は、圧縮機、凝
縮器、蒸発器、およびこれらを接続する冷媒系統を備え
て冷凍サイクルを構成し、蒸発器に通水する冷水系統を
有する冷凍装置において、前記蒸発器として満液式蒸発
器とプレート式蒸発器を併用して、冷水を前記満液式蒸
発器に通水し、さらに前記プレート式蒸発器で０℃付近
まで冷却するように構成するとともに、少なくとも、前
記プレート式蒸発器の冷媒系統入口に設けた冷媒供給弁
と、前記プレート式蒸発器の冷媒系統出口からの液，ガ
ス混合冷媒を気液分離させるサージドラムと、分離され
た冷媒ガスを圧縮機吸込口に導く配管とを備え、前記凝
縮器から前記プレート式蒸発器に至る冷媒ガスバイパス
配管および該配管途中に弁を設け、前記プレート式蒸発
器の内圧相当部位に圧力検知器を設け、前記プレート式
蒸発器のプレート表面が結氷したときに、前記圧力検知
器の検知信号を用いて、蒸発圧力が或る設定圧力を下回
ると、前記バイパス配管途中の弁を開にし、かつ前記プ
レート式蒸発器入口部の前記冷媒供給弁を閉じて解氷運
転を行い、蒸発圧力が別の設定圧力まで回復すると、前
記バイパス配管途中の弁を閉じ、かつ前記冷媒供給弁を
開にして解氷運転を解除するように制御回路を構成した
ものである。In order to achieve the above-mentioned object, a first structure of a refrigerating apparatus according to the present invention comprises a compressor, a condenser, an evaporator, and a refrigerant system for connecting them to perform refrigeration. In a refrigerating apparatus that constitutes a cycle and has a cold water system that allows water to pass through to an evaporator, a flood type evaporator and a plate type evaporator are used together as the evaporator, and cold water is passed through the flood type evaporator. Further, the plate evaporator is configured to cool to around 0 ° C., and at least the refrigerant supply valve provided at the refrigerant system inlet of the plate evaporator and the refrigerant system outlet of the plate evaporator are provided. A refrigerant gas bypass pipe from the condenser to the plate evaporator and the pipe, which includes a surge drum for separating liquid and gas mixed refrigerant into gas and liquid, and a pipe for guiding the separated refrigerant gas to a compressor suction port A valve is provided inside, and a pressure detector is provided at a portion corresponding to the internal pressure of the plate-type evaporator, and when the plate surface of the plate-type evaporator freezes, the evaporating pressure is detected by using the detection signal of the pressure detector. When it falls below a certain set pressure, the valve in the middle of the bypass pipe is opened, and the refrigerant supply valve at the inlet of the plate type evaporator is closed to perform the deicing operation, and the evaporation pressure is recovered to another set pressure. The control circuit is configured so that the valve in the middle of the bypass pipe is closed and the refrigerant supply valve is opened to cancel the deicing operation.
【００１１】また、上記目的を達成するために、本発明
に係る冷凍装置の第２の構成は、上記第１の構成に加え
て、解氷運転に入ると、圧縮機の吸込部に設けられてい
る容量制御装置のベーンダンパーを最低可能制御開度ま
で絞つて保持するようにし、解氷運転が解除されると、
元の自動温度調整回路に切り替わるようにしたものであ
る。Further, in order to achieve the above object, the second structure of the refrigerating apparatus according to the present invention, in addition to the first structure, is provided in the suction part of the compressor when the defrosting operation is started. The vane damper of the capacity control device that is being held is squeezed and held to the minimum possible control opening, and when the thawing operation is canceled,
It is designed to switch to the original automatic temperature control circuit.
【００１２】[0012]
【発明の実施の形態】以下、本発明の実施の形態を図１
を参照して説明する。図１は、本発明の一実施の形態を
示す冷凍装置の系統図である。図中、矢印は冷媒および
冷水の流れを示すものである。図１において、１は、冷
凍サイクルを構成する満液式蒸発器、２は、満液式蒸発
器１と併用して冷凍サイクルを構成するプレート式蒸発
器、３は、プレート式蒸発器２で発生する気液混合冷媒
の気液を分離するサージドラム、４は、満液式蒸発器１
と圧縮機６とを結ぶ冷媒ガス配管２１に設けた電動弁、
５は、冷凍サイクルを構成する凝縮器、６は圧縮機、７
は、圧縮機６を駆動する電動機、８は、圧縮機６の吸込
側の容量制御装置である。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to FIG.
Will be described with reference to. FIG. 1 is a system diagram of a refrigeration system showing an embodiment of the present invention. In the figure, arrows indicate the flows of the refrigerant and the cold water. In FIG. 1, 1 is a full-fill type evaporator that constitutes a refrigeration cycle, 2 is a plate-type evaporator that is used in combination with the full-fill type evaporator 1 to form a refrigeration cycle, and 3 is a plate-type evaporator 2. The surge drums 4 for separating the generated gas-liquid mixed gas-liquid refrigerant are the liquid-filled evaporator 1
And a motor-operated valve provided in the refrigerant gas pipe 21 that connects the compressor 6 to the compressor 6,
5 is a condenser which constitutes a refrigeration cycle, 6 is a compressor, 7
Is a motor for driving the compressor 6, and 8 is a capacity control device on the suction side of the compressor 6.
【００１３】９は、凝縮器５からプレート式蒸発器２の
入口部に至る冷媒ガスバイパス配管、１０は、その冷媒
ガスバイパス配管９の途中に設けられた電磁弁、１１
（１１−１，１１−２の総称）は、プレート式蒸発器２
の入口部の冷媒供給弁で、冷媒供給弁１１は、冷媒配管
２０に設けられている。１２は、満液式蒸発器１の冷水
出口側の冷水配管１３に具備した温度検知器、１８は、
プレート式蒸発器２の最終冷水出口側の冷水配管１６に
具備した温度検知器、１７は、前記冷水配管１６に設け
た冷水ポンプである。Reference numeral 9 is a refrigerant gas bypass pipe extending from the condenser 5 to the inlet of the plate type evaporator 2, 10 is an electromagnetic valve provided in the middle of the refrigerant gas bypass pipe 9, 11
The plate type evaporator 2 is a general term for 11-1 and 11-2.
The refrigerant supply valve 11 is provided in the refrigerant pipe 20 at the inlet portion of the refrigerant supply valve 11. 12 is a temperature detector provided in the cold water pipe 13 on the cold water outlet side of the liquid-filled evaporator 1, and 18 is
The temperature detector provided in the cold water pipe 16 on the final cold water outlet side of the plate type evaporator 2 is a cold water pump 17 provided in the cold water pipe 16.
【００１４】１３は、満液式蒸発器１とプレート式蒸発
器２との間を接続する冷水配管、１９（１９−１，１９
−２の総称）は、冷水配管１３に設けた仕切り弁であ
る。２０は、圧縮機６，凝縮器５，満液式蒸発器１，プ
レート式蒸発器２を接続する冷媒系統の冷媒配管、２１
は、満液式蒸発器１，圧縮機６間の冷媒ガス配管、２２
は、プレート式蒸発器２，サージドラム３間の冷媒配
管、２３は、サージドラム３，圧縮機６間の冷媒ガス配
管、２４は、サージドラム３，プレート式蒸発器２間の
冷媒配管で、プレート式蒸発器２における冷媒循環回路
を構成する。２５は、クーリングタワーへ通じ凝縮器５
の冷却管群に冷却水を流通させる冷却水系統である。ま
た、３１は、電動機７の冷却系を示す。Reference numeral 13 is a cold water pipe connecting between the full liquid type evaporator 1 and the plate type evaporator 2, and 19 (19-1, 19).
-2) is a sluice valve provided in the cold water pipe 13. Reference numeral 20 is a refrigerant pipe of a refrigerant system that connects the compressor 6, the condenser 5, the liquid-filled evaporator 1, and the plate-type evaporator 2, 21
Is a refrigerant gas pipe between the liquid-filled evaporator 1 and the compressor 6, 22
Is a refrigerant pipe between the plate evaporator 2 and the surge drum 3, 23 is a refrigerant gas pipe between the surge drum 3 and the compressor 6, 24 is a refrigerant pipe between the surge drum 3 and the plate evaporator 2, A refrigerant circulation circuit in the plate evaporator 2 is configured. 25 leads to the cooling tower and condenser 5
It is a cooling water system for circulating cooling water through the cooling pipe group. Reference numeral 31 indicates a cooling system of the electric motor 7.
【００１５】図１に示すように、本実施の形態の冷凍装
置は、主要機器として、満液式蒸発器１、プレート式蒸
発器２、サージドラム３、電動弁４、凝縮器５、圧縮機
６、電動機７、容量制御装置８、冷媒ガスバイパス配管
９、電動弁１０、および冷媒系統、冷水系統により構成
される。As shown in FIG. 1, the refrigerating apparatus according to the present embodiment has, as main components, a liquid-filled evaporator 1, a plate evaporator 2, a surge drum 3, an electric valve 4, a condenser 5, and a compressor. 6, the electric motor 7, the capacity control device 8, the refrigerant gas bypass pipe 9, the electric valve 10, the refrigerant system, and the cold water system.
【００１６】満液式蒸発器１は、詳細を図示しないが、
一般に良く知られているように、容器内に冷水管群（チ
ューブバンドル）が設けられ、そのチューブ１ａ内に冷
水が流通し、チューブ１ａ外は冷媒に浸っている。チュ
ーブ１ａ内面には、図示しないが熱伝達率を促進するた
めの突起が形成されている。１ｂはエリミネータを示
す。The full-fill type evaporator 1 is not shown in detail, but
As is generally well known, a cold water pipe group (tube bundle) is provided in a container, cold water flows through the tube 1a, and the outside of the tube 1a is immersed in a refrigerant. Although not shown, a projection is formed on the inner surface of the tube 1a to promote the heat transfer coefficient. 1b shows an eliminator.
【００１７】また、プレート式蒸発器２は、詳細を図示
しないが、一般に良く知られているように、数枚のプレ
ートが所定の間隔で配列され、上部には、外部配管から
供給される冷水の受水槽１４を設けており、受水槽１４
の底には、各プレート上部より冷水を表面に流下させる
ための多数の小孔が穿孔されている。プレートは対接す
るプレート間に冷媒通路を形成してあり、この冷媒通路
内の冷媒はプレート外表面を流下する冷水と熱交換され
冷媒の一部がガス化し、プレートから出たのち、気液混
合状態で冷媒配管２２を経てサージドラム３に送られ
る。サージドラム３の内部は、詳細を図示しないが、一
般に知られているように、冷媒液とガスを分離する多孔
板を設けたものである。Although not shown in detail in the plate type evaporator 2, as is generally well known, several plates are arranged at a predetermined interval, and cold water supplied from an external pipe is provided at the upper part. The water receiving tank 14 of
In the bottom of the plate, a large number of small holes are formed to allow cold water to flow down from the top of each plate to the surface. The plates form a refrigerant passage between the plates facing each other.The refrigerant in the refrigerant passage is heat-exchanged with the cold water flowing down the outer surface of the plate, a part of the refrigerant is gasified, and after exiting the plate, gas-liquid mixing is performed. In this state, it is sent to the surge drum 3 via the refrigerant pipe 22. Although not shown in detail, the inside of the surge drum 3 is provided with a perforated plate for separating the refrigerant liquid and the gas, as is generally known.
【００１８】次に、本実施の形態の冷凍装置の動作につ
いて図１を参照して説明する。負荷側から冷水ポンプ
（図示せず）で供給される冷水は、まず満液式蒸発器１
に冷水管群（チューブバンドル）を構成するチューブ１
ａ内を流通する。例えば１２℃で流入する冷水は、ここ
で冷媒液と熱交換して４℃まで冷却される。満液式蒸発
器１の冷水出口側の冷水配管１３に具備された温度検知
器１２により冷水温度を検知する。この検知温度と制御
装置（３０）に予め設定された所定の設定温度との差を
極力ゼロにするように、満液式蒸発器１から発生し冷媒
ガス配管２１を経て圧縮機６に導かれる冷媒ガス量を、
前記制御装置により電動弁４を作動させて自動調整す
る。Next, the operation of the refrigerating apparatus of this embodiment will be described with reference to FIG. The cold water supplied by the cold water pump (not shown) from the load side is first filled with the liquid-filled evaporator 1.
Tube 1 that constitutes a cold water pipe group (tube bundle)
distributed in a. For example, cold water flowing at 12 ° C. exchanges heat with the refrigerant liquid here and is cooled to 4 ° C. The cold water temperature is detected by the temperature detector 12 provided in the cold water pipe 13 on the cold water outlet side of the full liquid evaporator 1. In order to make the difference between the detected temperature and a predetermined temperature preset in the control device (30) as small as possible, it is generated from the full liquid type evaporator 1 and guided to the compressor 6 through the refrigerant gas pipe 21. The amount of refrigerant gas
The motor-operated valve 4 is operated by the control device to automatically adjust.
【００１９】圧縮機６で圧縮された高温高圧の冷媒ガス
は凝縮器５に至り冷却水と熱交換して凝縮する。凝縮器
５からの冷媒液は冷媒配管２０を経て満液式蒸発器１と
プレート式蒸発器２へ分流される。次に、満液式蒸発器
１からの冷水は、冷水配管１３によりプレート式蒸発器
２へ供給される。このとき、仕切り弁１９−１が開、仕
切り弁１９−２が閉となっている。The high-temperature and high-pressure refrigerant gas compressed by the compressor 6 reaches the condenser 5 and exchanges heat with the cooling water to be condensed. The refrigerant liquid from the condenser 5 is branched to the full liquid type evaporator 1 and the plate type evaporator 2 through the refrigerant pipe 20. Next, the cold water from the full liquid type evaporator 1 is supplied to the plate type evaporator 2 through the cold water pipe 13. At this time, the gate valve 19-1 is open and the gate valve 19-2 is closed.
【００２０】プレート式蒸発器２では、冷水はプレート
上部に設けられた受水槽１４に流入し、受水槽１４の底
に設けられた多数の小孔から散布され、各プレートの外
表面を流下し、プレート内の通路を流れる冷媒と熱交換
して仕様温度（例えば１℃）まで冷却される。流下した
冷水はプレート式蒸発器２の下部にある水槽１５に集め
られる。このとき、前記プレート式蒸発器２の冷媒通路
内では、冷媒液が蒸発し液とガスの混合状態で冷媒配管
２２を経てサージドラム３に入り液とガスに分離され
る。In the plate type evaporator 2, the cold water flows into the water receiving tank 14 provided at the upper portion of the plate, is sprayed from a large number of small holes provided at the bottom of the water receiving tank 14, and flows down on the outer surface of each plate. , And exchanges heat with the refrigerant flowing through the passages in the plate and is cooled to a specified temperature (for example, 1 ° C.). The cold water that has flowed down is collected in a water tank 15 at the bottom of the plate evaporator 2. At this time, in the refrigerant passage of the plate type evaporator 2, the refrigerant liquid evaporates and enters the surge drum 3 through the refrigerant pipe 22 in a mixed state of the liquid and gas to be separated into liquid and gas.
【００２１】前記水槽１５に集められた冷水は、冷水配
管１６を介して冷水ポンプ１７により蓄熱槽（Ａ）に送
水される。この最終冷水出口側である冷水配管１６に具
備された温度検出器１８により最終冷水の温度を検知す
る。この検知温度と制御装置に予め設定された所定の設
定温度との差を極力ゼロにするように、プレート式蒸発
器２から発生しサージドラム３、冷媒配管２３を経て圧
縮機６に導かれる冷媒ガス量を、前記制御装置により容
量制御装置８を作動させてサクションダンパー８ａの開
閉を自動調整する。The cold water collected in the water tank 15 is sent to the heat storage tank (A) by the cold water pump 17 through the cold water pipe 16. The temperature of the final cold water is detected by the temperature detector 18 provided in the cold water pipe 16 on the final cold water outlet side. Refrigerant generated from the plate type evaporator 2 and guided to the compressor 6 via the surge drum 3 and the refrigerant pipe 23 so that the difference between the detected temperature and a predetermined set temperature preset in the control device becomes zero as much as possible. The amount of gas is automatically adjusted by opening and closing the suction damper 8a by operating the capacity control device 8 by the control device.
【００２２】サージドラム３で分離された冷媒ガスは冷
媒配管２３を介して前述のように圧縮機６へ導かれる。
一方、サージドラム３で分離された冷媒液は、冷媒配管
２４により、凝縮器５から冷媒配管２０，冷媒供給弁１
１（１１−１，１１−２）を経て供給された冷媒液と合
流して再度プレート式蒸発器２に導かれる。上述の冷水
１℃取り出し運転は、深夜の安価な電力で行われる蓄熱
運転に有効である。The refrigerant gas separated by the surge drum 3 is guided to the compressor 6 through the refrigerant pipe 23 as described above.
On the other hand, the refrigerant liquid separated by the surge drum 3 is transferred from the condenser 5 to the refrigerant pipe 20 and the refrigerant supply valve 1 by the refrigerant pipe 24.
1 (11-1, 11-2) and the coolant liquid supplied to the plate-type evaporator 2. The cold water 1 ° C. extraction operation described above is effective for the heat storage operation performed at low cost at midnight.
【００２３】次に、図１を参照して本発明の特徴部につ
いて説明する。冷水量の変動や、スケール付着によるプ
レートの熱伝達率が低下する場合には、プレート式蒸発
器２のプレート外表面で結氷する恐れがある。結氷して
も、プレート間隔の確保により氷の膨脹等による異常荷
重の発生はなく、損傷の恐れはないが、性能低下を引き
起こす。Next, the features of the present invention will be described with reference to FIG. When the amount of cold water fluctuates or the heat transfer coefficient of the plate decreases due to scale adhesion, frost may form on the outer surface of the plate of the plate evaporator 2. Even if ice forms, due to the space between the plates, abnormal load due to expansion of ice does not occur, and there is no risk of damage, but performance is degraded.
【００２４】結氷によりプレート表面の熱伝達性能が低
下すると蒸発圧力が低下する。プレート式蒸発器２の内
圧相当部位であるサージドラム３に取り付けた圧力検知
器２６の信号を操作盤３０（制御装置）に取り込み、制
御装置に予め設定されている設定値以下になると、プレ
ート式蒸発器２の冷水出口温度を所定の設定温度に一定
制御する運転状態から、容量制御装置８を強制的に最低
可能制御開度までベーンダンパー８ａを絞って保持す
る。When the heat transfer performance on the plate surface is reduced due to freezing, the evaporation pressure is reduced. When the signal of the pressure detector 26 attached to the surge drum 3 which is a portion corresponding to the internal pressure of the plate type evaporator 2 is taken into the operation panel 30 (control device) and becomes less than or equal to a preset value set in the control device, the plate type From the operating state where the chilled water outlet temperature of the evaporator 2 is constantly controlled to a predetermined set temperature, the capacity control device 8 is forcibly held by squeezing the vane damper 8a to the lowest possible control opening.
【００２５】次に、冷媒ガスバイパス配管９の電磁弁１
０を開き、冷媒供給弁１１を閉じる。こうして凝縮器５
から加熱ガスを冷媒ガスバイパス配管９を経てプレート
式蒸発器２に送ることにより、プレート表面に付着して
いる氷を解氷する。解氷後、蒸発圧力が所定の設定圧力
まで回復すると、冷媒ガスバイパス配管９の電磁弁１０
を閉じ、冷媒供給弁１１を開く。さらに容量制御装置８
を元の自動温度調整運転に戻し、解氷運転を解除する。Next, the solenoid valve 1 of the refrigerant gas bypass pipe 9
0 is opened and the refrigerant supply valve 11 is closed. Thus condenser 5
The heated gas is sent to the plate type evaporator 2 through the refrigerant gas bypass pipe 9 to dissolve the ice adhering to the plate surface. When the evaporation pressure recovers to a predetermined set pressure after the thawing, the solenoid valve 10 of the refrigerant gas bypass pipe 9
And the refrigerant supply valve 11 is opened. Further capacity control device 8
Return to the original automatic temperature control operation and cancel the deicing operation.
【００２６】本実施の形態によれば、伝熱性能の高い満
液式蒸発器１と、凍結に対する信頼性の高いプレート式
蒸発器２を併用した冷凍装置において、プレート式蒸発
器２が結氷状態に陥った際の対応を自動化することによ
り、メンテナンス性の向上を図ったものであり、冷凍サ
イクル内の冷媒ガス温度を有効利用した低コストな手段
を提供するものである。According to the present embodiment, in the refrigerating apparatus in which the full liquid type evaporator 1 having high heat transfer performance and the plate type evaporator 2 having high reliability against freezing are used together, the plate type evaporator 2 is in an iced state. In order to improve the maintainability by automating the response to the case of the above, it is possible to provide a low-cost means that effectively uses the refrigerant gas temperature in the refrigeration cycle.
【００２７】[0027]
【発明の効果】以上詳細に説明したように、本発明によ
れば、中大容量の低温冷水を製造し、コスト的に安価
で、かつ凍結に対して信頼性の高い冷凍装置を提供する
ことことができる。As described above in detail, according to the present invention, it is possible to provide a refrigerating apparatus which produces low temperature cold water of medium and large capacity, is inexpensive in cost, and is highly reliable against freezing. be able to.
【図１】本発明の一実施の形態を示す冷凍装置の系統図
である。FIG. 1 is a system diagram of a refrigeration system showing an embodiment of the present invention.
１…満液式蒸発器、２…プレート式蒸発器、３…サージ
ドラム、４…電動弁、５…凝縮器、６…圧縮機、７…電
動機、８…容量制御装置、９…冷媒ガスバイパス配管、
１０…電磁弁、１１，１１−１，１１−２…冷媒供給
弁、１２，１８…温度検知器、１３，１６…冷水配管、
１４…受水槽、１５…水槽、１７…冷水ポンプ、１９−
１，１９−２…仕切り弁、２０…冷媒配管、２１，２３
…冷媒ガス配管、２６…圧力検出器、３０…操作盤。DESCRIPTION OF SYMBOLS 1 ... Liquid-fill type evaporator, 2 ... Plate type evaporator, 3 ... Surge drum, 4 ... Electric valve, 5 ... Condenser, 6 ... Compressor, 7 ... Electric motor, 8 ... Capacity control device, 9 ... Refrigerant gas bypass Piping,
10 ... Solenoid valve, 11, 11-1, 11-2 ... Refrigerant supply valve, 12, 18 ... Temperature detector, 13, 16 ... Cold water piping,
14 ... Water tank, 15 ... Water tank, 17 ... Cold water pump, 19-
1, 19-2 ... Gate valve, 20 ... Refrigerant piping 21, 23
... Refrigerant gas pipe, 26 ... Pressure detector, 30 ... Operation panel.
フロントページの続き (72)発明者 木庭 賢二 福岡県福岡市南区塩原二丁目１番47号 九州電力株式会社総合研究所内 (56)参考文献 特開 平２−52959（ＪＰ，Ａ) 特開 平９−210479（ＪＰ，Ａ) 特開 平８−327169（ＪＰ，Ａ) 特開 平４−28976（ＪＰ，Ａ) 特開 平１−247972（ＪＰ，Ａ) 実開 昭63−101765（ＪＰ，Ｕ) 特許2691154（ＪＰ，Ｂ２) (58)調査した分野(Int.Cl.7，ＤＢ名) F25B 5/00 Front page continuation (72) Kenji Kiniwa Kenji Kiniwa 2-47 Shiobara, Minami-ku, Fukuoka City, Fukuoka Prefecture Kyushu Electric Power Co., Inc. Research Institute (56) Reference JP-A-2-52959 (JP, A) JP-A 9-210479 (JP, A) JP 8-327169 (JP, A) JP 4-28976 (JP, A) JP 1-247972 (JP, A) Actual development Sho 63-101765 (JP, U) Patent 2691154 (JP, B2) (58) Fields investigated (Int.Cl. 7 , DB name) F25B 5/00
Claims (2)
接続する冷媒系統を備えて冷凍サイクルを構成し、蒸発
器に通水する冷水系統を有する冷凍装置において、 前記蒸発器として満液式蒸発器とプレート式蒸発器を併
用して、冷水を前記満液式蒸発器に通水し、さらに前記
プレート式蒸発器で０?付近まで冷却するように構成す
るとともに、前記冷凍サイクルは、深夜の蓄熱運転時に、冷媒ガスが
前記圧縮機で高温高圧に圧縮され、この冷媒ガスが前記
凝縮器で凝縮され、この凝縮した冷媒液が前記満液式蒸
発器と前記プレート式蒸発器へ分流してそれぞれの蒸発
器で蒸発され、前記満液式蒸発器で蒸発された冷媒ガス
と前記プレート式蒸発器で蒸発された冷媒ガスとが合流
して前記圧縮機に戻されるように前記冷媒配管を接続
し、 前 記プレート式蒸発器の冷媒系統入口に設けた冷媒供給
弁と、前記プレート式蒸発器の冷媒系統出口からの液，
ガス混合冷媒を気液分離させるサージドラムと、分離さ
れた冷媒ガスを圧縮機吸込口に導く配管とを備え、 前記凝縮器から前記プレート式蒸発器に至る冷媒ガスバ
イパス配管および該配管途中に弁を設け、 前記プレート式蒸発器の内圧相当部位に圧力検知器を設
け、 前記プレート式蒸発器のプレート表面が結氷したとき
に、前記圧力検知器の検知信号を用いて、蒸発圧力が或
る設定圧力を下回ると、前記バイパス配管途中の弁を開
にし、かつ前記プレート式蒸発器入口部の前記冷媒供給
弁を閉じて解氷運転を行い、 蒸発圧力が別の設定圧力まで回復すると、前記バイパス
配管途中の弁を閉じ、かつ前記冷媒供給弁を開にして解
氷運転を解除するように制御回路を構成したことを特徴
とする冷凍装置。1. A refrigeration system comprising a compressor, a condenser, an evaporator, and a refrigerant system connecting them to constitute a refrigeration cycle, and a chilled water system for passing water to the evaporator, wherein the evaporator is full of liquid. in combination with formula evaporator and a plate evaporator, and passed through cold water to the flooded evaporator is configured to cool further to 0? around with the plate evaporator with said refrigeration cycle, Refrigerant gas is discharged during heat storage operation at midnight.
Compressed to high temperature and high pressure by the compressor, the refrigerant gas is
Condensed in the condenser, the condensed refrigerant liquid is filled with the liquid
Divide into the generator and the plate-type evaporator and evaporate each
Gas evaporated in the vaporizer and evaporated in the liquid-filled evaporator
And the refrigerant gas evaporated in the plate evaporator merge.
And connect the refrigerant pipe to be returned to the compressor
And, a coolant supply valve provided in the refrigerant system inlet before Symbol plate evaporator, the liquid from the refrigerant system outlet of the plate evaporator,
A surge drum that separates the gas-mixed refrigerant into gas and liquid, and a pipe that guides the separated refrigerant gas to the compressor suction port, a refrigerant gas bypass pipe from the condenser to the plate evaporator, and a valve in the middle of the pipe. A pressure detector is provided at a portion corresponding to the internal pressure of the plate-type evaporator, and when the plate surface of the plate-type evaporator is frozen, the detection signal of the pressure detector is used to set the evaporation pressure to a certain value. When the pressure falls below the pressure, the valve in the middle of the bypass pipe is opened, and the refrigerant supply valve at the inlet of the plate-type evaporator is closed to perform the deicing operation. When the evaporation pressure recovers to another set pressure, the bypass A refrigerating apparatus comprising a control circuit configured to close a valve in the middle of the pipe and open the refrigerant supply valve to cancel the deicing operation.
られている容量制御装置のベーンダンパーを最低可能制
御開度まで絞つて保持するようにし、解氷運転が解除さ
れると、元の自動温度調整回路に切り替わるようにした
ことを特徴とする請求項１記載の冷凍装置。2. When the thawing operation is started, the vane damper of the capacity control device provided in the suction part of the compressor is squeezed and held to the minimum possible control opening, and the thawing operation is canceled. The refrigeration apparatus according to claim 1, wherein the refrigeration apparatus is switched to the original automatic temperature control circuit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12710998A JP3467407B2 (en) | 1998-05-11 | 1998-05-11 | Refrigeration equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12710998A JP3467407B2 (en) | 1998-05-11 | 1998-05-11 | Refrigeration equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH11325627A JPH11325627A (en) | 1999-11-26 |
| JP3467407B2 true JP3467407B2 (en) | 2003-11-17 |
Family
ID=14951836
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12710998A Expired - Fee Related JP3467407B2 (en) | 1998-05-11 | 1998-05-11 | Refrigeration equipment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3467407B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109612142A (en) * | 2018-12-20 | 2019-04-12 | 江阴爱尔姆真空设备有限公司 | A kind of flooded screw unit |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102129297B1 (en) * | 2013-07-29 | 2020-07-03 | 삼성전자주식회사 | Air conditional and method for controlling the same |
| CN111988962A (en) * | 2020-08-20 | 2020-11-24 | 武汉众维亿方大数据科技有限公司 | Heat exchange device and heat exchange method for exchanging heat for cabinet air conditioner |
-
1998
- 1998-05-11 JP JP12710998A patent/JP3467407B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109612142A (en) * | 2018-12-20 | 2019-04-12 | 江阴爱尔姆真空设备有限公司 | A kind of flooded screw unit |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH11325627A (en) | 1999-11-26 |
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