JP2013519066A - Heat source and cold source of air conditioning system with independent control of temperature and humidity - Google Patents

Heat source and cold source of air conditioning system with independent control of temperature and humidity Download PDF

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JP2013519066A
JP2013519066A JP2013509427A JP2013509427A JP2013519066A JP 2013519066 A JP2013519066 A JP 2013519066A JP 2013509427 A JP2013509427 A JP 2013509427A JP 2013509427 A JP2013509427 A JP 2013509427A JP 2013519066 A JP2013519066 A JP 2013519066A
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compressor
evaporator
condenser
expansion valve
cold
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ション ワン
タオ ジャン
デハイ ジョウ
シエンティン リ
ウェンシン シ
シャオフア リウ
ダ ヤン
バオロン ワン
陽一郎 入谷
憲治 上田
潤之助 仲谷
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Mitsubishi Heavy Industries Ltd
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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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/147—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with both heat and humidity transfer between supplied and exhausted air
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator

Abstract

本発明は、圧縮機（１）と、連続して接続された第１の凝縮器（２）及び第２の凝縮器（３）と、それぞれが第２の凝縮器（３）に接続された第１の膨張弁（４）及び第２の膨張弁（５）と、それぞれが圧縮機（１）に接続された第１の蒸発器（６）及び第２の蒸発器（７）とを備えた、ＴＨＩＣ空調システムの熱源及び冷熱源を開示する。第１の蒸発器（６）は第１の膨張弁（４）に接続されて第１の循環支流を形成し、第２の蒸発器（７）は第２の膨張弁（５）に接続されて第２の循環支流を形成し、並列に接続された第１の循環支流と前記第２の循環支流とが、第２の凝縮器（３）と圧縮機（１）とを接続している。本発明のＴＨＩＣ空調システムの熱源及び冷熱源は、比較的高い冷凍効率を有し、それにより、エネルギー消費を著しく低減し、且つ、大気環境を保護する。  The present invention comprises a compressor (1), a first condenser (2) and a second condenser (3) connected in series, each connected to a second condenser (3). A first expansion valve (4) and a second expansion valve (5), and a first evaporator (6) and a second evaporator (7) each connected to the compressor (1). Further, a heat source and a cold heat source of the THIC air conditioning system are disclosed. The first evaporator (6) is connected to the first expansion valve (4) to form a first circulation tributary, and the second evaporator (7) is connected to the second expansion valve (5). The second circulation tributary and the first circulation tributary connected in parallel and the second circulation tributary connect the second condenser (3) and the compressor (1). . The heat and cold sources of the THIC air conditioning system of the present invention have a relatively high refrigeration efficiency, thereby significantly reducing energy consumption and protecting the atmospheric environment.

Description

本発明は、概して、冷凍及び空調設備の技術分野に関するものであり、より詳細には、温度及び湿度を独立して制御可能な（Ｔｅｍｐｅｒａｔｕｒｅ ａｎｄ Ｈｕｍｉｄｉｔｙ Ｉｎｄｅｐｅｎｄｅｎｔ Ｃｏｎｔｒｏｌ：ＴＨＩＣ）空調システムの熱源及び冷熱源に関する。   The present invention relates generally to the technical field of refrigeration and air conditioning equipment, and more particularly to heat and cold sources of an air conditioning system with independent control of temperature and humidity (THIC). .

ＴＨＩＣ空調システムは、屋内の温度制御のための独立した顕熱処理システム、及び屋内の湿度制御のための独立した潜熱処理システムから成る空調システムを対象としている。ＴＨＩＣ空調システムは、空調システムの性能を改善し、エネルギー消費量を低減し、屋内の空気の質を高め、且つ、大気環境を保護するという利点により、近年益々広く用いられている。特許文献１は、ヒートポンプにより駆動される、液体乾燥剤を用いた高効率なフレッシュエア処理ユニットを提示している。   The THIC air conditioning system is intended for an air conditioning system consisting of an independent sensible heat treatment system for indoor temperature control and an independent latent heat treatment system for indoor humidity control. THIC air conditioning systems are increasingly used in recent years due to the advantages of improving the performance of air conditioning systems, reducing energy consumption, improving indoor air quality, and protecting the air environment. Patent Document 1 presents a high-efficiency fresh air processing unit using a liquid desiccant driven by a heat pump.

このフレッシュエアユニットは、乾燥剤濃縮溶液をヒートポンプの蒸発器（エバポレータ）により冷却して溶液の吸湿能力を高めるとともに、吸湿プロセス中に放出される潜熱を除去する。また、このフレッシュエアユニットは、再生された希薄溶液を同一のヒートポンプの凝縮器により加熱する。この溶液は、全熱回収の排気を用いた全熱交換を実行することにより濃縮され、再生された溶液となる。   This fresh air unit cools the desiccant concentrated solution by an evaporator (evaporator) of a heat pump to increase the moisture absorption capacity of the solution and remove latent heat released during the moisture absorption process. Moreover, this fresh air unit heats the regenerated diluted solution by the condenser of the same heat pump. This solution is concentrated and regenerated by performing a total heat exchange using exhaust from total heat recovery.

特許文献１に提示されているヒートポンプ駆動式液体乾燥剤フレッシュエアユニットのエネルギー効率比（ＥＥＲ）は比較的高く、このフレッシュエアユニットの実用性は非常に有望である。以下に記載するＴＨＩＣ空調システムにおいて、液体乾燥剤フレッシュエアユニットとは、特許文献１に提示されたヒートポンプ駆動式液体乾燥剤フレッシュエアユニットを示す。   The energy efficiency ratio (EER) of the heat pump driven liquid desiccant fresh air unit presented in Patent Document 1 is relatively high, and the practicality of this fresh air unit is very promising. In the THIC air conditioning system described below, the liquid desiccant fresh air unit refers to the heat pump-driven liquid desiccant fresh air unit presented in Patent Document 1.

図１は、先行技術におけるＴＨＩＣ空調システムの動作原理を示す概略図である。屋内の顕熱が冷凍機１からの高温（約１８℃）冷水により除去され、屋内の潜熱が液体乾燥剤フレッシュエアユニットからの乾燥した冷たいフレッシュエアにより除去される。液体乾燥剤フレッシュエアユニットにおいて、液体除湿器により要求される冷却能力、及び、液体再生器により要求される加熱能力が冷凍機２により提供される。冷凍機１及び冷凍機２は、ＴＨＩＣ空調システムの熱源及び冷熱源と見なすことができる。   FIG. 1 is a schematic diagram showing the operating principle of a THIC air conditioning system in the prior art. Indoor sensible heat is removed by high temperature (about 18 ° C.) cold water from the refrigerator 1 and indoor latent heat is removed by dry cold fresh air from the liquid desiccant fresh air unit. In the liquid desiccant fresh air unit, the refrigerator 2 provides the cooling capacity required by the liquid dehumidifier and the heating capacity required by the liquid regenerator. The refrigerator 1 and the refrigerator 2 can be regarded as a heat source and a cold heat source of the THIC air conditioning system.

先行技術におけるＴＨＩＣ空調システムの熱源及び冷熱源に関し、冷凍機１は、通常、比較的大きい冷却能力を有するターボ冷凍機又はスクリュー冷凍機であり、冷凍機２は、通常、比較的小さい冷却能力を有する渦流冷凍機である。冷凍機２として、ターボ冷凍機は用いられない。なぜなら、慣用のターボ冷凍機の冷却能力は数千キロワットであり、冷凍機２により要求される冷却能力は、通常のフレッシュエアの必要条件（１８０００ｍ３／時未満）によれば通常２００ｋｗ未満であるからである。 Regarding the heat source and cooling source of the THIC air conditioning system in the prior art, the refrigerator 1 is usually a turbo refrigerator or a screw refrigerator having a relatively large cooling capacity, and the refrigerator 2 usually has a relatively small cooling capacity. It is an eddy current refrigerator. A turbo refrigerator is not used as the refrigerator 2. Because the cooling capacity of a conventional turbo refrigerator is several thousand kilowatts, the cooling capacity required by the refrigerator 2 is usually less than 200 kW according to the normal fresh air requirements (less than 18000 m 3 / hour) Because.

しかし、渦流冷凍機の冷凍効率は、通常、ターボ冷凍機の冷凍効率よりも低い（渦流冷凍機の定格値は通常３〜４であるのに対し、ターボ冷凍機の冷凍効率の定格値は５〜６である）。ターボ冷凍機を、渦流冷凍機の冷却能力レベルを有する程度に十分に小さくすることができるならば、渦流冷凍機をターボ冷凍機に置き替えることが可能である。   However, the refrigeration efficiency of the vortex refrigerator is usually lower than the refrigeration efficiency of the turbo chiller (the rated value of the vortex refrigerator is usually 3 to 4, whereas the rated value of the refrigeration efficiency of the turbo refrigerator is 5). ~ 6). If the turbo refrigerator can be made small enough to have the cooling capacity level of the vortex refrigerator, the vortex refrigerator can be replaced by a turbo refrigerator.

要約すると、先行技術のＴＨＩＣ空調システムの熱源及び冷熱源の冷凍効率は比較的低く、エネルギー消費量を低減して大気環境を保護することには不利である。 In summary, the refrigeration efficiency of the heat and cold sources of the prior art THIC air conditioning system is relatively low, which is disadvantageous for reducing energy consumption and protecting the atmospheric environment.

中国特許出願公開第１８６２１２３号明細書Chinese Patent Application Publication No. 1862123

本発明により解決されるべき技術的課題は、上記の欠点に対して、エネルギー消費量を低減し且つ大気環境を保護するために、冷凍効率が高められたＴＨＩＣ空調システムの熱源及び冷熱源を提供することにある。   The technical problem to be solved by the present invention is to provide a heat source and a cold heat source of a THIC air conditioning system with an increased refrigeration efficiency in order to reduce energy consumption and protect the atmospheric environment, against the above drawbacks. There is to do.

上記の技術的課題を解決するために、本発明は、ＴＨＩＣ空調システムの熱源及び冷熱源であって圧縮機１と、連続して接続された第１の凝縮器２及び第２の凝縮器３と、前記第２の凝縮器３に接続された第１の膨張弁４と、前記第２の凝縮器３に接続された前記第２の膨張弁５と、前記圧縮機１に接続された第１の蒸発器６と、前記圧縮機１に接続された第２の蒸発器７とを備えた熱源及び冷熱源を提供する。前記第１の蒸発器６は前記第１の膨張弁４に接続されて第１の循環支流を形成し、前記第２の蒸発器７は第２の膨張弁５に接続されて第２の循環支流を形成し、並列に接続された前記第１の循環支流と前記第２の循環支流とが、前記第２の凝縮器３と前記圧縮機１とを接続している。   In order to solve the above technical problem, the present invention is a heat source and a cold heat source of a THIC air conditioning system, which is a compressor 1 and a first condenser 2 and a second condenser 3 connected in series. The first expansion valve 4 connected to the second condenser 3, the second expansion valve 5 connected to the second condenser 3, and the first expansion valve connected to the compressor 1. A heat source and a cold source provided with one evaporator 6 and a second evaporator 7 connected to the compressor 1 are provided. The first evaporator 6 is connected to the first expansion valve 4 to form a first circulation branch, and the second evaporator 7 is connected to the second expansion valve 5 to be connected to the second circulation valve. The first circulation tributary and the second circulation tributary that form a tributary and are connected in parallel connect the second condenser 3 and the compressor 1.

前記圧縮機１が遠心圧縮機であるのが好ましい。前記第１の膨張弁４が、前記第１の蒸発器６の出口冷水の温度を調節するために用いられるのが好ましい。前記第２の膨張弁５が、前記第２の蒸発器７の出口希釈溶液の温度を調節するために用いられるのが好ましい。   The compressor 1 is preferably a centrifugal compressor. The first expansion valve 4 is preferably used to adjust the temperature of the outlet cold water of the first evaporator 6. The second expansion valve 5 is preferably used to adjust the temperature of the outlet diluted solution of the second evaporator 7.

本発明は、さらに、ＴＨＩＣ空調システムの熱及び冷熱源であって、１以上の冷凍機ａと、１以上の冷凍機ｂを備え、前記冷凍機ａが、環を形成するように互いに接続された、第１の圧縮機１ａと、第１の凝縮器２ａと、第１の膨張弁３ａと、第１の蒸発器４ａとを含み、前記冷凍機ｂが、環を形成するように互いに接続された、第２の圧縮機１ｂと、第２の凝縮器２ｂと、第２の膨張弁３ｂと、第２の蒸発器４ｂとを含む熱源及び冷熱源を提供する。   The present invention is further a heat and cold source of a THIC air conditioning system, comprising one or more refrigerators a and one or more refrigerators b, wherein the refrigerators a are connected to each other so as to form a ring. The first compressor 1a, the first condenser 2a, the first expansion valve 3a, and the first evaporator 4a are connected to each other so that the refrigerator b forms a ring. Thus, a heat source and a cold source including the second compressor 1b, the second condenser 2b, the second expansion valve 3b, and the second evaporator 4b are provided.

前記第１の圧縮機１ａ及び前記第２の圧縮機１ｂが遠心圧縮機であるのが好ましい。
前記１以上の冷凍機ａがそれぞれ独立に制御され、前記１以上の冷凍機ｂがそれぞれ独立に制御されるのが好ましい。 The first compressor 1a and the second compressor 1b are preferably centrifugal compressors.
Preferably, the one or more refrigerators a are controlled independently, and the one or more refrigerators b are controlled independently.

本発明は、屋内の顕熱及び屋内の潜熱を除去するための圧縮機として１つのターボ冷凍機が用いられるＴＨＩＣ空調システムの熱源及び冷熱源を提供することにより、小規模なＴＨＩＣ空調システム（全冷却能力が２５０ｋＷ未満）の熱源及び冷熱源に求められる要件を満たすことができる。   The present invention provides a heat source and a cold source of a THIC air conditioning system in which one turbo chiller is used as a compressor for removing indoor sensible heat and indoor latent heat. The requirements for a heat source having a cooling capacity of less than 250 kW) and a cold heat source can be satisfied.

本発明は、さらに、屋内の顕熱及び屋内の潜熱をそれぞれ独立に除去するために少なくとも２つのターボ冷凍機が圧縮機として用いられる他のＴＨＩＣ空調システムの熱源及び冷熱源を提供することにより、大規模なＴＨＩＣ空調システム（全冷却能力が５００ｋＷよりも大きい）の熱源及び冷熱源に求められる要件を満たすことができる。   The present invention further provides heat and cold sources for other THIC air conditioning systems in which at least two turbo chillers are used as compressors to independently remove indoor sensible heat and indoor latent heat, respectively. The requirements for heat and cold sources of large scale THIC air conditioning systems (total cooling capacity greater than 500 kW) can be met.

従来の渦流冷凍機と比較して、ターボ冷凍機は、冷凍効率に関する明確な利点を有するので、ターボ冷凍機をＴＨＩＣ空調システムの熱源及び冷熱源として用いることにより、全冷凍効率が高められ得る。従って、エネルギー消費を著しく低減し、且つ大気環境を保護することが可能である。   Compared to conventional vortex chillers, turbo chillers have distinct advantages with respect to refrigeration efficiency, so the total refrigeration efficiency can be increased by using turbo chillers as heat and cold sources for THIC air conditioning systems. Therefore, it is possible to significantly reduce energy consumption and protect the atmospheric environment.

従来技術におけるＴＨＩＣ空調システムの動作原理を示す概略図である。It is the schematic which shows the operation principle of the THIC air conditioning system in a prior art. 本発明の第１の実施形態に係るＴＨＩＣ空調システムの熱源及び冷熱源を示す構造概略図である。1 is a structural schematic diagram showing a heat source and a cold heat source of a THIC air conditioning system according to a first embodiment of the present invention. 本発明の第２の実施形態に係るＴＨＩＣ空調システムの熱源及び冷熱源を示す構造概略図である。FIG. 5 is a structural schematic diagram showing a heat source and a cold heat source of a THIC air conditioning system according to a second embodiment of the present invention.

以下に、本発明を実施するための特定の実施形態について、図面及び実施形態を参照しつつ詳細に説明する。以下の実施形態は、本発明の説明として提示されるものであり、本発明の範囲を限定するものではない。   Hereinafter, specific embodiments for carrying out the present invention will be described in detail with reference to the drawings and embodiments. The following embodiments are presented as explanations of the present invention and are not intended to limit the scope of the present invention.

＜第１の実施形態＞
図２は、本発明の第１の実施形態に係るＴＨＩＣ空調システムの熱源及び冷熱源を示す構造概略図である。図２に示されているように、ＴＨＩＣ空調システムの熱源及び冷熱源は、圧縮機１と、連続して接続された第１の凝縮器２及び第２の凝縮器３と、第２の凝縮器３に接続された第１の膨張弁４と、第２の凝縮器３に接続された第２の膨張弁５と、圧縮器１に接続された第１の蒸発器６と、圧縮機１に接続された第２の蒸発器７とを備えている。 <First Embodiment>
FIG. 2 is a structural schematic diagram showing a heat source and a cold heat source of the THIC air conditioning system according to the first embodiment of the present invention. As shown in FIG. 2, the heat source and the cold source of the THIC air conditioning system are the compressor 1, the first condenser 2 and the second condenser 3 connected in series, and the second condensation. A first expansion valve 4 connected to the compressor 3, a second expansion valve 5 connected to the second condenser 3, a first evaporator 6 connected to the compressor 1, and the compressor 1 And a second evaporator 7 connected to the.

第１の蒸発器６は第１の膨張弁４に接続されて第１の循環支流を形成し、第２の蒸発器７は第２の膨張弁５に接続されて第２の循環支流を形成している。並列に接続された第１の循環支流と第２の循環支流とが、第２の凝縮器３と圧縮機１とを接続している。   The first evaporator 6 is connected to the first expansion valve 4 to form a first circulation tributary, and the second evaporator 7 is connected to the second expansion valve 5 to form a second circulation tributary. doing. The first circulation tributary and the second circulation tributary connected in parallel connect the second condenser 3 and the compressor 1.

最初に、圧縮機１からの高温（４５℃よりも高温）の出口冷媒が第１の凝縮器２に流入し、出口冷媒とは逆方向に第１の凝縮器２の他方を流れる濃縮溶液を加熱する。次に、第１の凝縮器２からの出口冷媒が第２の凝縮器３に流入し、出口冷媒とは逆方向に第２の凝縮器３の他方を流れる冷却水により余剰凝縮熱が除去される。   First, a high-temperature (higher than 45 ° C.) outlet refrigerant from the compressor 1 flows into the first condenser 2, and a concentrated solution that flows through the other side of the first condenser 2 in the opposite direction to the outlet refrigerant. Heat. Next, the outlet refrigerant from the first condenser 2 flows into the second condenser 3, and excess condensation heat is removed by the cooling water flowing in the other direction of the second condenser 3 in the opposite direction to the outlet refrigerant. The

第２の凝縮器３の出口冷媒は、第１の膨張弁４及び第２の膨張弁５によりそれぞれ調節される２つの流れに分岐される。これらの流れの一方が、第１の循環支流に入って第１の膨張弁４を通過してから第１の蒸発器６に流入することにより、出口冷媒とは逆方向に第１の蒸発器６の他方を流れる高温（１８〜２１℃）の冷水を冷却する。   The outlet refrigerant of the second condenser 3 is branched into two flows respectively adjusted by the first expansion valve 4 and the second expansion valve 5. One of these flows enters the first circulation branch, passes through the first expansion valve 4 and then flows into the first evaporator 6, whereby the first evaporator is in the direction opposite to the outlet refrigerant. The cold water of high temperature (18-21 degreeC) which flows through the other of 6 is cooled.

他方の流れは、第２の循環支流に入って第２の膨張弁５を通過してから第２の蒸発器７に流入することにより、出口冷媒とは逆方向に第２の蒸発器７の他方を流れる希釈溶液を冷却する。第１の循環支流及び第２の循環支流の（すなわち、第１の蒸発器６及び第２の蒸発器７の）出口冷媒は、混合されて１つの冷媒流となって圧縮機１に戻る。そして、冷媒は、処理された後に次のサイクルに入る。   The other flow enters the second circulation tributary, passes through the second expansion valve 5 and then flows into the second evaporator 7, thereby causing the second evaporator 7 to flow in the direction opposite to the outlet refrigerant. Cool the diluted solution flowing through the other. The outlet refrigerant of the first circulation tributary and the second circulation tributary (that is, the first evaporator 6 and the second evaporator 7) is mixed and returned to the compressor 1 as one refrigerant stream. The refrigerant then enters the next cycle after being processed.

この実施形態において、ＴＨＩＣ空調システムの熱源及び冷熱源の圧縮機１は、遠心圧縮機、例えば、１７５ｋＷの冷却能力を有する遠心圧縮機である（ワン ジアら（Ｗａｎｇ Ｊｉａ ｅｔ ａｌ．）、「マイクロターボ冷凍機の性能分析（Ｐｅｒｆｏｒｍａｎｃｅ ａｎａｌｙｓｉｓ ｏｎ ｍｉｃｒｏ ｃｅｎｔｒｉｆｕｇａｌ ｃｈｉｌｌｅｒｓ）」、中国暖通空調ＨＶ＆ＡＣ、空気調和・衛生工学会論文、２００９年、第３９巻、第５期、１０４〜１０８頁）。   In this embodiment, the THIC air conditioning system heat source and cold source compressor 1 is a centrifugal compressor, eg, a centrifugal compressor having a cooling capacity of 175 kW (Wang Jia et al., “Micro “Performance analysis on micro centrifugal chillers”, China Hyundai Air Conditioning HV & AC, Air Conditioning and Sanitary Engineering Society, 2009, Vol. 39, No. 5, pp. 104-108).

この実施形態においては、濃縮溶液入口９を通って第１の凝縮器２に入る濃縮溶液が、冷媒により約４５℃に加熱され、濃縮溶液出口８を通って再生器に送られる。冷水入口１２を通って第１の蒸発器６に入った冷水が、冷媒により約１８℃に冷却され、冷水出口１３を通って屋内の顕熱部に送られる。希釈溶液入口１４を通って第２の蒸発器７に入った希釈溶液が、冷媒により約１４℃に冷却され、希釈溶液出口１５を通って除湿器に送られる。   In this embodiment, the concentrated solution entering the first condenser 2 through the concentrated solution inlet 9 is heated to about 45 ° C. by the refrigerant and sent to the regenerator through the concentrated solution outlet 8. The cold water that has entered the first evaporator 6 through the cold water inlet 12 is cooled to about 18 ° C. by the refrigerant, and is sent to the indoor sensible heat section through the cold water outlet 13. The diluted solution that has entered the second evaporator 7 through the diluted solution inlet 14 is cooled to about 14 ° C. by the refrigerant, and is sent to the dehumidifier through the diluted solution outlet 15.

この実施形態においては、第１の蒸発器６の出口冷水の温度、及び、第２の蒸発器７の出口希釈溶液の温度が、それぞれ、第１の膨張弁４及び第２の膨張弁５により調節され、第１の蒸発器６及び第２の蒸発器７の冷却能力がそれぞれ蒸発器としての必要条件を満たすものとされる。   In this embodiment, the temperature of the outlet cold water of the first evaporator 6 and the temperature of the outlet diluted solution of the second evaporator 7 are changed by the first expansion valve 4 and the second expansion valve 5, respectively. The cooling capacity of the first evaporator 6 and the second evaporator 7 is adjusted so as to satisfy the requirements as an evaporator.

この実施形態においては、圧縮機１の周波数又はガイドベーン（案内羽根）の角度が、第１の蒸発器６及び第２の蒸発器７の出口冷媒の過熱度に応じて全冷媒流を調節するように調節され、冷凍機の全冷却能力が顕熱及び潜熱を除去する必要条件を満たすものとされる。   In this embodiment, the frequency of the compressor 1 or the angle of the guide vane (guide vane) adjusts the total refrigerant flow according to the degree of superheat of the outlet refrigerant of the first evaporator 6 and the second evaporator 7. Thus, the total cooling capacity of the refrigerator satisfies the requirement for removing sensible heat and latent heat.

この実施形態においては、凝縮温度が、冷却水入口１１を通って第２の凝縮器３に入る冷却水の温度又は流れを調節することにより調節され、第１の凝縮器２の出口濃縮溶液温度が、濃縮溶液の必要条件を満たすものとされる。   In this embodiment, the condensing temperature is adjusted by adjusting the temperature or flow of cooling water entering the second condenser 3 through the cooling water inlet 11 and the outlet concentrated solution temperature of the first condenser 2. However, it shall satisfy the requirements of the concentrated solution.

＜第２の実施形態＞
図３は、本発明の第２の実施形態に係るＴＨＩＣ空調システムの熱源及び冷熱源の構造概略図である。図３に示されているように、ＴＨＩＣ空調システムの熱源及び冷熱源は、１以上の冷凍機ａと、１以上の冷凍機ｂを備え、冷凍機ａが、第１の圧縮機１ａ、第１の凝縮器２ａ、第１の膨張弁３ａ、及び、第１の蒸発器４ａを含み、これらが互いに接続されて環を形成している。また、冷凍機ｂが、第２の圧縮機１ｂ、第２の凝縮器２ｂ、第２の膨張弁３ｂ、及び、第２の蒸発器４ｂを含み、これらが互いに接続されて環を形成している。 <Second Embodiment>
FIG. 3 is a schematic structural diagram of a heat source and a cold heat source of a THIC air conditioning system according to the second embodiment of the present invention. As shown in FIG. 3, the heat source and the cold heat source of the THIC air conditioning system include one or more refrigerators a and one or more refrigerators b, and the refrigerator a includes the first compressor 1a, the first 1 condenser 2a, 1st expansion valve 3a, and 1st evaporator 4a, these are connected mutually and form the ring. The refrigerator b includes a second compressor 1b, a second condenser 2b, a second expansion valve 3b, and a second evaporator 4b, which are connected to each other to form a ring. Yes.

冷凍機ａにおいては、最初に、第１の圧縮機１ａの出口冷媒が第１の凝縮器２ａに流入し、出口冷媒とは逆方向に第１の凝縮器２ａの他方を流れる冷却水により冷凍機ａにより発生された凝縮熱が除去される。第１の凝縮器２ａからの出口冷媒が、第１の膨張弁３ａを通って第１の蒸発器４ａに流入し、出口冷媒とは逆方向に第１の蒸発器４ａの他方を流れる高温冷水が冷却される。第１の蒸発器４ａの出口冷媒は、第１の圧縮機１ａに流入し、処理された後に次のサイクルに入る。   In the refrigerator a, first, the outlet refrigerant of the first compressor 1a flows into the first condenser 2a, and is refrigerated by the cooling water flowing in the other direction of the first condenser 2a in the opposite direction to the outlet refrigerant. The heat of condensation generated by machine a is removed. High-temperature cold water in which the outlet refrigerant from the first condenser 2a flows into the first evaporator 4a through the first expansion valve 3a and flows through the other side of the first evaporator 4a in the opposite direction to the outlet refrigerant. Is cooled. The outlet refrigerant of the first evaporator 4a flows into the first compressor 1a and enters the next cycle after being processed.

冷凍機ｂにおいては、最初に、第２の圧縮機１ｂの出口冷媒が第２の凝縮器２ｂに流入し、出口冷媒とは逆方向に第２の凝縮器２ｂの他方を流れる濃縮溶液を冷媒の高温により加熱する。第２の凝縮器２ｂの出口冷媒が、第２の膨張弁３ｂを通って第２の蒸発器４ｂに流入し、出口冷媒とは逆方向に第２の蒸発器４ｂの他方を流れる希釈溶液が冷却される。第２の蒸発器４ｂの出口冷媒は、第２の圧縮機１ｂに流入し、処理された後に次のサイクルに入る。   In the refrigerator b, first, the outlet refrigerant of the second compressor 1b flows into the second condenser 2b, and the concentrated solution flowing in the other direction of the second condenser 2b in the opposite direction to the outlet refrigerant is used as the refrigerant. Heat at high temperature. The outlet refrigerant of the second condenser 2b flows into the second evaporator 4b through the second expansion valve 3b, and the diluted solution flowing through the other side of the second evaporator 4b in the direction opposite to the outlet refrigerant is To be cooled. The outlet refrigerant of the second evaporator 4b flows into the second compressor 1b and enters the next cycle after being processed.

この実施形態において、第１の圧縮機１ａ及び第２の圧縮機１ｂは、例えば、１７５ｋＷの冷却能力を有する遠心圧縮機である（ワン ジアら（Ｗａｎｇ Ｊｉａ ｅｔ ａｌ．）、「マイクロターボ冷凍機の性能分析（Ｐｅｒｆｏｒｍａｎｃｅ ａｎａｌｙｓｉｓ ｏｎ ｍｉｃｒｏ ｃｅｎｔｒｉｆｕｇａｌ ｃｈｉｌｌｅｒ）」、中国暖通空調ＨＶ＆ＡＣ、空気調和・衛生工学会論文、２００９年、第３９巻、第５期、１０４〜１０８頁）。   In this embodiment, the first compressor 1a and the second compressor 1b are, for example, centrifugal compressors having a cooling capacity of 175 kW (Wang Jia et al., “Micro Turbo Refrigerator”). (Performance analysis on micro centrifugal chiller) ”, China Hot Air Conditioning HV & AC, Air Conditioning and Sanitary Engineering Society, 2009, Vol. 39, No. 5, 104-108).

この実施形態においては、冷水入口７を通って第１の蒸発器４ａに入った高温冷水が、冷媒により約１８℃に冷却され、冷水出口８を通って屋内の顕熱部に送られる。濃縮溶液入口１０を通って第２の凝縮器ｂに入る濃縮溶液が、冷媒により約４５℃に加熱され、濃縮溶液出口９を通って再生器に送られる。希釈溶液入口１１を通って第２の蒸発器４ｂに入った希釈溶液が、冷媒により約１４℃に冷却され、希釈溶液出口１２を通って除湿器に送られる。   In this embodiment, the high-temperature cold water that has entered the first evaporator 4 a through the cold water inlet 7 is cooled to about 18 ° C. by the refrigerant and is sent to the indoor sensible heat section through the cold water outlet 8. The concentrated solution entering the second condenser b through the concentrated solution inlet 10 is heated to about 45 ° C. by the refrigerant and sent to the regenerator through the concentrated solution outlet 9. The diluted solution that has entered the second evaporator 4 b through the diluted solution inlet 11 is cooled to about 14 ° C. by the refrigerant, and is sent to the dehumidifier through the diluted solution outlet 12.

この実施形態においては、１以上の冷凍機ａがそれぞれ独立に制御される。また１以上の冷凍機ｂがそれぞれ独立に制御される。   In this embodiment, one or more refrigerators a are controlled independently. One or more refrigerators b are controlled independently.

要約すると、本発明は、屋内の顕熱及び屋内の潜熱の両方を除去するために１つのターボ冷凍機が圧縮機として用いられるＴＨＩＣ空調システムの熱源及び冷熱源を提供することにより、小規模なＴＨＩＣ空調システム（全冷却能力が２５０ｋＷ未満）の熱源及び冷熱源に求められる要件を満たすことができる。本発明は、さらに、屋内の顕熱及び屋内の潜熱をそれぞれ独立に除去するために少なくとも２つのターボ冷凍機が圧縮機として用いられる他のＴＨＩＣ空調システムの熱源及び冷熱源を提供することにより、大規模なＴＨＩＣ空調システム（全冷却能力が５００ｋＷよりも大きい）の熱源及び冷熱源に求められる要件を満たすことができる。   In summary, the present invention provides a heat source and cold source for a THIC air conditioning system in which one turbo refrigerator is used as a compressor to remove both indoor sensible heat and indoor latent heat. The requirements for the heat source and the cold source of the THIC air conditioning system (total cooling capacity less than 250 kW) can be satisfied. The present invention further provides heat and cold sources for other THIC air conditioning systems in which at least two turbo chillers are used as compressors to independently remove indoor sensible heat and indoor latent heat, respectively. The requirements for heat and cold sources of large scale THIC air conditioning systems (total cooling capacity greater than 500 kW) can be met.

従来の渦流冷凍機と比較して、ターボ冷凍機は、冷凍効率に関する明確な利点を有するので、ターボ冷凍機をＴＨＩＣ空調システムの熱源及び冷熱源として用いることにより、全冷凍効率が高められ得る。従って、エネルギー消費を著しく低減し、且つ大気環境を保護することが可能である。   Compared to conventional vortex chillers, turbo chillers have distinct advantages with respect to refrigeration efficiency, so the total refrigeration efficiency can be increased by using turbo chillers as heat and cold sources for THIC air conditioning systems. Therefore, it is possible to significantly reduce energy consumption and protect the atmospheric environment.

上記の実施形態は、本発明を説明するためにのみ用いられるが、本発明の保護範囲を限定するものではない。当業者は、本発明の趣旨及び範囲から逸脱せずに様々な変更及び修正を実行し得る。従って、均等な解決手段の全ては、添付の特許請求の範囲により定義される本発明の保護範囲内にあるものとする。   The above embodiments are used only to explain the present invention, but do not limit the protection scope of the present invention. Those skilled in the art may make various changes and modifications without departing from the spirit and scope of the present invention. Accordingly, all equivalent solutions are intended to be within the protection scope of the present invention as defined by the appended claims.

１ 圧縮機
１ａ 第１の圧縮機
２ 第１の凝縮器
２ａ 第１の凝縮器
２ｂ 第２の凝縮器
３ 第２の凝縮器
３ａ 第１の膨張弁
３ｂ 第１の膨張弁
４ 第１の膨張弁
４ａ 第１の蒸発器
４ｂ 第２の蒸発器
５ 第２の膨張弁
６ 第１の蒸発器
７ 第２の蒸発器
９ 濃縮液入口
１１ 冷却水入口 DESCRIPTION OF SYMBOLS 1 Compressor 1a 1st compressor 2 1st condenser 2a 1st condenser 2b 2nd condenser 3 2nd condenser 3a 1st expansion valve 3b 1st expansion valve 4 1st expansion Valve 4a First evaporator 4b Second evaporator 5 Second expansion valve 6 First evaporator 7 Second evaporator 9 Concentrate inlet 11 Cooling water inlet

Claims (7)

温度及び湿度を独立に制御可能な空調システムの熱源及び冷熱源であって、
圧縮機（１）と、
連続して接続された第１の凝縮器（２）及び第２の凝縮器（３）と、
前記第２の凝縮器（３）に接続された第１の膨張弁（４）と、
前記第２の凝縮器（３）に接続された第２の膨張弁（５）と、
前記圧縮機（１）に接続された第１の蒸発器（６）と、
前記圧縮機（１）に接続された第２の蒸発器（７）とを備え、
前記第１の蒸発器（６）が前記第１の膨張弁（４）に接続されて第１の循環支流を形成し、
前記第２の蒸発器（７）が前記第２の膨張弁（５）に接続されて第２の循環支流を形成し、
並列に接続された前記第１の循環支流と前記第２の循環支流とが、前記第２の凝縮器（３）と前記圧縮機（１）とを接続している熱源及び冷熱源。 A heat source and a cold source of an air conditioning system capable of independently controlling temperature and humidity,
A compressor (1);
A first condenser (2) and a second condenser (3) connected in series;
A first expansion valve (4) connected to the second condenser (3);
A second expansion valve (5) connected to the second condenser (3);
A first evaporator (6) connected to the compressor (1);
A second evaporator (7) connected to the compressor (1),
The first evaporator (6) is connected to the first expansion valve (4) to form a first circulation tributary;
The second evaporator (7) is connected to the second expansion valve (5) to form a second circulation tributary;
A heat source and a cold heat source in which the first circulation branch and the second circulation branch connected in parallel connect the second condenser (3) and the compressor (1). 前記圧縮機（１）が遠心圧縮機である請求項１に記載の熱源及び冷熱源。   The heat source and cold source according to claim 1, wherein the compressor (1) is a centrifugal compressor. 前記第１の膨張弁（４）が、前記第１の蒸発器（６）の出口冷水の温度を調節するために用いられる請求項１に記載の熱源及び冷熱源。   The heat and cold source according to claim 1, wherein the first expansion valve (4) is used to adjust the temperature of the outlet cold water of the first evaporator (6). 前記第２の膨張弁（５）が、第２の蒸発器（７）の出口希釈溶液の温度を調節するために用いられる請求項１に記載の熱源及び冷熱源。   The heat and cold source according to claim 1, wherein the second expansion valve (5) is used to adjust the temperature of the outlet diluted solution of the second evaporator (7). 温度及び湿度を独立に制御可能な空調システムの熱源及び冷熱源であって、
１以上の冷凍機（ａ）と、
１以上の冷凍機（ｂ）を備え、
前記冷凍機（ａ）が、環を形成するように互いに接続された、第１の圧縮機（１ａ）と、第１の凝縮器（２ａ）と、第１の膨張弁（３ａ）と、第１の蒸発器（４ａ）とを含み、
前記冷凍機（ｂ）が、環を形成するように互いに接続された、第２の圧縮機（１ｂ）と、第２の凝縮器（２ｂ）と、第２の膨張弁（３ｂ）と、第２の蒸発器（４ｂ）を含む熱源及び冷熱源。 A heat source and a cold source of an air conditioning system capable of independently controlling temperature and humidity,
One or more refrigerators (a);
Comprising one or more refrigerators (b),
A first compressor (1a), a first condenser (2a), a first expansion valve (3a), a first compressor, and a refrigerator (a) connected to each other so as to form a ring. 1 evaporator (4a),
A second compressor (1b), a second condenser (2b), a second expansion valve (3b), and a second compressor (b) connected to each other so as to form a ring. Heat source and cold source including two evaporators (4b). 前記第１の圧縮機（１ａ）及び前記第２の圧縮機（１ｂ）が遠心圧縮機である請求項５に記載の熱源及び冷熱源。   The heat source and cold source according to claim 5, wherein the first compressor (1a) and the second compressor (1b) are centrifugal compressors. 前記１以上の冷凍機（ａ）がそれぞれ独立に制御され、
前記１以上の冷凍機（ｂ）がそれぞれ独立に制御される請求項５に記載の熱源及び冷熱源。 The one or more refrigerators (a) are independently controlled;
The heat source and cold heat source according to claim 5, wherein the one or more refrigerators (b) are controlled independently of each other.
JP2013509427A 2011-04-12 2011-04-12 Heat source and cold source of air conditioning system with independent control of temperature and humidity Pending JP2013519066A (en)

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