JP2003207223A - Exhaust heat recovery-type refrigerating device - Google Patents
Exhaust heat recovery-type refrigerating deviceInfo
- Publication number
- JP2003207223A JP2003207223A JP2002007050A JP2002007050A JP2003207223A JP 2003207223 A JP2003207223 A JP 2003207223A JP 2002007050 A JP2002007050 A JP 2002007050A JP 2002007050 A JP2002007050 A JP 2002007050A JP 2003207223 A JP2003207223 A JP 2003207223A
- Authority
- JP
- Japan
- Prior art keywords
- evaporator
- compressor
- refrigerating
- absorption
- condenser
- 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.)
- Pending
Links
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
- Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/14—Combined heat and power generation [CHP]
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
- Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply
Landscapes
- Sorption Type Refrigeration Machines (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、空気調和装置に用
いることができる冷凍装置に係り、特に、エンジン、タ
ービン、燃料電池各種プラント等からの排熱を熱源とす
る吸収冷凍機からの冷凍効果を、圧縮冷凍機と組合せて
有効利用する冷凍装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerating apparatus that can be used in an air conditioner, and more particularly, to a refrigerating effect from an absorption refrigerating machine that uses exhaust heat from an engine, a turbine, various fuel cell plants, etc. as a heat source. The present invention relates to a refrigerating apparatus for effectively using the above in combination with a compression refrigerator.
【０００２】[0002]
【従来の技術】コージェネレーションシステムでは、電
気と共に、比較的温度の低い温水が供給される。この温
水は、温度があまり高くなく、低ポテンシャルエネルギ
に分類され、給湯又は暖房に利用されることが多く、ま
た最近は、吸収冷凍機の熱源として冷房に利用されるこ
とも多くなってきている。コージェネレーションシステ
ムの中で、この温水は、エンジンの冷却（ジャケット温
水）あるいはエンジン排ガスからの熱回収、あるいはガ
スタービンの排ガスからの熱回収で得られる。なお、排
ガスを温水に変換せず、直接吸収冷凍機の熱源とするこ
ともある。しかし、コージェネレーションシステムで、
排熱だけで吸収冷凍機を運転して、システムが必要とす
る冷凍負荷が賄えることはあまりなく、通常は、なんら
かの方法でバックアップしている。例えば、低ポテンシ
ャルエネルギ（温水）で、吸収冷凍機を運転する場合、
温水をバーナーで加熱し、熱量を増して冷凍容量を大き
くすることもあれば、排熱吸収冷凍機とは別に、直火式
の二重効用吸収冷凍機を設置し、冷凍負荷を賄えるよう
にしている。2. Description of the Related Art In a cogeneration system, hot water having a relatively low temperature is supplied together with electricity. This hot water is not so high in temperature, is classified into low potential energy, and is often used for hot water supply or heating. Recently, it has also been often used for cooling as a heat source of an absorption refrigerator. . In a cogeneration system, this hot water is obtained by cooling the engine (jacket hot water), recovering heat from the engine exhaust gas, or recovering heat from the exhaust gas of the gas turbine. The exhaust gas may be directly used as a heat source for the absorption refrigerator without being converted into hot water. But with the cogeneration system,
It is not possible to operate the absorption chiller with only the exhaust heat to cover the refrigeration load required by the system, and usually, some kind of backup is used. For example, when operating the absorption refrigerator with low potential energy (hot water),
In some cases, hot water is heated with a burner to increase the amount of heat to increase the refrigeration capacity.In addition to the exhaust heat absorption refrigerator, a direct-fire double-effect absorption refrigerator is installed to cover the refrigeration load. ing.
【０００３】また、排熱による冷凍効果だけでは負荷を
賄いきれないことを前提に、低ポテンシャルエネルギを
高ポテンシャルエネルギと共に用い、必要とする高ポテ
ンシャルエネルギ（燃料：ガス、油）の量を減らそうと
いう複合冷房装置も提案され採用されている。これらは
いずれも排熱の他に、さらに熱を加え、熱によるバック
アップを行うものである。一方、バックアップに用いる
高ポテンシャルエネルギを電気とし、必要とする電気の
量を減らす方法もある。即ち、吸収冷凍機の冷熱で、圧
縮冷凍機の循環冷媒を過冷却する冷凍装置（特開平１１
−２２３４１２号公報）である。しかし、この冷凍装置
においては、圧縮冷凍機の熱源側熱交換器が空気による
冷却と吸収冷凍機による冷却を直列に設けており、圧縮
冷凍機の圧縮機を運転しないかぎり、吸収冷凍機の冷凍
効果を利用することができなかった。また、冷媒液を冷
却しているだけであるので、負荷が軽く冷媒液量が少な
いと、吸収冷凍機の冷凍効果を使い切れないこともあ
り、排熱供給や冷房負荷の増減に対しての対応が不充分
であった。Further, on the assumption that the load cannot be covered only by the refrigerating effect by the exhaust heat, the low potential energy is used together with the high potential energy to reduce the required high potential energy (fuel: gas, oil). The combined air conditioner has been proposed and adopted. In addition to the exhaust heat, all of these apply heat to perform backup by heat. On the other hand, there is also a method in which the high potential energy used for backup is electricity and the amount of required electricity is reduced. That is, a refrigerating apparatus that supercools the circulating refrigerant of the compression refrigerator by the cold heat of the absorption refrigerator (Japanese Patent Laid-Open No. H11 (1999) -111945)
No. 223412). However, in this refrigeration system, the heat source side heat exchanger of the compression refrigerator is provided with cooling by air and cooling by the absorption refrigerator in series, and unless the compressor of the compression refrigerator is operated, refrigeration of the absorption refrigerator is performed. The effect could not be used. Also, since the refrigerant liquid is only being cooled, if the load is light and the amount of refrigerant liquid is small, the refrigeration effect of the absorption refrigerator may not be used up, so measures to deal with the increase or decrease in exhaust heat supply and cooling load Was insufficient.
【０００４】[0004]
【発明が解決しようとする課題】本発明は、上記従来技
術の問題点を解消し、冷房負荷及び吸収冷凍効果の状態
に応じて圧縮冷凍機の運転状態を調節でき、より具体的
には、排熱による吸収効果だけで冷凍負荷を賄えない
時、高ポテンシャルエネルギを電気としてバックアップ
できる経済的で効率のよい運転ができる空気調和装置と
して用いることのできる冷凍装置を提供することを課題
とする。DISCLOSURE OF THE INVENTION The present invention solves the above-mentioned problems of the prior art and can adjust the operating state of the compression refrigerator according to the cooling load and the state of the absorption refrigeration effect, and more specifically, An object of the present invention is to provide a refrigeration system that can be used as an air conditioner that can economically and efficiently operate by backing up high potential energy as electricity when the refrigeration load cannot be covered only by the absorption effect of exhaust heat. .
【０００５】[0005]
【課題を解決するための手段】上記課題を解決するため
に、本発明では、排熱を熱源として冷凍効果を発揮する
蒸発器Ｅを有する吸収冷凍機と、圧縮機、外気又は冷却
水で冷却する第一凝縮器、前記吸収冷凍機の蒸発器Ｅと
熱交換関係に接続した第二凝縮器及び冷凍効果を発揮す
る蒸発器Ｅｃを有する圧縮冷凍機とを組合せた冷凍装置
であって、前記圧縮機には、前記吸収冷凍機の冷凍効果
だけでば蒸発器Ｅｃへの負荷を賄いきれない時に運転す
る制御手段を備えていることを特徴とする冷凍装置とし
たものである。前記冷凍装置において、圧縮冷凍機は、
１台の吸収冷凍機に、複数台を接続することができ、ま
た、前記圧縮機を運転する制御手段は、前記蒸発器Ｅｃ
における被冷却媒体の目標温度と実際の温度（検出温
度）との差を基に（検出温度＞目標温度＋αのとき圧縮
機運転）行うか、又は、前記蒸発機Ｅｃにおける冷媒の
蒸発圧力を基に（蒸発圧力＞所定の圧力又は目標圧力＋
αのとき圧縮機運転）行うか、又は、前記吸収冷凍機の
蒸発温度又は蒸発温度に関連する物理量（例えば、吸収
冷凍機の冷熱搬送媒温度）を基に（蒸発温度＞所定温度
のとき圧縮機運転）行うことができる。In order to solve the above-mentioned problems, in the present invention, an absorption refrigerator having an evaporator E that exerts a refrigerating effect by using exhaust heat as a heat source, and a compressor, outside air or cooling water is used for cooling. Which is a combination of a first condenser, an evaporator E of the absorption refrigerator, a second condenser connected in a heat exchange relationship, and a compression refrigerator having an evaporator Ec exhibiting a refrigerating effect. The compressor is provided with a control means which is operated when the load on the evaporator Ec cannot be covered only by the refrigerating effect of the absorption refrigerating machine. In the refrigeration system, the compression refrigerator is
A plurality of units can be connected to one absorption refrigerator, and the control means for operating the compressor is the evaporator Ec.
Is performed based on the difference between the target temperature of the medium to be cooled and the actual temperature (detected temperature) (compressor operation when detected temperature> target temperature + α), or based on the evaporation pressure of the refrigerant in the evaporator Ec. (Evaporation pressure> predetermined pressure or target pressure +
Compressor operation when α), or based on the evaporation temperature of the absorption refrigerator or a physical quantity related to the evaporation temperature (for example, cold heat carrier medium temperature of the absorption refrigerator) (compression when evaporation temperature> predetermined temperature) Machine operation) can be performed.
【０００６】[0006]
【発明の実施の形態】本発明は、コジェネシステムにて
冷凍あるいは冷房を行うものであって、吸収冷凍機の出
力（冷凍効果）だけで負荷を賄いきれない時に圧縮冷凍
機でバックアップしようとするものである。また、本発
明は、自然循環吸収冷凍機を基にすれば、エンジン、タ
ービン、燃料電池等からの排熱を熱源とする吸収冷凍機
の冷凍効果にて、吸収冷凍機の作動媒体として吸収冷凍
機機器間を循環する冷媒とは別の冷媒Ｒｃ（冷凍効果搬
送冷媒）を凝縮器Ｃｃ２で凝縮させ、該凝縮冷媒を吸収
冷凍機とは別の場所にある蒸発器Ｅｃにて蒸発させて冷
凍効果を発揮させ、該蒸発冷媒は前記凝縮器Ｃｃ２に戻
すようにした冷凍装置（空気調和装置）であって、前記
冷凍効果搬送冷媒回路に、少なくとも冷媒蒸気を圧縮す
る圧縮機と外気あるいは冷却水で冷却する凝縮器Ｃｃ１
とを備え、吸収冷凍機の冷凍効果だけでは、蒸発器Ｅｃ
への負荷を賄いきれない時に、圧縮機を運転する制御手
段を備えている冷凍装置である。BEST MODE FOR CARRYING OUT THE INVENTION The present invention is for refrigerating or cooling in a cogeneration system, and tries to back up with a compression refrigerator when the load cannot be covered only by the output (refrigeration effect) of the absorption refrigerator. It is a thing. Further, according to the present invention, based on a natural circulation absorption refrigerator, absorption refrigeration as a working medium of the absorption refrigerator is achieved by the refrigeration effect of the absorption refrigerator that uses exhaust heat from an engine, a turbine, a fuel cell, etc. as a heat source. Refrigerant Rc (refrigerant effect carrier refrigerant) different from the refrigerant circulated between the machines and devices is condensed in the condenser Cc2, and the condensed refrigerant is evaporated in an evaporator Ec in a different place from the absorption refrigerator to be frozen. A refrigerating device (air conditioner) that exerts an effect and returns the evaporated refrigerant to the condenser Cc2, wherein a compressor for compressing at least refrigerant vapor and outside air or cooling water is provided in the refrigerating effect carrier refrigerant circuit. Condenser Cc1 cooled by
And the refrigerating effect of the absorption chiller alone is sufficient for the evaporator Ec.
The refrigeration system is equipped with a control means for operating the compressor when the load on the compressor cannot be covered.
【０００７】次に、本発明を図面を用いて詳細に説明す
る。図１〜図４は、本発明の冷凍装置の圧縮冷凍機側の
構成機器の接続例を示すフロー構成図であり、図５と図
６は、本発明の冷凍装置の吸収冷凍機と圧縮冷凍機とを
組合せた接続例を示すフロー構成図である。図におい
て、Ｍｃは圧縮機、Ｅｃは蒸発器、Ｃｃ１は第一凝縮
器、Ｃｃ２は第二凝縮器、ＴＡ、ＴＲ、ＴＳは温度セン
サー、Ｓｃは過冷却器を示す。図１において、（ａ）は
全体構成図、（ｂ）はＥｃ部詳細図であり、蒸発器Ｅｃ
からの冷媒蒸気は、圧縮機Ｍｃ停止中は、第二凝縮器Ｃ
ｃ２に吸引され、圧縮機Ｍｃ運転中は、圧縮機Ｍｃ又は
圧縮機Ｍｃと第二凝縮器Ｃｃ２に吸引される。吸収式か
らの熱搬送媒体の温度が低く、第二凝縮器Ｃｃ２で冷媒
蒸気が凝縮可能であれば、第二凝縮器Ｃｃ２に吸引さ
れ、第二凝縮器Ｃｃ２にて凝縮する。Next, the present invention will be described in detail with reference to the drawings. 1 to 4 are flow configuration diagrams showing connection examples of components on the compression refrigerator side of the refrigeration apparatus of the present invention, and FIGS. 5 and 6 are absorption refrigeration apparatus and compression refrigeration apparatus of the refrigeration apparatus of the present invention. It is a flow block diagram which shows the example of connection which combined with the machine. In the figure, Mc is a compressor, Ec is an evaporator, Cc1 is a first condenser, Cc2 is a second condenser, TA, TR, and TS are temperature sensors, and Sc is a supercooler. In FIG. 1, (a) is an overall configuration diagram, (b) is a detailed view of the Ec portion, and the evaporator Ec
The refrigerant vapor from the second condenser C while the compressor Mc is stopped.
It is sucked by c2 and is sucked by the compressor Mc or the compressor Mc and the second condenser Cc2 while the compressor Mc is operating. If the temperature of the heat transfer medium from the absorption type is low and the refrigerant vapor can be condensed in the second condenser Cc2, it is sucked into the second condenser Cc2 and condensed in the second condenser Cc2.
【０００８】吸収式からの熱搬送媒体の温度が高く、第
二凝縮器Ｃｃ２で冷媒蒸気が凝縮不能であれば、冷媒蒸
気の形で第二凝縮器Ｃｃ２に存在し、伝熱は殆ど生じな
い。圧縮冷凍機蒸発器Ｅｃの要求能力は、例えば、蒸発
器Ｅｃで冷却される媒体の温度を測る温度センサーと被
冷却媒体の目標温度との差とする。圧縮冷凍機を停止し
ていても、目標温度≧検出温度であれば、圧縮機Ｍｃを
運転する必要はない。目標温度≦検出温度のとき、圧縮
機Ｍｃを運転する必要が出てきたと判断する。あるディ
ファレンシャルを持たせて圧縮機Ｍｃを運転する。ま
た、インバータ付であれば、最小回転数で運転開始し、
停止時は、最小回転の後、温度比較をして判断する、図
中、過冷却器Ｓｃは、なくても差支えない。圧縮機Ｍｃ
を、複数台で構成してもよい。圧縮機複数台の場合、１
台をインバータ制御、他を台数制御（発停）としてもよ
い。If the temperature of the heat transfer medium from the absorption type is high and the refrigerant vapor cannot be condensed in the second condenser Cc2, it exists in the second condenser Cc2 in the form of refrigerant vapor, and heat transfer hardly occurs. . The required capacity of the compression refrigerator evaporator Ec is, for example, the difference between the temperature sensor measuring the temperature of the medium cooled by the evaporator Ec and the target temperature of the medium to be cooled. Even if the compression refrigerator is stopped, if the target temperature ≧ the detected temperature, it is not necessary to operate the compressor Mc. When the target temperature ≦ the detected temperature, it is determined that it is necessary to operate the compressor Mc. The compressor Mc is operated with a certain differential. Also, with an inverter, start operation at the minimum speed,
When stopped, the temperature is compared after the minimum rotation for determination. In the figure, the supercooler Sc may be omitted. Compressor Mc
May be composed of a plurality of units. For multiple compressors, 1
The table may be controlled by an inverter, and the others may be controlled by the number of vehicles (starting and stopping).
【０００９】図２（ａ）では、蒸発器Ｅｃからの冷媒蒸
気は、圧縮機Ｍｃ停止中は、第二凝縮器Ｃｃ２に吸引さ
れ、圧縮機Ｍｃ運転中は、圧縮機Ｍｃ又は圧縮機Ｍｃと
第二凝縮器Ｃｃ２に吸引される。吸収式からの熱搬送媒
体の温度が低く、第二凝縮器Ｃｃ２で冷媒蒸気が凝縮可
能であれば、第二凝縮器Ｃｃ２に吸引され、第二凝縮器
Ｃｃ２で凝縮する。吸収式からの熱搬送媒体の温度が高
く、第二凝縮器Ｃｃ２で冷媒蒸気が凝縮不能であれば、
冷媒蒸気の形で第二凝縮器Ｃｃ２には吸引されない。Ｃ
ｃ１で凝縮した冷媒液は、Ｃｃ２で過冷却される。制御
は、吸込み圧力を基に、吸込み圧が所定値より低い場合
は、圧縮機を停止し、越えた場合は運転とし、さらに目
標値になるように圧縮機の回転速度を調整するような制
御をしてもよい。図２（ｂ）のようにして、冷媒液の流
れ方向の切換えで、Ｃｃ２での過冷却の有無を制御し、
吸収冷凍機への負荷を調整しても差支えなく、また、図
１と同様に温度で制御しても差支えない。また、図２に
おいて、蒸発器Ｅｃは、図１（ｂ）と同様である。In FIG. 2 (a), the refrigerant vapor from the evaporator Ec is sucked into the second condenser Cc2 while the compressor Mc is stopped, and is discharged to the compressor Mc or the compressor Mc while the compressor Mc is operating. It is sucked into the second condenser Cc2. If the temperature of the heat transfer medium from the absorption type is low and the refrigerant vapor can be condensed in the second condenser Cc2, it is sucked into the second condenser Cc2 and condensed in the second condenser Cc2. If the temperature of the heat transfer medium from the absorption type is high and the refrigerant vapor cannot be condensed in the second condenser Cc2,
It is not sucked into the second condenser Cc2 in the form of refrigerant vapor. C
The refrigerant liquid condensed in c1 is supercooled in Cc2. The control is based on the suction pressure, when the suction pressure is lower than a predetermined value, the compressor is stopped, and when it exceeds, it is operated, and the rotation speed of the compressor is adjusted to reach the target value. You may As shown in FIG. 2 (b), the presence or absence of supercooling in Cc2 is controlled by switching the flow direction of the refrigerant liquid,
It does not matter if the load on the absorption refrigerator is adjusted, or if it is controlled by temperature as in FIG. Further, in FIG. 2, the evaporator Ec is the same as that in FIG. 1 (b).
【００１０】図３は、圧縮機Ｍｃ１と第一凝縮器Ｃｃ１
の系統と、圧縮機Ｍｃ２と第二凝縮器Ｃｃ２の系統とを
持った構成を示す。第二凝縮器Ｃｃ２の系統の圧縮機Ｍ
ｃ２を停止している状態の動作は、図１と同様の動きを
する。圧縮冷凍機蒸発器Ｅｃの要求能力は、例えば、蒸
発器Ｅｃで冷却される媒体の温度を測る温度センサーと
被冷却媒体の目標温度との差とする。圧縮冷凍機を停止
していても、目標温度≧検出温度であれば、圧縮機を運
転する必要はない。目標温度≦検出温度のとき、Ｃｃ２
の凝縮温度あるいは吸収冷凍効果搬送媒体の温度を判断
して、所定の値より高ければ、低ヘッド圧縮機Ｍｃ２を
運転し、低ければ、高ヘッド圧縮機Ｍｃ１を運転する。
一方の圧縮機を運転しても要求能力を満足できない時
は、両方とも運転する。簡易的には、吸収冷凍効果搬送
媒体の温度を基にして、低ヘッド圧縮機Ｍｃ２の運転、
高ヘッド圧縮機Ｍｃ１の運転を制御しても差支えない。FIG. 3 shows a compressor Mc1 and a first condenser Cc1.
And a system of the compressor Mc2 and the second condenser Cc2. Compressor M of the system of the second condenser Cc2
The operation when c2 is stopped operates in the same manner as in FIG. The required capacity of the compression refrigerator evaporator Ec is, for example, the difference between the temperature sensor measuring the temperature of the medium cooled by the evaporator Ec and the target temperature of the medium to be cooled. Even if the compression refrigerator is stopped, if the target temperature ≧ the detected temperature, it is not necessary to operate the compressor. Cc2 when target temperature ≤ detected temperature
If the temperature is higher than the predetermined value, the low head compressor Mc2 is operated, and if it is lower than the predetermined value, the high head compressor Mc1 is operated.
If one compressor does not meet the required capacity even if it is operated, both compressors are operated. Briefly, the operation of the low head compressor Mc2 is based on the temperature of the absorption / refrigeration effect carrier medium,
It does not matter if the operation of the high head compressor Mc1 is controlled.
【００１１】図４（ａ）は、圧縮機Ｍｃ１と第一凝縮器
Ｃｃ１の系統と、圧縮機Ｍｃ２と第二凝縮器Ｃｃ２系統
とを持った構成を示す。第二凝縮器Ｃｃ２の系統の圧縮
機Ｍｃ２を停止している状態の動作は、図２と同様の動
きをする。圧縮冷凍機蒸発器Ｅｃの要求能力は、例え
ば、蒸発器Ｅｃで冷却される媒体の温度を測る温度セン
サーと被冷却媒体の目標温度との差とする。圧縮冷凍機
を停止していても、目標温度≧検出温度であれば、圧縮
機を運転する必要はない。目標温度≦検出温度のとき、
Ｃｃ２の凝縮温度を判断して所定の値より、高ければ、
低ヘッド圧縮機Ｍｃ２を運転し、低ければ、高ヘッド圧
縮機Ｍｃ１を運転する。一方の圧縮機を運転しても要求
能力を満足できない時は、両方とも運転する。Ｃｃ１で
凝縮した冷媒液は、Ｃｃ２で過冷却される。図４（ｂ）
のようにして、Ｃｃ２での過冷却の有無を制御しても差
支えない。FIG. 4A shows a configuration having a compressor Mc1 and a first condenser Cc1 system, and a compressor Mc2 and a second condenser Cc2 system. The operation in the state in which the compressor Mc2 of the system of the second condenser Cc2 is stopped operates in the same manner as in FIG. The required capacity of the compression refrigerator evaporator Ec is, for example, the difference between the temperature sensor measuring the temperature of the medium cooled by the evaporator Ec and the target temperature of the medium to be cooled. Even if the compression refrigerator is stopped, if the target temperature ≧ the detected temperature, it is not necessary to operate the compressor. When target temperature ≤ detected temperature,
If the condensation temperature of Cc2 is judged and is higher than a predetermined value,
The low head compressor Mc2 is operated, and if it is low, the high head compressor Mc1 is operated. If one compressor does not meet the required capacity even if it is operated, both compressors are operated. The refrigerant liquid condensed in Cc1 is supercooled in Cc2. Figure 4 (b)
As described above, the presence or absence of supercooling in Cc2 may be controlled.
【００１２】図５と図６は、吸収冷凍機と圧縮冷凍機と
を組合せたフロー構成図であり、図５と図６において、
Ａは吸収器、Ｅは蒸発器、Ｇは再生器、Ｃは凝縮器、Ｓ
Ｐは吸収溶液ポンプ、ＲＰは冷媒ポンプ、１は吸収冷凍
機、１０は熱交換器、１１〜１４、１６は溶液管路、１
５、１７、１８は冷媒管路、１９は冷水循環路、２０は
冷却水循環路、２１は排熱源流路である。図５、図６に
おいて、吸収冷凍機では、冷媒を吸収した溶液は、吸収
器Ａから吸収溶液ポンプＳＰにより熱交換器１０の被加
熱側を通り、管路１２から再生器Ｇへと導かれる。再生
器Ｇでは、溶液は、外部ガスタービン等からの排ガスを
熱源２１として加熱されて冷媒を蒸発して濃縮され、管
路１３から熱交換器１０の加熱側を通り、吸収器Ａへ導
入される。一方、再生器Ｇで発生した冷媒蒸気は、凝縮
器Ｃにおいて冷却水により凝縮した後蒸発器Ｅへと導か
れ、蒸発器Ｅでは、冷水循環路１９から潜熱を奪うこと
で冷水の取り出しが可能となる。FIGS. 5 and 6 are flow configuration diagrams in which an absorption refrigerator and a compression refrigerator are combined. In FIGS. 5 and 6,
A is an absorber, E is an evaporator, G is a regenerator, C is a condenser, S
P is an absorption solution pump, RP is a refrigerant pump, 1 is an absorption refrigerator, 10 is a heat exchanger, 11 to 14 and 16 are solution lines, 1
5, 17 and 18 are refrigerant pipes, 19 is a cold water circulation path, 20 is a cooling water circulation path, and 21 is an exhaust heat source flow path. 5 and 6, in the absorption refrigerator, the solution that has absorbed the refrigerant passes from the absorber A to the heated side of the heat exchanger 10 by the absorption solution pump SP, and is guided from the pipe line 12 to the regenerator G. . In the regenerator G, the solution is heated by using the exhaust gas from the external gas turbine or the like as the heat source 21 to evaporate the refrigerant to be concentrated, and then is introduced from the pipe line 13 into the absorber A through the heating side of the heat exchanger 10. It On the other hand, the refrigerant vapor generated in the regenerator G is guided to the evaporator E after being condensed by the cooling water in the condenser C, and in the evaporator E, the latent heat is taken from the cold water circulation path 19 so that the cold water can be taken out. Becomes
【００１３】図５では、圧縮冷凍機サイクルは図１の過
冷却器なしの構成であり、前記の蒸発器Ｅの吸収冷凍効
果を搬送媒体（例えば、冷水循環路１９）を各凝縮器Ｃ
ｃ２に直列に分配している。図６は、冷水分配を並列に
した例であり、圧縮冷凍機サイクルは図２の例である。
各Ｃｃ２への分配量を制御し、吸収冷凍機への負荷を調
整してもよい。吸収冷凍機側の制御は、排熱を総て生か
しきるように運転して、蒸発器冷媒凍結回避及び吸収溶
液結晶回避のときは、熱源からの入熱量を制限する。圧
縮式とは無関係に、吸収式側だけで制御をしてもよい。In FIG. 5, the compression refrigerator cycle is the structure without the supercooler of FIG. 1, and the absorption refrigeration effect of the evaporator E is transferred to the carrier medium (for example, the cold water circulation path 19) to each condenser C.
It is distributed in series to c2. FIG. 6 is an example in which cold water distribution is performed in parallel, and the compression refrigerator cycle is the example in FIG. 2.
The load on the absorption refrigerator may be adjusted by controlling the distribution amount to each Cc2. The control on the absorption refrigerating machine side is operated so as to make full use of the exhaust heat, and limits the heat input amount from the heat source at the time of avoiding the freezing of the evaporator refrigerant and avoiding the absorption solution crystal. Regardless of the compression type, control may be performed only on the absorption type side.
【００１４】吸収冷凍機への負荷が多すぎて、あるいは
吸収式への熱源熱量による能力よりも多すぎて、吸収式
の蒸発温度あるいは冷凍出力温度が高くなり過ぎる場
合、過冷却器への熱媒流量等を減少、あるいは第二凝縮
器Ｃｃ２への熱媒流量等を減少させる。これらの制御
は、吸収式側から一方的に行っても差支えない。複数台
の圧縮冷凍機と１台の吸収冷凍機を組合せる場合、熱媒
体循環量を全体として制御してもよいし、個別に制御し
てもよい。圧縮冷凍機側は、利用できる吸収冷凍機出力
を用い、その範囲内で制御している。また、圧縮機側と
吸収式側とを関連付けて制御しても差支えないが、制御
系が複雑になり過ぎる欠点がでる。If the absorption refrigerating machine has too much load, or is too much in capacity as the heat quantity of the heat source to the absorption type, and the evaporation temperature or the refrigerating output temperature of the absorption type becomes too high, the heat to the subcooler is increased. The medium flow rate or the like is reduced, or the heat medium flow rate or the like to the second condenser Cc2 is reduced. These controls may be performed unilaterally from the absorption side. When a plurality of compression refrigerators and one absorption refrigerator are combined, the heat medium circulation amount may be controlled as a whole or individually. The compression refrigerator side uses available absorption refrigerator output and controls within that range. Further, although it does not matter if the compressor side and the absorption type side are associated and controlled, there is a drawback that the control system becomes too complicated.
【００１５】本発明において、吸収冷凍機は、単効用、
二重効用、一二重効用等、特に限定はなく、また吸収冷
凍機の作動媒体による限定もない。熱源の形態も、温
水、水蒸気、燃料あるいは排ガスなど、特に限定はな
い。また、排熱に限定せず、安価な燃料などを熱源とす
る吸収冷凍機であってもよい。また、本発明では、１台
の圧縮冷凍機を構成する各機器は複数器であっても差支
えない。圧縮冷凍機として、説明しているが、配管切換
でヒートポンプによる暖房運転とする形態をとってもよ
い。そのとき、吸収冷凍機を冷温水機として温熱をヒー
トポンプに与え、あるいは、排熱源を直接ヒートポンプ
に与えても良い。In the present invention, the absorption refrigerator is a single-effect type,
There is no particular limitation such as double effect or single effect, and there is no limitation due to the working medium of the absorption refrigerator. The form of the heat source is not particularly limited, such as hot water, steam, fuel or exhaust gas. Further, it is not limited to exhaust heat, and may be an absorption refrigerator that uses an inexpensive fuel or the like as a heat source. Further, in the present invention, each device constituting one compression refrigerator may be a plurality of devices. Although described as a compression refrigerator, a mode of performing heating operation by a heat pump by switching pipes may be adopted. At that time, the absorption refrigerator may be used as a cold / hot water machine to supply heat to the heat pump, or the exhaust heat source may be directly supplied to the heat pump.
【００１６】[0016]
【発明の効果】本発明は、圧縮冷凍機の圧縮機を運転せ
ず、吸収冷凍効果単独でも冷媒回路の冷凍能力（圧縮冷
凍機の冷凍能力）を出すことができ、また、圧縮機を運
転している時でも、吸収冷凍効果を充分に発揮できるよ
うにしている。また、吸収冷凍効果を優先的に用い、吸
収冷凍効果単独での運転を可能とし、電気によるバック
アップも可能にして、吸収冷凍効果を充分に利用、使い
きることができる空気調和装置として用いることができ
る冷凍装置である。INDUSTRIAL APPLICABILITY According to the present invention, the refrigerating capacity of the refrigerant circuit (refrigerating capacity of the compression refrigerator) can be obtained by the absorption refrigeration effect alone without operating the compressor of the compression refrigerator, and the compressor is operated. It is designed so that the absorption and refrigeration effect can be fully exerted even when it is being used. Further, the absorption refrigeration effect is preferentially used, the operation of the absorption refrigeration effect alone can be performed, and the backup by electric power is also possible, so that the absorption refrigeration effect can be used sufficiently and used as an air conditioner. It is a refrigeration device that can.
【図１】本発明の冷凍装置の圧縮冷凍機の一例を示すフ
ロー構成図で、（ａ）は全体図、（ｂ）はＥｃ部詳細
図。FIG. 1 is a flow configuration diagram showing an example of a compression refrigerator of a refrigeration apparatus of the present invention, (a) is an overall view, and (b) is a detailed view of an Ec portion.
【図２】（ａ）、（ｂ）は、本発明の冷凍装置の圧縮冷
凍機の他の例を示すフロー構成図。2A and 2B are flow configuration diagrams showing another example of the compression refrigerator of the refrigeration apparatus of the present invention.
【図３】本発明の冷凍装置の圧縮冷凍機の他の例を示す
フロー構成図。FIG. 3 is a flow configuration diagram showing another example of the compression refrigerator of the refrigeration apparatus of the present invention.
【図４】（ａ）、（ｂ）は、本発明の冷凍装置の圧縮冷
凍機の他の例を示すフロー構成図。4A and 4B are flow configuration diagrams showing another example of the compression refrigerator of the refrigeration apparatus of the present invention.
【図５】本発明の冷凍装置の吸収冷凍機と圧縮冷凍機を
組合せた例を示すフロー構成図。FIG. 5 is a flow configuration diagram showing an example in which an absorption refrigerator and a compression refrigerator of the refrigeration apparatus of the present invention are combined.
【図６】本発明の冷凍装置の吸収冷凍機と圧縮冷凍機を
組合せた別の例を示すフロー構成図。FIG. 6 is a flow configuration diagram showing another example in which the absorption refrigerator and the compression refrigerator of the refrigeration apparatus of the present invention are combined.
Ｍｃ、Ｍｃ１、Ｍｃ２：圧縮機、Ｅｃ：蒸発器、Ｃｃ
１：第一凝縮器、Ｃｃ２：第二凝縮器、Ｓｃ：過冷却
器、ＴＡ、ＴＲ、ＴＳ：温度センサー、Ａ：吸収器、
Ｇ：再生器、Ｃ：凝縮器、Ｅ：蒸発器、ＳＰ：吸収溶液
ポンプ、ＲＰ：冷媒ポンプ、１：吸収冷凍機、１０：熱
交換器、１１〜１４、１６：溶液管路、１５、１７、１
８：冷媒管路、１９：冷水循環路、２０：冷却水循環
路、２１：排熱源流路Mc, Mc1, Mc2: Compressor, Ec: Evaporator, Cc
1: first condenser, Cc2: second condenser, Sc: supercooler, TA, TR, TS: temperature sensor, A: absorber,
G: regenerator, C: condenser, E: evaporator, SP: absorption solution pump, RP: refrigerant pump, 1: absorption refrigerator, 10: heat exchanger, 11 to 14, 16: solution pipe line, 15, 17, 1
8: Refrigerant pipeline, 19: Cold water circulation channel, 20: Cooling water circulation channel, 21: Exhaust heat source channel
───────────────────────────────────────────────────── フロントページの続き (72)発明者 入江 毅一 東京都大田区羽田旭町11番１号 株式会社 荏原製作所内 (72)発明者 遠藤 哲也 東京都大田区羽田旭町11番１号 株式会社 荏原製作所内 (72)発明者 青山 淳 東京都大田区羽田旭町11番１号 株式会社 荏原製作所内 (72)発明者 内村 知行 東京都大田区羽田旭町11番１号 株式会社 荏原製作所内 (72)発明者 福住 幸大 東京都大田区羽田旭町11番１号 株式会社 荏原製作所内 ─────────────────────────────────────────────────── ─── Continued front page (72) Inventor, Koichi Irie 11-1 Haneda Asahi-cho, Ota-ku, Tokyo Co., Ltd. Inside the EBARA CORPORATION (72) Inventor Tetsuya Endo 11-1 Haneda Asahi-cho, Ota-ku, Tokyo Co., Ltd. Inside the EBARA CORPORATION (72) Inventor Jun Aoyama 11-1 Haneda Asahi-cho, Ota-ku, Tokyo Co., Ltd. Inside the EBARA CORPORATION (72) Inventor Tomoyuki Uchimura 11-1 Haneda Asahi-cho, Ota-ku, Tokyo Co., Ltd. Inside the EBARA CORPORATION (72) Inventor Kodai Fukuzumi 11-1 Haneda Asahi-cho, Ota-ku, Tokyo Co., Ltd. Inside the EBARA CORPORATION
Claims (5)
発器Ｅを有する吸収冷凍機と、圧縮機、外気又は冷却水
で冷却する第一凝縮器、前記吸収冷凍機の蒸発器Ｅと熱
交換関係に接続した第二凝縮器及び冷凍効果を発揮する
蒸発器Ｅｃを有する圧縮冷凍機とを組合せた冷凍装置で
あって、前記圧縮機には、前記吸収冷凍機の冷凍効果だ
けでは蒸発器Ｅｃへの負荷を賄いきれない時に運転する
制御手段を備えていることを特徴とする冷凍装置。1. An absorption refrigerator having an evaporator E that exerts a refrigerating effect using exhaust heat as a heat source, a compressor, a first condenser cooled by outside air or cooling water, an evaporator E of the absorption refrigerator, and heat. A refrigerating apparatus in which a second condenser connected in an exchange relationship and a compression refrigerator having an evaporator Ec exhibiting a refrigerating effect are combined, and the compressor is an evaporator having only the refrigerating effect of the absorption refrigerator. A refrigerating apparatus comprising a control unit that operates when the load on Ec cannot be covered.
に、複数台を接続することを特徴とする請求項１記載の
冷凍装置。2. The refrigerating apparatus according to claim 1, wherein a plurality of the compression refrigerators are connected to one absorption refrigerator.
蒸発器Ｅｃにおける被冷却媒体の目標温度と実際の温度
との差を基に行うことを特徴とする請求項１又は２記載
の冷凍装置。3. The refrigerating machine according to claim 1 or 2, wherein the control means for operating the compressor operates based on a difference between a target temperature and an actual temperature of the medium to be cooled in the evaporator Ec. apparatus.
蒸発器Ｅｃにおける冷媒の蒸発圧力を基に行うことを特
徴とする請求項１又は２記載の冷凍装置。4. The refrigerating apparatus according to claim 1, wherein the control means for operating the compressor operates based on the evaporation pressure of the refrigerant in the evaporator Ec.
吸収冷凍機の蒸発温度又は蒸発温度に関連する物理量を
基に行うことを特徴とする請求項１又は２記載の冷凍装
置。5. The refrigerating apparatus according to claim 1, wherein the control means for operating the compressor performs the evaporation temperature of the absorption refrigerator or a physical quantity related to the evaporation temperature.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002007050A JP2003207223A (en) | 2002-01-16 | 2002-01-16 | Exhaust heat recovery-type refrigerating device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002007050A JP2003207223A (en) | 2002-01-16 | 2002-01-16 | Exhaust heat recovery-type refrigerating device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003207223A true JP2003207223A (en) | 2003-07-25 |
Family
ID=27645656
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2002007050A Pending JP2003207223A (en) | 2002-01-16 | 2002-01-16 | Exhaust heat recovery-type refrigerating device |
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| Country | Link |
|---|---|
| JP (1) | JP2003207223A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010249356A (en) * | 2009-04-13 | 2010-11-04 | Daikin Ind Ltd | Refrigerating device |
| JP2010249357A (en) * | 2009-04-13 | 2010-11-04 | Daikin Ind Ltd | Refrigerating device |
| JP2010255862A (en) * | 2009-04-21 | 2010-11-11 | Daikin Ind Ltd | Refrigerating device |
| JP2010255860A (en) * | 2009-04-21 | 2010-11-11 | Daikin Ind Ltd | Refrigerating device |
| CN106679210A (en) * | 2016-11-28 | 2017-05-17 | 中国科学院理化技术研究所 | Novel variable-pressure-ratio vapor compression/heat pipe integrated machine room air conditioning system and control method thereof |
-
2002
- 2002-01-16 JP JP2002007050A patent/JP2003207223A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010249356A (en) * | 2009-04-13 | 2010-11-04 | Daikin Ind Ltd | Refrigerating device |
| JP2010249357A (en) * | 2009-04-13 | 2010-11-04 | Daikin Ind Ltd | Refrigerating device |
| JP2010255862A (en) * | 2009-04-21 | 2010-11-11 | Daikin Ind Ltd | Refrigerating device |
| JP2010255860A (en) * | 2009-04-21 | 2010-11-11 | Daikin Ind Ltd | Refrigerating device |
| CN106679210A (en) * | 2016-11-28 | 2017-05-17 | 中国科学院理化技术研究所 | Novel variable-pressure-ratio vapor compression/heat pipe integrated machine room air conditioning system and control method thereof |
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