JP5351097B2 - Refrigerant circulation device - Google Patents
Refrigerant circulation device Download PDFInfo
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- JP5351097B2 JP5351097B2 JP2010139401A JP2010139401A JP5351097B2 JP 5351097 B2 JP5351097 B2 JP 5351097B2 JP 2010139401 A JP2010139401 A JP 2010139401A JP 2010139401 A JP2010139401 A JP 2010139401A JP 5351097 B2 JP5351097 B2 JP 5351097B2
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- temperature
- condenser
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- evaporator
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- 239000003507 refrigerant Substances 0.000 title claims description 143
- 238000001816 cooling Methods 0.000 claims description 50
- 239000007788 liquid Substances 0.000 claims description 33
- 230000005494 condensation Effects 0.000 claims description 26
- 238000009833 condensation Methods 0.000 claims description 26
- 238000001514 detection method Methods 0.000 claims description 14
- 238000007664 blowing Methods 0.000 claims description 2
- 239000003570 air Substances 0.000 description 23
- 238000001704 evaporation Methods 0.000 description 20
- 230000008020 evaporation Effects 0.000 description 19
- 238000010586 diagram Methods 0.000 description 14
- 230000007423 decrease Effects 0.000 description 6
- 239000002826 coolant Substances 0.000 description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 3
- KYKAJFCTULSVSH-UHFFFAOYSA-N chloro(fluoro)methane Chemical compound F[C]Cl KYKAJFCTULSVSH-UHFFFAOYSA-N 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 239000012080 ambient air Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
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- H—ELECTRICITY
- H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
- H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
- H05K7/00—Constructional details common to different types of electric apparatus
- H05K7/20—Modifications to facilitate cooling, ventilating, or heating
- H05K7/20709—Modifications to facilitate cooling, ventilating, or heating for server racks or cabinets; for data centers, e.g. 19-inch computer racks
- H05K7/208—Liquid cooling with phase change
- H05K7/20818—Liquid cooling with phase change within cabinets for removing heat from server blades
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0266—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
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- H—ELECTRICITY
- H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
- H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
- H05K7/00—Constructional details common to different types of electric apparatus
- H05K7/20—Modifications to facilitate cooling, ventilating, or heating
- H05K7/20709—Modifications to facilitate cooling, ventilating, or heating for server racks or cabinets; for data centers, e.g. 19-inch computer racks
- H05K7/20836—Thermal management, e.g. server temperature control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
- F28F2250/08—Fluid driving means, e.g. pumps, fans
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Computer Hardware Design (AREA)
- Microelectronics & Electronic Packaging (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Air Conditioning Control Device (AREA)
Description
本発明は冷媒循環装置に関し、特に空気調和システムにおける冷却ユニット送風機の故障時の冷却能力を制御するための冷媒循環装置に関する。 The present invention relates to a refrigerant circulation device, and more particularly to a refrigerant circulation device for controlling the cooling capacity at the time of failure of a cooling unit blower in an air conditioning system.
サーバルームには、コンピュータやサーバ等の電子機器が集約された状態で多数設置される。電子機器は一般にラックマウント方式、すなわち、電子機器を機能単位別に分割して収納するラック(筐体)をキャビネットに段積みする方式で設置され、キャビネットはサーバルームの床上に多数整列配置される。 A large number of electronic devices such as computers and servers are gathered in the server room. Electronic devices are generally installed in a rack mount system, that is, a system in which racks (casings) for storing electronic devices divided into functional units are stacked in a cabinet, and a large number of cabinets are arranged on the floor of a server room.
これらの電子機器は、正常な動作をするために一定の温度環境が必要とされ、高温状態になるとシステム停止等のトラブルを引き起こすおそれがある。このため、サーバルームは、年間冷房型パッケージ空調機等によって一定の温度環境に管理されている。しかし、空調機が故障すると、機器類の発熱により室内が高温状態になったり、局所的に高温の箇所が発生したりする状態となる。一般に、電子機器類の許容温度は常温程度であり、周囲空気が高温になった場合、機器自身が保護制御により自動停止し運転の継続が不能となったり、さらには機器の構成部品が破壊されて故障したりするおそれもある。 These electronic devices require a certain temperature environment in order to operate normally, and may cause troubles such as system stoppage when the temperature becomes high. For this reason, the server room is managed in a constant temperature environment by an annual cooling type package air conditioner or the like. However, if the air conditioner breaks down, the room becomes hot due to the heat generated by the equipment, or a hot spot is locally generated. In general, the permissible temperature of electronic devices is about room temperature, and when the ambient air becomes hot, the device itself automatically stops due to protection control and operation cannot be continued, and further, the components of the device are destroyed. May break down.
特許文献1には、空調機の故障時の対策がなされた冷媒循環装置が開示されている。特許文献1の冷媒循環装置は室内機、室外機、圧縮機、膨張弁、これらを接続する冷媒配管から構成されており、たとえば圧縮機が故障した場合に、室内機送風機が運転可能な判断をした後、室内に設置した温度センサの測定値に基づいて演算された最高温度が、電子機器類の許容温度に基づいて設定された上限温度を超えている場合、送風機の運転を継続する。 Patent Document 1 discloses a refrigerant circulation device in which measures are taken when an air conditioner fails. The refrigerant circulation device of Patent Document 1 is composed of an indoor unit, an outdoor unit, a compressor, an expansion valve, and a refrigerant pipe connecting them. For example, when the compressor breaks down, it is determined that the indoor unit blower can be operated. After that, when the maximum temperature calculated based on the measured value of the temperature sensor installed indoors exceeds the upper limit temperature set based on the allowable temperature of the electronic equipment, the operation of the blower is continued.
しかしながら、特許文献1の冷媒循環装置は、圧縮機が故障した際に冷却運転ができないので、冷却性能が低下し、室内の温度上昇につながり、電子機器類が故障するというおそれがあった。また、送風機の故障時にはいかなる手段もこうじることはできなかった。 However, since the refrigerant circulation device of Patent Document 1 cannot perform a cooling operation when the compressor fails, there is a concern that the cooling performance is lowered, the temperature inside the room is increased, and the electronic devices are broken. Also, no means could be used when the blower failed.
本発明はこのような事情に鑑みてなされたもので、冷媒を自然循環させる空調システムの冷媒循環装置において、蒸発器に送風する複数の送風機のうち少なくとも1台が故障し、風量が減少し冷却能力が低下する場合でも、冷却能力を増加させ能力を補償することができる冷媒循環装置を提供することを目的とする。 The present invention has been made in view of such circumstances, and in a refrigerant circulation device of an air conditioning system that naturally circulates refrigerant, at least one of a plurality of blowers that blows air to an evaporator fails, and the amount of air is reduced and cooled. An object of the present invention is to provide a refrigerant circulation device capable of increasing the cooling capacity and compensating for the capacity even when the capacity decreases.
本発明は、前記目的を達成するために、蒸発器と、蒸発器に送風する複数の送風機と、凝縮器と、前記蒸発器と前記凝縮器を接続する冷媒液管及び冷媒ガス管とを備えた冷媒循環装置において、前記送風機の故障を検知する送風機故障検知手段と、凝縮器側冷媒温度制御機器と、前記凝縮器に供給する熱媒体の流量を制御する熱媒体流量制御弁と、前記凝縮器から前記蒸発器に供給される冷媒液の温度を検知する凝縮器冷媒液温度センサとを備え、前記凝縮器側冷媒温度制御機器は、前記送風機故障検知手段から故障信号が入力された場合に、凝縮器側外部入力温度の設定温度を低下させ、前記凝縮器冷媒液温度センサによって測定された測定値が設定温度になるように前記熱媒体流量制御弁を制御することを特徴とする冷媒循環装置を提供する。 In order to achieve the above object, the present invention includes an evaporator, a plurality of blowers that blow air to the evaporator, a condenser, and a refrigerant liquid pipe and a refrigerant gas pipe that connect the evaporator and the condenser. In the refrigerant circulating apparatus, a fan failure detecting means for detecting a failure of the fan, a condenser-side refrigerant temperature control device, a heat medium flow control valve for controlling a flow rate of a heat medium supplied to the condenser, and the condensation A condenser refrigerant liquid temperature sensor for detecting the temperature of the refrigerant liquid supplied from the condenser to the evaporator, and the condenser-side refrigerant temperature control device receives a failure signal from the blower failure detection means. The refrigerant circulation is characterized in that the set temperature of the condenser side external input temperature is lowered and the heat medium flow control valve is controlled so that the measured value measured by the condenser refrigerant liquid temperature sensor becomes the set temperature. Provide equipment That.
本発明は、上述の課題を解決するため、凝縮温度を低下させることで、冷却能力を増大させるものである。 In order to solve the above-described problems, the present invention increases the cooling capacity by lowering the condensation temperature.
本発明に係る冷媒循環装置は、すなわち、冷媒を自然に循環させる冷媒循環装置は、蒸発器よりも高所に設置された凝縮器を、ガス配管及び液配管で接続することによって構成されている。そして、蒸発器で気化された冷媒の気体がガス配管を介して凝縮器に送られ、凝縮器で液化された冷媒の液体が液配管を介して蒸発器に送られることによって、冷媒が自然循環され、蒸発器で冷却作用を得ることができる。このような冷媒自然循環型の空調システムを、サーバの局所冷却に適用することによって、空調機のランニングコストを削減することができる。 The refrigerant circulation apparatus according to the present invention, that is, the refrigerant circulation apparatus that circulates the refrigerant naturally, is configured by connecting a condenser installed at a higher position than the evaporator with a gas pipe and a liquid pipe. . Then, the refrigerant gas evaporated by the evaporator is sent to the condenser via the gas pipe, and the refrigerant liquid liquefied by the condenser is sent to the evaporator via the liquid pipe, so that the refrigerant circulates naturally. In addition, a cooling action can be obtained with an evaporator. The running cost of the air conditioner can be reduced by applying such a refrigerant natural circulation type air conditioning system to the local cooling of the server.
本発明においては、凝縮器側制御温度演算手段を備え、前記凝縮器側冷媒温度制御機器に、前記送風機故障検知手段から故障信号が入力された場合に、前記凝縮器側制御温度演算手段は送風機の故障台数と予め設定された冷却性能テーブルから必要な凝縮器側制御温度を演算し、前記凝縮器側冷媒温度制御機器は、凝縮器側外部入力温度の設定温度を前記演算した値に低下させ、前記凝縮器冷媒液温度センサ測定値が設定温度になるように前記熱媒体流量制御弁を制御することが好ましい。 In the present invention, when the failure signal is input from the blower failure detecting means to the condenser side refrigerant temperature control device, the condenser side control temperature calculating means is provided with a blower. The required condenser side control temperature is calculated from the number of failures and the preset cooling performance table, and the condenser side refrigerant temperature control device reduces the set temperature of the condenser side external input temperature to the calculated value. It is preferable to control the heat medium flow control valve so that the measured value of the condenser refrigerant liquid temperature sensor becomes a set temperature.
本発明は、送風機の故障台数と冷却性能テーブルから必要な凝縮温度を演算し、その凝縮温度に低下させることで、冷却能力を増大させるものである。 The present invention calculates the necessary condensing temperature from the number of blower failures and the cooling performance table, and decreases the condensing temperature to increase the cooling capacity.
本発明においては、蒸発器内圧力センサを備え、前記凝縮器側冷媒温度制御機器に、前記送風機故障検知手段から故障信号が入力された場合に、前記凝縮器側制御温度演算手段は送風機の故障台数と前記蒸発器内圧力センサの測定値と予め設定された冷却性能テーブルとから必要な凝縮器側制御温度を演算し、前記凝縮器側冷媒温度制御機器は、凝縮器側外部入力温度の設定温度を前記演算した値に低下させ、凝縮器冷媒液温度センサ測定値が設定温度になるように熱媒体流量制御弁を制御することが好ましい。 In the present invention, an evaporator internal pressure sensor is provided, and when the failure signal is input from the blower failure detection means to the condenser side refrigerant temperature control device, the condenser side control temperature calculation means is a failure of the blower. The required condenser-side control temperature is calculated from the number of units, the measured value of the pressure sensor in the evaporator, and a preset cooling performance table, and the condenser-side refrigerant temperature control device sets the condenser-side external input temperature. It is preferable to control the heat medium flow control valve so that the temperature is lowered to the calculated value and the measured value of the condenser refrigerant liquid temperature sensor becomes the set temperature.
本発明は、送風機の故障台数と蒸発器内圧力センサ測定値と冷却性能テーブルから必要な凝縮温度を演算し、その凝縮温度に低下させることで、冷却能力を増大させるものである。実際に蒸発器内圧力センサで蒸発温度を測定することにより、より正確に必要な冷却能力をだすための凝縮温度に設定することができる。これにより、熱量のロスを防止する。 The present invention calculates the necessary condensing temperature from the number of blower failures, the measured value in the evaporator pressure sensor and the cooling performance table, and lowers the condensing temperature to increase the cooling capacity. By actually measuring the evaporating temperature with the pressure sensor in the evaporator, it is possible to set the condensing temperature to obtain the required cooling capacity more accurately. This prevents heat loss.
本発明においては、室内露点温度センサを備え、前記凝縮器側冷媒温度制御機器に、前記送風機故障検知手段から故障信号が入力された場合に、前記凝縮器側制御温度演算手段は送風機の故障台数と予め設定された冷却性能テーブルとから必要な凝縮器側制御温度を演算し、前記凝縮器側冷媒温度制御機器は、前記演算した値が室内露点温度以上の場合は凝縮器側外部入力温度の設定温度を演算値にし、前記演算した値が室内露点温度以下の場合は設定温度を室内露点温度に低下させ、凝縮器冷媒液温度センサ測定値が設定温度になるように熱媒体流量制御弁を制御することが好ましい。 In the present invention, an indoor dew point temperature sensor is provided, and when the failure signal is input from the blower failure detection means to the condenser side refrigerant temperature control device, the condenser side control temperature calculation means is the number of blower failures. Required condenser side control temperature is calculated from the preset cooling performance table, and the condenser side refrigerant temperature control device calculates the condenser side external input temperature when the calculated value is equal to or higher than the indoor dew point temperature. If the set temperature is the calculated value and the calculated value is less than or equal to the indoor dew point temperature, the set temperature is lowered to the indoor dew point temperature, and the heat medium flow control valve is adjusted so that the measured value of the condenser refrigerant liquid temperature sensor becomes the set temperature. It is preferable to control.
本発明は、結露防止策を加えたものである。 In the present invention, a measure for preventing condensation is added.
本発明の冷媒循環装置によれば、蒸発器に送風する送風機のうち少なくとも1台が故障した場合、凝縮温度を低下させることで、冷却能力を増大させたので、冷却ユニット能力を補償することができる。また、それに加えて、蒸発器の結露を防止することができる。 According to the refrigerant circulation device of the present invention, when at least one of the blowers blown to the evaporator fails, the cooling capacity is increased by reducing the condensation temperature, so that the cooling unit capacity can be compensated. it can. In addition, condensation of the evaporator can be prevented.
以下、添付図面に従って本発明に係る冷媒循環装置の好ましい実施の形態について説明する。 Hereinafter, preferred embodiments of a refrigerant circulation device according to the present invention will be described with reference to the accompanying drawings.
図1は、第1の実施の形態の冷媒循環装置の構成を示したブロック図である。 FIG. 1 is a block diagram showing the configuration of the refrigerant circulation device according to the first embodiment.
図1において、凝縮器3は、2台の蒸発器1、1で気化した冷媒を冷却して凝縮させる装置である。なお、蒸発器1の台数は2台に限定されるものではない。
In FIG. 1, the
凝縮器3は、蒸発器1よりも高所、たとえば建屋の屋上に設けられる。凝縮器3は、内部に冷媒を冷却する熱媒体(例えば冷水)が通るコイルが設けられ、気化した冷媒が熱交換をし、冷媒が液化される。凝縮器3において前記冷媒を冷却する熱媒体は、熱媒体作成装置21(例えば冷凍機)から熱媒体搬送装置22を用いて供給される。
The
蒸発器1、1と凝縮器3は、冷媒液管4と冷媒ガス管5とを介して接続される。冷媒ガス管5の上端は凝縮器3内のコイルの一端に接続されており、冷媒ガス管5の下端は蒸発器1のコイル一端に接続されている。一方、冷媒液管4の上端は、凝縮器3内のコイルの他端に接続されており、冷媒液管4の下端は蒸発器1のコイルの他端に接続されている。したがって、各蒸発器1、1によって気化された冷媒の気体は、冷媒ガス管5を通って凝縮器3に自然に送られ、この凝縮器3で液化された後、液化された冷媒は冷媒液管4を通って蒸発器1に自然に流下される。これにより、冷媒の自然循環が行われる。
The evaporators 1, 1 and the
循環する冷媒としては、フロン、あるいは代替フロンとしてのHFC(ハイドロフロロカーボン)等を使用することができる。また、大気圧よりも低い圧力で使用するならば、水を使用することも可能である。 As the circulating refrigerant, chlorofluorocarbon or HFC (hydrofluorocarbon) as an alternative chlorofluorocarbon can be used. In addition, water can be used if it is used at a pressure lower than atmospheric pressure.
蒸発器1と蒸発器1に通風する送風機2とから構成される冷却ユニットは、サーバラック24の背面に備え付けられ、サーバラック24内に収められた電子機器の排熱は、送風機2によって蒸発器1に送風することで行われる。これにより、電子機器により暖められた空気が冷却され、サーバルームの室内に放出される。送風機2には、送風機2の故障を検知する送風機故障検知手段6が設けられる。
The cooling unit including the evaporator 1 and the
この冷媒循環装置は、凝縮器3に供給される冷媒温度を制御するための凝縮器側冷媒温度制御機器7が設けられている。この凝縮器側冷媒温度制御機器7は、凝縮器3の出口の冷媒液管4に設けられた凝縮器冷媒液温度センサ8の測定値が凝縮器側外部入力温度の設定温度になるように、熱媒体配管25に設けられた熱媒体流量制御弁23の開度を制御する。
This refrigerant circulation device is provided with a condenser-side refrigerant temperature control device 7 for controlling the refrigerant temperature supplied to the
また、凝縮器側冷媒温度制御機器7は、送風機故障検知手段6から故障信号が入力された場合に、凝縮器側外部入力温度の設定温度を低下させ、凝縮器冷媒液温度センサ8の測定値が設定温度になるように熱媒体流量制御弁23の開度を制御する。
Further, when a failure signal is input from the blower failure detection means 6, the condenser-side refrigerant temperature control device 7 decreases the set temperature of the condenser-side external input temperature, and the measured value of the condenser refrigerant
これにより、第1の実施の形態の冷媒循環装置によれば、凝縮温度を低下させて冷却能力を増大させることができるので、冷却ユニットの能力を補償することができる。 Thereby, according to the refrigerant circulation device of the first embodiment, the cooling temperature can be increased by reducing the condensation temperature, so that the capacity of the cooling unit can be compensated.
図2は、第2の実施の形態の冷媒循環装置の構成を示したブロック図であり、図1に示した冷媒循環装置と同一又は類似の部材については同一の符号を付して説明する。 FIG. 2 is a block diagram showing the configuration of the refrigerant circulation device according to the second embodiment, and the same or similar members as those in the refrigerant circulation device shown in FIG.
図2の冷媒循環装置は、図1に示した冷媒循環装置に対し、凝縮器3の制御温度を演算する凝縮器側制御温度演算手段9が設けられている。
The refrigerant circulation device of FIG. 2 is provided with condenser side control temperature calculation means 9 for calculating the control temperature of the
凝縮器側冷媒温度制御機器7に送風機故障検知手段6から故障信号が入力された場合に、風量が低下した分の熱量をだすために、蒸発温度を下げる必要がある。この冷媒循環装置の冷媒自然循環システムは、凝縮温度とともに蒸発温度が変動するので、この場合では凝縮温度を低下させる。 When a failure signal is input from the blower failure detection means 6 to the condenser-side refrigerant temperature control device 7, it is necessary to lower the evaporation temperature in order to generate the amount of heat corresponding to the decrease in the air volume. In the refrigerant natural circulation system of the refrigerant circulation device, the evaporation temperature varies with the condensation temperature, and in this case, the condensation temperature is lowered.
風量低下分に対応した蒸発温度を下げるため、凝縮器側制御温度演算手段9は、送風機2の故障台数と予め設定した冷却性能テーブルとから必要な凝縮器側制御温度を演算(演算値)する。そして、凝縮器側冷媒温度制御機器7は、凝縮器側外部入力温度の設定温度を演算値に低下させ、凝縮器冷媒液温度センサ8の測定値が設定温度になるように熱媒体流量制御弁23の開度を制御する。
In order to lower the evaporation temperature corresponding to the air volume drop, the condenser side control temperature calculation means 9 calculates (calculates) the necessary condenser side control temperature from the number of failed
これにより、第2の実施の形態の冷媒循環装置によれば、凝縮温度を低下させて冷却能力を増大させることができるので、冷却ユニット能力を補償することができる。 Thereby, according to the refrigerant circulation device of the second embodiment, the cooling temperature can be increased by lowering the condensation temperature, so that the cooling unit capability can be compensated.
凝縮器側制御温度の演算は、風量と冷却能力の関係式と、冷却能力と蒸発温度の関係式と、設計条件と、蒸発温度と凝縮温度の関係式と、凝縮温度と凝縮器冷媒液温度の関係式を予め冷却性能テーブルに設定しておくことにより行う。 The calculation of the condenser side control temperature consists of a relational expression between air volume and cooling capacity, a relational expression between cooling capacity and evaporation temperature, design conditions, a relational expression between evaporation temperature and condensation temperature, condensation temperature and condenser refrigerant liquid temperature. Is set in the cooling performance table in advance.
図3は、第3の実施の形態の冷媒循環装置の構成を示したブロック図であり、図1に示した冷媒循環装置と同一又は類似の部材については同一の符号を付して説明する。 FIG. 3 is a block diagram showing the configuration of the refrigerant circulation device according to the third embodiment, and the same or similar members as those in the refrigerant circulation device shown in FIG.
図3の冷媒循環装置は、図2に示した冷媒循環装置において、蒸発器1内の圧力を検知する蒸発器内圧力センサ11が設けられている。 The refrigerant circulation device of FIG. 3 is provided with an evaporator internal pressure sensor 11 for detecting the pressure in the evaporator 1 in the refrigerant circulation device shown in FIG.
凝縮器側冷媒温度制御機器7に送風機故障検知手段6から故障信号が入力された場合に、風量が低下した分の熱量をだすために、蒸発温度を下げる必要がある。冷媒循環装置の冷媒自然循環システムは、凝縮温度とともに蒸発温度が変動するので、この場合では凝縮温度を低下させる。 When a failure signal is input from the blower failure detection means 6 to the condenser-side refrigerant temperature control device 7, it is necessary to lower the evaporation temperature in order to generate the amount of heat corresponding to the decrease in the air volume. In the refrigerant natural circulation system of the refrigerant circulation device, the evaporation temperature varies with the condensation temperature. In this case, the condensation temperature is lowered.
減少した風量に対応した蒸発温度にするために、凝縮器側制御温度演算手段9は、予め設定した蒸発器内圧力センサ11の測定値より蒸発温度を算出し、その蒸発温度からいくら蒸発温度を下げればよいか演算し、蒸発温度と凝縮温度の関係式より凝縮温度をいくら下げればよいかを演算(演算値)する。凝縮器側冷媒温度制御機器7は、その凝縮温度にするために凝縮温度と凝縮器冷媒液温度の関係式より凝縮器側外部入力温度を演算し、凝縮器側外部入力温度の設定温度を演算値に低下させ、凝縮器冷媒液温度センサ8の測定値が設定温度になるように熱媒体流量制御弁23の開度を制御する。
In order to obtain the evaporation temperature corresponding to the reduced air volume, the condenser side control temperature calculation means 9 calculates the evaporation temperature from the preset measurement value of the evaporator pressure sensor 11, and the evaporation temperature is calculated from the evaporation temperature. It is calculated whether the lowering of the condensing temperature is calculated (calculated value) from the relational expression between the evaporation temperature and the condensing temperature. The condenser side refrigerant temperature control device 7 calculates the condenser side external input temperature from the relational expression between the condensation temperature and the condenser refrigerant liquid temperature, and calculates the set temperature of the condenser side external input temperature in order to obtain the condensation temperature. The opening degree of the heat medium
これにより、第3の実施の形態の冷媒循環装置によれば、より正確に必要な冷却能力をだすための凝縮温度に設定しながら、冷却能力を増大させることができるので、冷却ユニット能力を補償することができる。 As a result, according to the refrigerant circulation device of the third embodiment, the cooling capacity can be increased while setting the condensation temperature to obtain the required cooling capacity more accurately, so that the cooling unit capacity is compensated. can do.
凝縮器側制御温度の演算は風量と冷却能力の関係式と、冷却能力と蒸発温度の関係式と、設計条件と、蒸発温度と凝縮温度の関係式と、凝縮温度と凝縮器冷媒液温度の関係式を予め冷却性能テーブルに設定して凝縮器側制御温度演算手段9で行う。 The calculation of the condenser side control temperature is based on the relationship between the air volume and the cooling capacity, the relation between the cooling capacity and the evaporation temperature, the design condition, the relation between the evaporation temperature and the condensation temperature, the condensation temperature and the condenser refrigerant liquid temperature. The relational expression is set in the cooling performance table in advance and is performed by the condenser side control temperature calculation means 9.
図4は、第4の実施の形態の冷媒循環装置の構成を示したブロック図であり、図1に示した冷媒循環装置と同一又は類似の部材については同一の符号を付して説明する。 FIG. 4 is a block diagram showing the configuration of the refrigerant circulation device according to the fourth embodiment, and the same or similar members as those in the refrigerant circulation device shown in FIG.
図4の冷媒循環装置は、図2に示した冷媒循環装置において、室内の露点温度を検知する室内露点温度センサ10が設けられている。
The refrigerant circulation device of FIG. 4 is provided with an indoor dew
凝縮器側冷媒温度制御機器7に送風機故障検知手段6から故障信号が入力された場合に、風量が低下した分の熱量をだすために、蒸発温度を下げる必要がある。この冷媒循環装置の冷媒自然循環システムは、凝縮温度とともに蒸発温度が変動するので、この場合では凝縮温度を低下させる。 When a failure signal is input from the blower failure detection means 6 to the condenser-side refrigerant temperature control device 7, it is necessary to lower the evaporation temperature in order to generate the amount of heat corresponding to the decrease in the air volume. In the refrigerant natural circulation system of the refrigerant circulation device, the evaporation temperature varies with the condensation temperature, and in this case, the condensation temperature is lowered.
風量低下分に対応した蒸発温度を下げるため、凝縮器側制御温度演算手段9は、予め設定した冷却性能テーブルから必要な凝縮器側制御温度を演算(演算値)する。そして、凝縮器側冷媒温度制御機器7は、その演算値が室内露点温度センサ10の測定値以上の場合は凝縮器側外部入力温度の設定温度を演算値にし、演算値が室内露点温度センサ10の測定値以下の場合は設定温度を室内露点温度センサ10の測定値に低下させ、凝縮器冷媒液温度センサ8の測定値が設定温度になるように熱媒体流量制御弁23の開度を制御する。
In order to lower the evaporation temperature corresponding to the air volume drop, the condenser side control temperature calculation means 9 calculates (calculates) the necessary condenser side control temperature from a preset cooling performance table. When the calculated value is equal to or greater than the measured value of the indoor dew
これにより、第4の実施の形態の冷媒循環装置によれば、凝縮温度を低下させて冷却能力を増大させることにより冷却ユニット能力を増大し、かつ蒸発器1での結露を防止することができる。 Thereby, according to the refrigerant circulation device of the fourth embodiment, the cooling unit capacity can be increased by lowering the condensation temperature to increase the cooling capacity, and condensation in the evaporator 1 can be prevented. .
凝縮器側制御温度の演算は風量と冷却能力の関係式と、冷却能力と蒸発温度の関係式と、設計条件と、蒸発温度と凝縮温度の関係式と、凝縮温度と凝縮器冷媒液温度の関係式を予め冷却性能テーブルに設定しておくことにより行う。 The calculation of the condenser side control temperature is based on the relationship between the air volume and the cooling capacity, the relation between the cooling capacity and the evaporation temperature, the design condition, the relation between the evaporation temperature and the condensation temperature, the condensation temperature and the condenser refrigerant liquid temperature. This is done by setting the relational expression in the cooling performance table in advance.
図5は、第5の実施の形態の冷媒循環装置の構成を示したブロック図であり、図1に示した冷媒循環装置と同一又は類似の部材については同一の符号を付して説明する。図5の冷媒循環装置は、図1に示した冷媒循環装置において、熱媒体流量制御弁23の開度を制御する代わりに、熱媒体搬送装置22の周波数を熱媒体搬送装置制御機器26によって制御する装置である。なお、図2〜図4に示した冷媒循環装置においても同様である。
FIG. 5 is a block diagram showing the configuration of the refrigerant circulation device according to the fifth embodiment, and the same or similar members as those in the refrigerant circulation device shown in FIG. The refrigerant circulation device of FIG. 5 controls the frequency of the heat
図6は、第6の実施の形態の冷媒循環装置の構成を示したブロック図であり、図1に示した冷媒循環装置と同一又は類似の部材については同一の符号を付して説明する。図6の冷媒循環装置は、図1に示した冷媒循環装置において、凝縮器3が散水式空冷凝縮器27の場合、熱媒体流量制御弁23の開度を制御する代わりに、散水式空冷凝縮器27の周波数を散水式空冷凝縮器送風機制御機器29で制御する装置である。なお、図2〜図4に示した冷媒循環装置においても同様である。
FIG. 6 is a block diagram showing the configuration of the refrigerant circulation device according to the sixth embodiment, and the same or similar members as those in the refrigerant circulation device shown in FIG. The refrigerant circulation device of FIG. 6 is the same as the refrigerant circulation device shown in FIG. 1, when the
図7は、第7の実施の形態の冷媒循環装置の構成を示したブロック図であり、図1に示した冷媒循環装置と同一又は類似の部材については同一の符号を付して説明する。図7の冷媒循環装置は、図6に示した冷媒循環装置において、散水式空冷凝縮器送風機制御機器29の周波数を制御する代わりに、散水用循環ポンプ30の周波数を散水用循環ポンプ制御機器31で制御する装置である。
FIG. 7 is a block diagram showing the configuration of the refrigerant circulation device according to the seventh embodiment, and the same or similar members as those in the refrigerant circulation device shown in FIG. The refrigerant circulation device of FIG. 7 is the refrigerant circulation device shown in FIG. 6, instead of controlling the frequency of the watering type air-cooled condenser
1…蒸発器、2…送風機、3…凝縮器、4…冷媒液管、5…冷媒ガス管、6…送風機故障検知手段、7…凝縮器側冷媒温度制御機器、8…凝縮器液管温度センサ、9…凝縮器側制御温度演算手段、10…室内露点温度センサ、11…蒸発器内圧力センサ、21…熱媒体作成装置、22…熱媒体搬送装置、23…熱媒体流量制御弁、24…サーバラック、25…熱媒体配管、26…熱媒体搬送装置制御機器、27…散水式空冷凝縮器、28…散水式空冷凝縮器送風機、29…散水式空冷凝縮器送風機制御機器、30…散水用循環ポンプ、31…散水用循環ポンプ制御機器
DESCRIPTION OF SYMBOLS 1 ... Evaporator, 2 ... Blower, 3 ... Condenser, 4 ... Refrigerant liquid pipe, 5 ... Refrigerant gas pipe, 6 ... Blower failure detection means, 7 ... Condenser side refrigerant temperature control apparatus, 8 ... Condenser liquid pipe temperature Sensor 9, condenser side control temperature calculating means 10, indoor dew point temperature sensor 11, evaporator
Claims (4)
前記送風機の故障を検知する送風機故障検知手段と、凝縮器側冷媒温度制御機器と、前記凝縮器に供給する熱媒体の流量を制御する熱媒体流量制御弁と、前記凝縮器から前記蒸発器に供給される冷媒液の温度を検知する凝縮器冷媒液温度センサとを備え、
前記凝縮器側冷媒温度制御機器は、前記送風機故障検知手段から故障信号が入力された場合に、凝縮器側外部入力温度の設定温度を低下させ、前記凝縮器冷媒液温度センサによって測定された測定値が設定温度になるように前記熱媒体流量制御弁を制御することを特徴とする冷媒循環装置。 In a refrigerant circulation device comprising an evaporator, a plurality of fans for blowing air to the evaporator, a condenser, a refrigerant liquid pipe and a refrigerant gas pipe connecting the evaporator and the condenser,
A blower failure detection means for detecting a failure of the blower, a condenser-side refrigerant temperature control device, a heat medium flow control valve for controlling the flow rate of the heat medium supplied to the condenser, and the condenser to the evaporator A condenser refrigerant liquid temperature sensor for detecting the temperature of the supplied refrigerant liquid,
The condenser-side refrigerant temperature control device reduces the set temperature of the condenser-side external input temperature when a failure signal is input from the blower failure detection means, and is measured by the condenser refrigerant liquid temperature sensor The refrigerant circulating apparatus, wherein the heat medium flow control valve is controlled so that a value becomes a set temperature.
前記凝縮器側冷媒温度制御機器に、前記送風機故障検知手段から故障信号が入力された場合に、前記凝縮器側制御温度演算手段は送風機の故障台数と予め設定された冷却性能テーブルから必要な凝縮器側制御温度を演算し、前記凝縮器側冷媒温度制御機器は、凝縮器側外部入力温度の設定温度を前記演算した値に低下させ、前記凝縮器冷媒液温度センサ測定値が設定温度になるように前記熱媒体流量制御弁を制御する請求項1に記載の冷媒循環装置。 Condenser side control temperature calculation means
When a failure signal is input from the blower failure detection means to the condenser-side refrigerant temperature control device, the condenser-side control temperature calculation means performs the necessary condensation based on the number of blower failures and a preset cooling performance table. The condenser-side control temperature is calculated, and the condenser-side refrigerant temperature control device lowers the set temperature of the condenser-side external input temperature to the calculated value, and the measured value of the condenser refrigerant liquid temperature sensor becomes the set temperature. The refrigerant circulation device according to claim 1, wherein the heat medium flow control valve is controlled as described above.
前記凝縮器側冷媒温度制御機器に、前記送風機故障検知手段から故障信号が入力された場合に、前記凝縮器側制御温度演算手段は送風機の故障台数と前記蒸発器内圧力センサの測定値と予め設定された冷却性能テーブルとから必要な凝縮器側制御温度を演算し、前記凝縮器側冷媒温度制御機器は、凝縮器側外部入力温度の設定温度を前記演算した値に低下させ、凝縮器冷媒液温度センサ測定値が設定温度になるように熱媒体流量制御弁を制御する請求項2に記載の冷媒循環装置。 Equipped with an evaporator pressure sensor,
When a failure signal is input from the blower failure detection means to the condenser-side refrigerant temperature control device, the condenser-side control temperature calculation means calculates the number of blower failures and the measured value of the pressure sensor in the evaporator in advance. The required condenser side control temperature is calculated from the set cooling performance table, and the condenser side refrigerant temperature control device reduces the set temperature of the condenser side external input temperature to the calculated value, and the condenser refrigerant The refrigerant circulation device according to claim 2, wherein the heat medium flow control valve is controlled so that the measured value of the liquid temperature sensor becomes a set temperature.
前記凝縮器側冷媒温度制御機器に、前記送風機故障検知手段から故障信号が入力された場合に、前記凝縮器側制御温度演算手段は送風機の故障台数と予め設定された冷却性能テーブルとから必要な凝縮器側制御温度を演算し、前記凝縮器側冷媒温度制御機器は、前記演算した値が室内露点温度以上の場合は凝縮器側外部入力温度の設定温度を演算値にし、前記演算した値が室内露点温度以下の場合は設定温度を室内露点温度に低下させ、凝縮器冷媒液温度センサ測定値が設定温度になるように熱媒体流量制御弁を制御する請求項2又は3に記載の冷媒循環装置。 It has an indoor dew point temperature sensor,
When a failure signal is input from the blower failure detection means to the condenser-side refrigerant temperature control device, the condenser-side control temperature calculation means is necessary from the number of blower failures and a preset cooling performance table. The condenser side control temperature is calculated, and when the calculated value is equal to or higher than the indoor dew point temperature, the condenser side refrigerant temperature control device uses the set temperature of the condenser side external input temperature as the calculated value, and the calculated value is The refrigerant circulation according to claim 2 or 3, wherein when the temperature is equal to or lower than the indoor dew point temperature, the set temperature is lowered to the indoor dew point temperature, and the heat medium flow control valve is controlled so that the measured value of the condenser refrigerant liquid temperature sensor becomes the set temperature. apparatus.
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JP2010139401A JP5351097B2 (en) | 2010-06-18 | 2010-06-18 | Refrigerant circulation device |
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GB1110161.5A GB2481317B (en) | 2010-06-18 | 2011-06-15 | Refrigerant circulation apparatus |
NL2006949A NL2006949C2 (en) | 2010-06-18 | 2011-06-16 | Refrigerant circulation apparatus. |
CN201110163201.XA CN102287972B (en) | 2010-06-18 | 2011-06-17 | Refrigerant circulation apparatus |
US13/162,912 US20110308262A1 (en) | 2010-06-18 | 2011-06-17 | Refrigerant circulation apparatus |
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JP5351097B2 true JP5351097B2 (en) | 2013-11-27 |
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JP2010139401A Active JP5351097B2 (en) | 2010-06-18 | 2010-06-18 | Refrigerant circulation device |
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US (1) | US20110308262A1 (en) |
JP (1) | JP5351097B2 (en) |
CN (1) | CN102287972B (en) |
GB (1) | GB2481317B (en) |
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Families Citing this family (22)
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AU2013219731B2 (en) | 2012-02-14 | 2015-05-14 | Nec Corporation | Cooling apparatus and cooling system |
JP5902053B2 (en) * | 2012-06-28 | 2016-04-13 | 株式会社日立製作所 | Cooling system and cooling method |
EP2927778A4 (en) * | 2012-12-03 | 2016-08-03 | Nec Corp | Cooling system for electronic equipment storage device and cooling system for electronic equipment storage facility |
ITPN20130005A1 (en) * | 2013-01-15 | 2014-07-16 | G I Ind Holding S P A | SYSTEM AND PROCEDURE TO COOL A CLOSED ENVIRONMENT, ESPECIALLY A WARDROBE CONTAINING ELECTRONIC APPLIANCES |
CN103115514B (en) * | 2013-02-25 | 2014-12-17 | 广东申菱空调设备有限公司 | Condensation-proof refrigerant circulating heat tube system and controlling method thereof |
JP6322425B2 (en) * | 2014-01-17 | 2018-05-09 | 株式会社デンソーエアクール | System for natural circulation of refrigerant |
JP6328004B2 (en) * | 2014-08-15 | 2018-05-23 | 株式会社大気社 | Compressor / pump switching type cooling device |
US20170280590A1 (en) * | 2014-08-27 | 2017-09-28 | Nec Corporation | Phase-change cooling device and phase-change cooling method |
US10375901B2 (en) | 2014-12-09 | 2019-08-13 | Mtd Products Inc | Blower/vacuum |
US11839062B2 (en) * | 2016-08-02 | 2023-12-05 | Munters Corporation | Active/passive cooling system |
US11255611B2 (en) * | 2016-08-02 | 2022-02-22 | Munters Corporation | Active/passive cooling system |
CN107249282B (en) * | 2017-07-10 | 2023-09-05 | 中国科学院广州能源研究所 | Heat pipe heat exchange device for reducing vertical temperature difference of data center rack server |
CN108562181A (en) * | 2017-12-28 | 2018-09-21 | 江西鑫田车业有限公司 | A kind of gravity type heat exchanger |
CN108050873A (en) * | 2017-12-28 | 2018-05-18 | 江西鑫田车业有限公司 | A kind of gravity type heat exchanger |
CN108088293A (en) * | 2017-12-28 | 2018-05-29 | 江西鑫田车业有限公司 | A kind of gravity type heat exchanger of 1X1 groups module |
CN107990770A (en) * | 2017-12-28 | 2018-05-04 | 江西鑫田车业有限公司 | A kind of gravity type heat exchanger of 2X2 groups module |
EP3620729B1 (en) | 2018-08-14 | 2024-04-17 | Hoffman Enclosures, Inc. | Thermal monitoring for cooling systems |
EP4001819A1 (en) * | 2020-11-12 | 2022-05-25 | Nokia Technologies Oy | Apparatus and systems for cooling |
CN112902314B (en) * | 2021-02-01 | 2023-07-14 | 青岛海信日立空调系统有限公司 | Air conditioner and control method for improving condensation and water blowing of air conditioner |
US11729940B2 (en) * | 2021-11-02 | 2023-08-15 | Oracle International Corporation | Unified control of cooling in computers |
US20230209774A1 (en) * | 2021-12-23 | 2023-06-29 | Baidu Usa Llc | Apparatus and system for two-phase server cooling |
US11711908B1 (en) * | 2022-03-18 | 2023-07-25 | Baidu Usa Llc | System and method for servicing and controlling a leak segregation and detection system of an electronics rack |
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JPH0810066B2 (en) * | 1987-10-31 | 1996-01-31 | 株式会社竹中工務店 | Building air conditioning system |
US5267450A (en) * | 1992-07-20 | 1993-12-07 | Matsushita Electric Ind. Co., Ltd. | Air conditioning apparatus |
JP2001248920A (en) * | 2000-03-06 | 2001-09-14 | Mitsubishi Electric Corp | Controller for refrigeration circuit |
US8322155B2 (en) * | 2006-08-15 | 2012-12-04 | American Power Conversion Corporation | Method and apparatus for cooling |
CN101646911B (en) * | 2007-02-14 | 2012-03-21 | 开利公司 | Optimization of air cooled chiller system operation |
JP4749369B2 (en) * | 2007-03-30 | 2011-08-17 | 三菱電機株式会社 | Refrigeration cycle apparatus failure diagnosis apparatus and refrigeration cycle apparatus equipped with the same |
US8151583B2 (en) * | 2007-08-01 | 2012-04-10 | Trane International Inc. | Expansion valve control system and method for air conditioning apparatus |
JP4780479B2 (en) * | 2008-02-13 | 2011-09-28 | 株式会社日立プラントテクノロジー | Electronic equipment cooling system |
JP2009216295A (en) * | 2008-03-10 | 2009-09-24 | Hitachi Plant Technologies Ltd | Cooling system of electronic device and its operating method |
DE102008030308A1 (en) * | 2008-06-30 | 2009-12-31 | Lindenstruth, Volker, Prof. | Building for a data center with facilities for efficient cooling |
JP5355008B2 (en) * | 2008-09-19 | 2013-11-27 | パナソニックヘルスケア株式会社 | Refrigeration equipment |
JP4850224B2 (en) * | 2008-10-28 | 2012-01-11 | 株式会社Nttファシリティーズ | Air conditioning system and operation method thereof |
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- 2011-06-15 SG SG2011043858A patent/SG177095A1/en unknown
- 2011-06-16 NL NL2006949A patent/NL2006949C2/en not_active IP Right Cessation
- 2011-06-17 US US13/162,912 patent/US20110308262A1/en not_active Abandoned
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GB2481317A (en) | 2011-12-21 |
US20110308262A1 (en) | 2011-12-22 |
SG177095A1 (en) | 2012-01-30 |
NL2006949A (en) | 2011-12-20 |
CN102287972B (en) | 2015-02-11 |
NL2006949C2 (en) | 2012-08-07 |
CN102287972A (en) | 2011-12-21 |
JP2012002456A (en) | 2012-01-05 |
GB201110161D0 (en) | 2011-07-27 |
GB2481317B (en) | 2012-08-08 |
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