JP5194517B2 - Air conditioner - Google Patents

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JP5194517B2
JP5194517B2 JP2007092436A JP2007092436A JP5194517B2 JP 5194517 B2 JP5194517 B2 JP 5194517B2 JP 2007092436 A JP2007092436 A JP 2007092436A JP 2007092436 A JP2007092436 A JP 2007092436A JP 5194517 B2 JP5194517 B2 JP 5194517B2
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heat recovery
heat exchanger
exhaust
outdoor
unit
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JP2008249267A (en
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博司 堤
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
    • 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

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  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Description

本発明は、空気調和装置の改良に関し、更に詳しくは、建物の排気ダクトに配置した熱回収機により排熱を再利用する空気調和装置に関する。   The present invention relates to an improvement of an air conditioner, and more particularly to an air conditioner that reuses exhaust heat by a heat recovery device disposed in an exhaust duct of a building.

従来、空調における省エネルギー対処策として、建物の排気には、一般的に、全（顕）熱交換器により再熱利用することが行われている。
しかしながら、前記全熱交換器を用いる場合、給気系統および排気系統を全てダクトにより構成する必要があるため、多大なスペースを要し、ダクト工事も大掛かりなものとなり、製作コストが高価であるという問題点があった。 Conventionally, as an energy-saving measure in air conditioning, reheating of buildings is generally performed using a full (sensible) heat exchanger.
However, when the total heat exchanger is used, since it is necessary to configure all of the air supply system and the exhaust system with ducts, a large space is required, the duct work becomes large, and the production cost is high. There was a problem.

前記問題点に対し、外気の取り入れ部と排気部とを建物の同一壁面部に設けてダクト工事の簡略化を図ることが考えられるが、この場合、外気の取り入れと排気とが同一壁面部で実施されることから排気が再度給気される虞があり、この方策は、実用上いま一つ不満足である。   In order to solve the above problems, it is conceivable to simplify the duct work by providing an outside air intake part and an exhaust part on the same wall surface of the building. There is a possibility that the exhaust gas is supplied again because it is implemented, and this measure is not satisfactory in practice.

特開平０９−０９６４６９JP 09-096469

この発明は、上述のような課題を解決するためになされたもので、その目的は、従来形式の空気調和装置におけるように、大きなスペースとか大掛かりなダクト工事を要することなく、既存の建物の一端の給気口から他端の排気口に延びる単一の排気系統または排気ダクトを利用し、該ダクト内に配置した熱回収用熱交換器を用いて再熱利用効率を有効に高め得る空気調和装置を提供することにある。   The present invention has been made in order to solve the above-described problems, and its object is to provide an end of an existing building without requiring a large space or a large-scale duct work as in a conventional air conditioner. Air conditioning that can effectively improve the efficiency of reheat utilization by using a single exhaust system or exhaust duct extending from the air supply port to the other exhaust port and using a heat recovery heat exchanger disposed in the duct To provide an apparatus.

この発明の空気調和装置においては、排気ダクトに配置した熱回収用熱交換器が蒸発器として作用するときは予め定めたスーパーヒート目標値を維持する一方、凝縮器として作用するときは予め定めたサブクール目標値を維持するように熱回収用電動膨張弁を制御する熱回収制御装置と、前記圧縮機における吸入圧力の飽和温度または吐出圧力の飽和温度が所定値となるように前記圧縮機の容量を制御する室外制御装置とを設けたものである。   In the air conditioner according to the present invention, when the heat recovery heat exchanger arranged in the exhaust duct acts as an evaporator, the predetermined superheat target value is maintained, while when it acts as a condenser, it is predetermined. A heat recovery control device that controls the electric expansion valve for heat recovery so as to maintain a subcool target value; and a capacity of the compressor such that a saturation temperature of the suction pressure or a saturation temperature of the discharge pressure in the compressor becomes a predetermined value. And an outdoor control device for controlling the.

この発明によれば、排気ダクト内に配置した熱回収機の熱回収用熱交換器を、室外機の冷媒系統に組み込み、該室外機の熱交換器における蒸発器または凝縮器として機能する状態と同一の熱交換作用状態となるように冷媒回路を制御し、排気温度に応じて熱回収用熱交換器に接続した電動膨張弁の開度を調節することにより室外機の熱交換器と熱回収用熱交換器との熱交換分担率を配分し、排熱利用効率を高めて空気調和装置全体の消費エネルギーを有効に低減することができる。   According to the present invention, the heat exchanger for heat recovery of the heat recovery machine arranged in the exhaust duct is incorporated in the refrigerant system of the outdoor unit, and functions as an evaporator or a condenser in the heat exchanger of the outdoor unit; Control the refrigerant circuit to achieve the same heat exchange action state, and adjust the opening of the electric expansion valve connected to the heat recovery heat exchanger according to the exhaust temperature to recover the heat exchanger and heat recovery of the outdoor unit It is possible to distribute the heat exchange share rate with the heat exchanger for use, increase the exhaust heat utilization efficiency, and effectively reduce the energy consumption of the entire air conditioner.

実施の形態１．
図1は、この発明を実施するための実施の形態１の冷暖同時型空気調和装置を用いた空調システムの概念図を示す。図1において、建物１の外部に室外機２が配置され、建物１における、例えば、事務室内に第1室内機３（室内機Ａ）、会議室内に第２室内機４（室内機Ｂ）が配置される。建物１の天井部に形成されたダクト６の一端に設けられた給気口（図示しない）の近くに給気ファン７が配置される。給気ファン７により、矢印８で示されるように、給気口から吸い込まれた新鮮な外気は、各部屋（事務室、会議室、作業室等）内に取り込まれ、各室内のＣＯ２濃度が一定値以下とされる。ダクト６の他端に設けられた排気口（図示しない）の近くに排気ファンを具備した排熱回収機１６が配置される。この排熱回収機１６は、本明細書において、単に熱回収機とも称する。排気ファンにより排気口（図示しない）に隣接して設けられた、例えば、便所の天井部から、前記事務室、会議室および便所の床部にそれぞれ設けられた連通孔を介して矢印１０で示されるように各部屋内の汚染空気が吸い出され、矢印９で示されるように建物１の外部に放出される。 Embodiment 1 FIG.
FIG. 1 shows a conceptual diagram of an air conditioning system using the cooling and heating simultaneous type air conditioning apparatus of Embodiment 1 for carrying out the present invention. In FIG. 1, an outdoor unit 2 is disposed outside the building 1. In the building 1, for example, a first indoor unit 3 (indoor unit A) is provided in an office room, and a second indoor unit 4 (indoor unit B) is provided in a conference room. Be placed. An air supply fan 7 is disposed near an air supply port (not shown) provided at one end of a duct 6 formed in the ceiling of the building 1. As shown by the arrow 8 by the air supply fan 7, fresh outside air sucked from the air supply port is taken into each room (office room, conference room, work room, etc.), and the CO 2 concentration in each room Is below a certain value. An exhaust heat recovery machine 16 having an exhaust fan is disposed near an exhaust port (not shown) provided at the other end of the duct 6. The exhaust heat recovery machine 16 is also simply referred to as a heat recovery machine in this specification. As indicated by an arrow 10, provided by an exhaust fan adjacent to an exhaust port (not shown), for example, from a ceiling portion of a toilet, through communication holes provided in the office room, the conference room, and the floor of the toilet, respectively. As shown by the arrow 9, the contaminated air in each room is sucked out and released to the outside of the building 1.

部屋の用途に応じて、外気の取り入れにより部屋の気圧を高めて汚染空気が他所から入らないようにするとか、排気ファンによる吸出しにより汚染空気が各部屋の天井部から漏出しないように各室内の気圧を低くし、適切な排気処理を施した後、建物１の外部に排気するように設計される。このようにして、新鮮な外気の取り入れおよび排気が常時実施される。   Depending on the usage of the room, increase the atmospheric pressure by taking in outside air to prevent contaminated air from entering from other places, or suck out by an exhaust fan so that the contaminated air does not leak from the ceiling of each room. It is designed to exhaust to the outside of the building 1 after lowering the atmospheric pressure and performing an appropriate exhaust treatment. In this way, fresh outside air intake and exhaust are always performed.

図１には、建物１における代表的に１つのダクト６の排気口の近くに設けた１つの排熱回収機１６（第１排熱回収機）のみが示されるが、建物１内で、例えば、他の２箇所にそれぞれ配置された排気ダクトの排気口（図示しない）の近くに、それぞれ、排熱回収機１６と同様の第２排熱回収機および第３排熱回収機（図１には、これらの図示を省略）が配置される。   FIG. 1 shows only one exhaust heat recovery machine 16 (first exhaust heat recovery machine) typically provided near the exhaust port of one duct 6 in the building 1. A second exhaust heat recovery machine and a third exhaust heat recovery machine (in FIG. 1) similar to the exhaust heat recovery machine 16, respectively, near the exhaust ports (not shown) of the exhaust ducts respectively disposed at the other two locations. Are omitted).

排熱回収機１６は、図２に示すように、ダクト６の排気口の近くに配置した送風機（排気ファン）１７と、白抜き太矢印で示すように送風機１７により取り込まれる排気流（空気流）の取り込み口部に配置された排気温度検知器（温度センサ）２１と、取り込まれた排気を受けて熱交換する熱回収用熱交換器１８とで構成される。   As shown in FIG. 2, the exhaust heat recovery machine 16 includes a blower (exhaust fan) 17 disposed near the exhaust port of the duct 6 and an exhaust flow (air flow) taken in by the blower 17 as indicated by a white thick arrow. ) And an exhaust temperature detector (temperature sensor) 21 disposed at the intake port, and a heat recovery heat exchanger 18 that receives the received exhaust and exchanges heat.

各排熱回収機１６は、建物１の天井裏に形成されたダクト６内に配置され、室外機２および各室内機（第１室内機４、第２室内機５、第３室内機６）と分離されているため、ダクト６を引き回す必要もなく、既存の通常の排気ダクト内に簡単に据付けることができる。また、当該空調システムのリニューアルにも容易に対応することができる。   Each exhaust heat recovery unit 16 is disposed in a duct 6 formed in the back of the ceiling of the building 1. The outdoor unit 2 and each indoor unit (first indoor unit 4, second indoor unit 5, third indoor unit 6). Therefore, the duct 6 does not need to be routed and can be easily installed in an existing normal exhaust duct. In addition, the air conditioning system can be easily renewed.

３つの第１排熱回収機１１、第２排熱回収機１２および第３排熱回収機１３（図４参照）と、３つの室内機、すなわち、第１室内機３、第２室内機４および建物１内の他の部屋、例えば、図示しない作業室に設けられた第３室内機５（図１には図示を省略する）とは、分流コントローラー１４及び配管１５を介して室外機２と接続され、詳細に後述する同一の冷媒系統、すなわち、同一の冷媒流体が流通する冷媒回路を構成する。建物１内の複数個所に配置した排熱回収機１６又は排気処理機をマルチ接続し、各箇所での小排気量をまとめることにより冷媒回路における排熱回収効果が有効に高められる。   Three first exhaust heat recovery units 11, a second exhaust heat recovery unit 12 and a third exhaust heat recovery unit 13 (see FIG. 4), and three indoor units, that is, a first indoor unit 3 and a second indoor unit 4 The third indoor unit 5 (not shown in FIG. 1) provided in another room in the building 1, for example, a work room (not shown) is connected to the outdoor unit 2 via the shunt controller 14 and the pipe 15. The same refrigerant system, which will be described in detail later, that is, a refrigerant circuit through which the same refrigerant fluid flows, is connected. By connecting multiple exhaust heat recovery units 16 or exhaust treatment units arranged at a plurality of locations in the building 1 and collecting the small exhaust amount at each location, the exhaust heat recovery effect in the refrigerant circuit is effectively enhanced.

図３は、室外機２と、３つの室内機、すなわち、第１室内機３、第２室内機４および第３室内機５並びに３つの排熱回収機１６（図３には、説明の簡略化のため、代表的に第１排熱回収機のみを示し、第２排熱回収機および第３排熱回収機の図示を省略）とを、分流コントローラー１４および配管１５を介して形成した冷媒回路を示す。図３において、室外機２は、圧縮機２４、アキュムレータ、四方弁２６、室外熱交換器２７、逆止弁２８及び送風機２９により構成される。室外機２における圧縮機２４は、詳細に後述するように、室外機制御器３０（図示しない）により圧縮作動容量が制御される。分流コントローラー１４は、気液分離器３１、３つの室内機（第１室内機３、第２室内機４および第３室内機６）および３つの排熱回収機１６のそれぞれに対応する三方弁３２並びに２つの電動膨張弁３３、３３により構成される。３つの室内機、すなわち、第１室内機３、第２室内機４および第３室内機５は、ともに、室内熱交換器３６、該室内熱交換器３６と接続された電動膨張弁３７および送風機３８により構成される。３つの排熱回収機１６は、ともに、送風機１７、熱回収用熱交換器１８及び該熱回収用熱交換器１８と接続した電動膨張弁１９により構成される。各熱回収用熱交換器１６は、蒸発器または凝縮器として機能する作動状態に応じて詳細に後述する熱回収制御器２０により電動膨張弁１９の開度が調節されて送出される冷媒温度が予め定めた所定値を維持するように制御される。   3 shows the outdoor unit 2 and three indoor units, that is, the first indoor unit 3, the second indoor unit 4, the third indoor unit 5, and the three exhaust heat recovery units 16 (the description is simplified in FIG. 3). For the sake of simplicity, only the first exhaust heat recovery machine is shown as a representative, and the second exhaust heat recovery machine and the third exhaust heat recovery machine are omitted) through the shunt controller 14 and the pipe 15. The circuit is shown. In FIG. 3, the outdoor unit 2 includes a compressor 24, an accumulator, a four-way valve 26, an outdoor heat exchanger 27, a check valve 28, and a blower 29. The compressor 24 in the outdoor unit 2 is controlled in compression operation capacity by an outdoor unit controller 30 (not shown), as will be described in detail later. The diversion controller 14 includes a three-way valve 32 corresponding to each of the gas-liquid separator 31, the three indoor units (the first indoor unit 3, the second indoor unit 4, and the third indoor unit 6) and the three exhaust heat recovery units 16. And two electric expansion valves 33 and 33. Three indoor units, that is, the first indoor unit 3, the second indoor unit 4, and the third indoor unit 5, are both an indoor heat exchanger 36, an electric expansion valve 37 connected to the indoor heat exchanger 36, and a blower. 38. The three exhaust heat recovery machines 16 are each composed of a blower 17, a heat recovery heat exchanger 18, and an electric expansion valve 19 connected to the heat recovery heat exchanger 18. Each of the heat recovery heat exchangers 16 has a refrigerant temperature that is sent out by adjusting the opening degree of the electric expansion valve 19 by a heat recovery controller 20 described later in detail according to an operating state that functions as an evaporator or a condenser. Control is performed so as to maintain a predetermined value.

以下に、図３に示される冷媒回路を構成する３つの排熱回収機（第１排熱回収機１１、第２排熱回収機１２および第３排熱回収機１３）の制御方法について説明する。なお、３つの第１排熱回収機１１、第２排熱回収機１２、第３排熱回収機１３は、それぞれ、排熱回収機Ａ、排熱回収機Ｂ、排熱回収機Ｃと略称し、３つの室内機（第１室内機３、第２室内機４、第３室内機５）は、それぞれ、室内機Ａ、室内機Ｂ、室内機Ｃと略称する。   Below, the control method of three waste heat recovery machines (the 1st waste heat recovery machine 11, the 2nd waste heat recovery machine 12, and the 3rd waste heat recovery machine 13) which constitute the refrigerant circuit shown in Drawing 3 is explained. . The three first exhaust heat recovery machines 11, the second exhaust heat recovery machine 12, and the third exhaust heat recovery machine 13 are abbreviated as an exhaust heat recovery machine A, an exhaust heat recovery machine B, and an exhaust heat recovery machine C, respectively. The three indoor units (first indoor unit 3, second indoor unit 4, and third indoor unit 5) are abbreviated as indoor unit A, indoor unit B, and indoor unit C, respectively.

いま、図４に示すように、３つの排熱回収機Ａ、排熱回収機Ｂ、排熱回収機Ｃ、３つの室内機Ａ、室内機Ｂ、室内機Ｃが室外機２と分流コントローラー１４を介して同一冷媒系統にマルチ接続され、これらの全ユニット（機器）が運転されるとする。各ユニットの熱交換能力として、例えば、表１に示すように、室内機Ａが４０％、室内機Ｂが３０％、室内機Ｃが３０％、排熱回収機Ａが２０％、排熱回収機Ｂが２０％、排熱回収機Ｃが２０％と設計されたとき、室外機２は、３つの排熱回収機Ａ、Ｂ、Ｃで不足する４０％の熱交換能力を補充するように制御される。３つの排熱回収機Ａ、Ｂ、Ｃのうち、何れも動作しない場合は、表２に示すように、室外機２は、１００％の熱交換能力となるように制御される。

表１

Figure 0005194517

表２
Figure 0005194517
Now, as shown in FIG. 4, the three exhaust heat recovery machines A, the exhaust heat recovery machine B, the exhaust heat recovery machine C, the three indoor units A, the indoor unit B, and the indoor unit C are the outdoor unit 2 and the shunt controller 14. It is assumed that all these units (equipment) are operated by multi-connection to the same refrigerant system via As the heat exchange capacity of each unit, for example, as shown in Table 1, indoor unit A is 40%, indoor unit B is 30%, indoor unit C is 30%, exhaust heat recovery machine A is 20%, exhaust heat recovery When the machine B is designed to be 20% and the exhaust heat recovery machine C is designed to be 20%, the outdoor unit 2 is replenished with the 40% heat exchange capacity that is lacking in the three exhaust heat recovery machines A, B, and C. Be controlled. When none of the three exhaust heat recovery machines A, B, and C operate, the outdoor unit 2 is controlled to have a heat exchange capacity of 100% as shown in Table 2.

Table 1
Figure 0005194517

Table 2
Figure 0005194517

室内機Ａ、Ｂ、Ｃのうち、例えば、室内機Ａのみを部分的に運転しているとき、表３に示すように、そのときの凝縮性能は排熱回収機Ａ、Ｂ、Ｃによりまかなえため、室外機２の熱交換能力は０％とされる。このとき、全ての排熱回収機Ａ、Ｂ、Ｃを運転する必要が無いため、排熱回収機Ａ、Ｂ、Ｃの運転台数が制御される。

表３

Figure 0005194517
Of the indoor units A, B, and C, for example, when only the indoor unit A is partially operated, the condensation performance at that time can be covered by the exhaust heat recovery units A, B, and C as shown in Table 3. Therefore, the heat exchange capacity of the outdoor unit 2 is set to 0%. At this time, since it is not necessary to operate all the exhaust heat recovery machines A, B, and C, the number of operating exhaust heat recovery machines A, B, and C is controlled.

Table 3
Figure 0005194517

室内機Ａ、Ｂ、Ｃが冷房運転され、したがって、室内熱交換器３６が蒸発器として作動している時、図５に示すように、少なくとも、室外機２の吸込温度、各排熱回収機１６の吸込温度ならびに圧縮機２４の高圧および低圧の情報に基づいて、室外機２における圧縮機２４の吐出圧力の飽和温度Ｔｃが一定となるように、室外機２の送風機２９および排熱回収機Ａ、Ｂ、Ｃの運転が制御される。このときの冷房能力を確保するため、図６に示すように、圧縮機２４の吸込圧力Ｔｅが予め定めた目標値Ｔｅｍに維持されるように制御される。   When the indoor units A, B, and C are in cooling operation, and therefore the indoor heat exchanger 36 is operating as an evaporator, as shown in FIG. 5, at least the suction temperature of the outdoor unit 2 and each exhaust heat recovery machine The blower 29 and the exhaust heat recovery machine of the outdoor unit 2 are set so that the saturation temperature Tc of the discharge pressure of the compressor 24 in the outdoor unit 2 is constant based on the suction temperature of 16 and the high and low pressure information of the compressor 24. The operation of A, B, and C is controlled. In order to ensure the cooling capacity at this time, as shown in FIG. 6, the suction pressure Te of the compressor 24 is controlled to be maintained at a predetermined target value Tem.

室内機３５（室内機Ａ、Ｂ、Ｃ）が冷房運転され、したがって、室内機３５の室内熱交換器３６が蒸発器として作用する状態とされるとき、室外機２の室外熱交換器２７が凝縮器として作用する状態とされ、排熱回収機１６（排熱回収機Ａ、Ｂ、Ｃ）の熱回収用熱交換器１８は凝縮器として作用する状態とされる。一方、室内機３５が暖房運転され、したがって、室内機３５の室内熱交換器３６が凝縮器として作用する状態とされるとき、室外機２の室外熱交換器２７が蒸発器として作用する状態とされ、排熱回収機１６の熱回収用熱交換器１８は凝縮器として作用する状態とされる。室外機２の室外熱交換器２７が蒸発器として作用する状態とされるとき、排熱回収機１６の熱回収用熱交換器１８は蒸発器として作用する状態とされる。   When the indoor unit 35 (indoor units A, B, and C) is in a cooling operation, and thus the indoor heat exchanger 36 of the indoor unit 35 is in a state of acting as an evaporator, the outdoor heat exchanger 27 of the outdoor unit 2 is It is set as the state which acts as a condenser, and the heat recovery heat exchanger 18 of the exhaust heat recovery machine 16 (exhaust heat recovery machines A, B, C) is set in a state where it functions as a condenser. On the other hand, when the indoor unit 35 is operated for heating, and therefore, the indoor heat exchanger 36 of the indoor unit 35 is in a state of acting as a condenser, the outdoor heat exchanger 27 of the outdoor unit 2 is in a state of acting as an evaporator. Thus, the heat recovery heat exchanger 18 of the exhaust heat recovery machine 16 is brought into a state of acting as a condenser. When the outdoor heat exchanger 27 of the outdoor unit 2 is in a state of acting as an evaporator, the heat recovery heat exchanger 18 of the exhaust heat recovery unit 16 is in a state of acting as an evaporator.

冷房運転時には、一般的に、室外空気の温度よりも室内排気の温度が低いため、排熱回収機１６において効率よく凝縮することができ、室外機２における凝縮性能は小さくて済むため、室外機２における送風機２９の駆動動力を有効に低減することができる。
一方、暖房運転時には、一般的に、室外空気の温度よりも室内排気の温度が高いため、排熱回収機１６において効率よく蒸発することができ、室外機２における蒸発性能は小さくて済むため、室外機２における送風機２９の駆動動力を有効に低減することができる。 During the cooling operation, the temperature of the indoor exhaust is generally lower than the temperature of the outdoor air, so that the exhaust heat recovery machine 16 can efficiently condense, and the outdoor unit 2 requires less condensing performance. The driving power of the blower 29 in 2 can be effectively reduced.
On the other hand, since the temperature of the indoor exhaust is generally higher than the temperature of the outdoor air during the heating operation, the exhaust heat recovery machine 16 can efficiently evaporate, and the evaporation performance in the outdoor unit 2 can be small. The driving power of the blower 29 in the outdoor unit 2 can be effectively reduced.

排熱回収機１６における送風機２９の駆動動力は、本来、排気する際に必要な動力であるため、排気の温度に依存することなく、熱回収用熱交換器１８で熱交換することで室外機２における送風機２９の送風動力を低減することができる。室外機２における送風機２９の送風動力の低減化により、室外機２における騒音低下の効果も奏功される。   Since the driving power of the blower 29 in the exhaust heat recovery machine 16 is originally necessary power for exhaust, the outdoor unit can be operated by exchanging heat with the heat recovery heat exchanger 18 without depending on the temperature of the exhaust. The blowing power of the blower 29 in 2 can be reduced. By reducing the blowing power of the blower 29 in the outdoor unit 2, the effect of reducing noise in the outdoor unit 2 is also effective.

室内機３５（室内機Ａ、Ｂ、Ｃ）は、リモートコントローラー（図示しない）等で運転操作するとき、送風機３８がＯＮ、室外機２の圧縮機２４がＯＮ、室内機３５の電動膨張弁３７が開とされるが、排熱回収機１６（排熱回収機Ａ、Ｂ、Ｃ）は、排気用送風機の制御が、当該空気調和装置の空調システムと独立しているため、排気用送風機１７（図２参照）がＯＮのときに、室内機３５などの操作により圧縮機２４がＯＮとなり、詳細に後述する室外機制御器３０および熱回収制御器２０（図１１参照）により、排熱回収機１６の運転が許可されたとき、排熱回収機１６の電動膨張弁１９が開（排熱回収機が運転）となる（図５参照）。   When the indoor unit 35 (indoor units A, B, C) is operated by a remote controller (not shown) or the like, the blower 38 is turned on, the compressor 24 of the outdoor unit 2 is turned on, and the electric expansion valve 37 of the indoor unit 35 However, since the exhaust heat recovery machine 16 (exhaust heat recovery machines A, B, C) is independent of the air conditioning system of the air conditioner, the exhaust fan 17 When ON (see FIG. 2) is ON, the compressor 24 is turned ON by operating the indoor unit 35 and the like, and exhaust heat recovery is performed by an outdoor unit controller 30 and a heat recovery controller 20 (see FIG. 11), which will be described in detail later. When the operation of the machine 16 is permitted, the electric expansion valve 19 of the exhaust heat recovery machine 16 is opened (the exhaust heat recovery machine is operating) (see FIG. 5).

排熱回収機１６の電動膨張弁１９は、当該排熱回収機１６に搭載された熱回収用熱交換器１８の配管温度に応じて制御される。具体的には、排熱回収機１６の熱回収用熱交換器１８が蒸発器として作用する状態にあるとき、熱交換器液側温度ＴＨ１と熱交換器ガス側温度ＴＨ２との差ＳＨ＝ＴＨ２−ＴＨ１が所定の値ＳＨｍに近づくように電動膨張弁１９の開度を調節する。ＳＨ＜ＳＨｍのとき、電動膨張弁１９の開度を小さくする一方、ＳＨ＞ＳＨｍのとき、電動膨張弁１９の開度を大きくする（図７参照）。ここで、ＳＨは蒸発器のスーパーヒートを意味する。   The electric expansion valve 19 of the exhaust heat recovery machine 16 is controlled according to the piping temperature of the heat recovery heat exchanger 18 mounted on the exhaust heat recovery machine 16. Specifically, when the heat recovery heat exchanger 18 of the exhaust heat recovery machine 16 is in a state of acting as an evaporator, the difference SH = TH2 between the heat exchanger liquid side temperature TH1 and the heat exchanger gas side temperature TH2. -Opening degree of the electric expansion valve 19 is adjusted so that TH1 approaches a predetermined value SHm. When SH <SHm, the opening degree of the electric expansion valve 19 is reduced. On the other hand, when SH> SHm, the opening degree of the electric expansion valve 19 is increased (see FIG. 7). Here, SH means superheat of the evaporator.

一方、排熱回収機１６の熱回収用熱交換器１８が凝縮器として作用する状態にあるときは、熱交換器液側温度ＴＨ１と室外機２から送信される高圧飽和温度Ｔｃとの差ＳＣ＝Ｔｃ−ＴＨ１が所定の値ＳＣｍに近づくように電動膨張弁１９の開度を調節する。ＳＣ＜ＳＣｍのとき、排熱回収機１６の電動膨張弁１９の開度を小さくする一方、ＳＣ＞ＳＣｍのとき、排熱回収機１６の電動膨張弁１９の開度を大きくする（図８参照）。ＳＣは凝縮器のサブクールを意味する。   On the other hand, when the heat recovery heat exchanger 18 of the exhaust heat recovery machine 16 is in a state of acting as a condenser, the difference SC between the heat exchanger liquid side temperature TH1 and the high pressure saturation temperature Tc transmitted from the outdoor unit 2 = Tc−TH1 is adjusted so that the opening degree of the electric expansion valve 19 approaches the predetermined value SCm. When SC <SCm, the opening degree of the electric expansion valve 19 of the exhaust heat recovery machine 16 is reduced, while when SC> SCm, the opening degree of the electric expansion valve 19 of the exhaust heat recovery machine 16 is increased (see FIG. 8). ). SC means the subcool of the condenser.

排熱回収機１６における電動膨張弁１９の制御は、他の室内機３５と同様にして行われ、各室内機３５（室内機Ａ、Ｂ、Ｃ）、排熱回収機１６の熱回収用熱交換器１８の出口の冷媒の状態、すなわち、蒸発器は予め定めたスーパーヒート目標値に、凝縮器は予め定めたサブクール目標値となるようになるように制御することにより、排熱回収機１６および室内機３５の複数台接続（マルチ接続）が容易とされる。   The control of the electric expansion valve 19 in the exhaust heat recovery machine 16 is performed in the same manner as the other indoor units 35, and the heat for heat recovery of each indoor unit 35 (indoor units A, B, C) and the exhaust heat recovery machine 16. The state of the refrigerant at the outlet of the exchanger 18, that is, the exhaust heat recovery machine 16 is controlled by controlling the evaporator to a predetermined superheat target value and the condenser to a predetermined subcool target value. In addition, a plurality of indoor units 35 can be easily connected (multi-connection).

室内機３５が冷房モードで運転されるとき、室外機２の室外熱交換器２７は凝縮器として作用する状態とされるが、室外機２の室外熱交換器２７が凝縮器として作用する状態にあるとき、排熱回収機１６も運転する場合、排熱回収機１６の熱回収用熱交換器１８も凝縮器として作用する状態とされる。これは、分流コントローラー１４により排熱回収機１６に供給する冷媒が凝縮器として作用する状態となるように制御される。   When the indoor unit 35 is operated in the cooling mode, the outdoor heat exchanger 27 of the outdoor unit 2 is in a state of acting as a condenser, but the outdoor heat exchanger 27 of the outdoor unit 2 is in a state of acting as a condenser. In some cases, when the exhaust heat recovery machine 16 is also operated, the heat recovery heat exchanger 18 of the exhaust heat recovery machine 16 also functions as a condenser. This is controlled by the shunt controller 14 so that the refrigerant supplied to the exhaust heat recovery machine 16 acts as a condenser.

排熱回収機１６が起動する、すなわち、電動膨張弁１９が開くとき、冷媒回路内の圧力が変動し、室内機３５の熱交換能力に影響する。その影響を小さくするために、排熱回収機１６の起動時、電動膨張弁１９の開度は予め定めた初期値に固定し、一定時間保持した後、上記ＳＨまたはＳＣに応じて電動膨張弁１９の開度を調節する。   When the exhaust heat recovery machine 16 is activated, that is, when the electric expansion valve 19 is opened, the pressure in the refrigerant circuit fluctuates and affects the heat exchange capability of the indoor unit 35. In order to reduce the influence, the opening degree of the electric expansion valve 19 is fixed to a predetermined initial value when the exhaust heat recovery machine 16 is started, and is held for a certain period of time, and then the electric expansion valve according to the SH or SC. Adjust the opening of 19.

また、室内機３５が暖房運転されるとき、室外機２の室外熱交換器２７に霜が付きにくくするため、排熱回収機１６の熱回収用熱交換器１８を主蒸発器として作用する状態として運転する。室内機３５が暖房モードで起動されるとき、室外機２の熱交換器２７は蒸発器として作用する状態とし、これと同時に、排熱回収機１６の熱回収用熱交換器１８も蒸発器として起動し、Ｔｅ制御に応じて停止する（図９参照）。このとき、蒸発温度が所定値となるように冷媒容量が制御されるが、排熱回収機１６の熱回収用熱交換器１８により冷媒が十分に蒸発されるときは、室外機２の送風機２９は停止される。除霜時、室内機３５の電動膨張弁３７を閉止し、室外機２の室外熱交換器２７を凝縮器として作用する状態とされ、排熱回収機１６の熱回収用熱交換器１８を蒸発器として作用する状態とすることにより、室内機３５の運転の快適性を損なわないようにされる。排熱回収機１６は、除霜時にも、送風機１７が常時駆動されているため、除霜能力の向上を図ることができる。   In addition, when the indoor unit 35 is operated for heating, the outdoor heat exchanger 27 of the outdoor unit 2 is less likely to be frosted, so that the heat recovery heat exchanger 18 of the exhaust heat recovery unit 16 acts as a main evaporator. Drive as. When the indoor unit 35 is activated in the heating mode, the heat exchanger 27 of the outdoor unit 2 functions as an evaporator, and at the same time, the heat recovery heat exchanger 18 of the exhaust heat recovery unit 16 also functions as an evaporator. It starts and stops according to Te control (see FIG. 9). At this time, the refrigerant capacity is controlled so that the evaporation temperature becomes a predetermined value. However, when the refrigerant is sufficiently evaporated by the heat recovery heat exchanger 18 of the exhaust heat recovery machine 16, the blower 29 of the outdoor unit 2 is used. Is stopped. At the time of defrosting, the electric expansion valve 37 of the indoor unit 35 is closed, and the outdoor heat exchanger 27 of the outdoor unit 2 acts as a condenser, and the heat recovery heat exchanger 18 of the exhaust heat recovery machine 16 is evaporated. By setting it as the state which acts as a container, it is made not to impair the operational comfort of the indoor unit 35. The exhaust heat recovery machine 16 can improve the defrosting capability because the blower 17 is always driven even during defrosting.

一方、排気に、室内の発熱負荷が加わる場合があり、室内機３５が冷房運転される時、排熱回収機１６の吸込温度が室外機２の吸込温度よりも高い場合がある。この場合、室外機２の室外熱交換器２７を凝縮器として作用させる方が熱交換効率は高いが、送風機２９の駆動動力の影響や、室外機２の騒音を低減するため、排熱回収機１６の熱回収用熱交換器１８を凝縮器として作用する状態にすることが必要となる。このとき、排気温度が高すぎる場合、益々高圧ガス圧力が上昇することなり、正常運転の維持ができなくなる。したがって、排気温度が高圧の飽和温度に対し予め定めた所定温度以上となるまでは、排熱回収機１６の熱回収用熱交換器１８を凝縮器として作用する状態とし、排気温度が所定温度を超えると、排熱回収機１６の電動膨張弁１９を閉止し、室外機２の室外熱交換器２７を主凝縮器として作用する運転状態とする（図５中、ステップ３（Ｓ３）の判別動作参照）。   On the other hand, an indoor heat generation load may be applied to the exhaust, and when the indoor unit 35 is cooled, the suction temperature of the exhaust heat recovery unit 16 may be higher than the suction temperature of the outdoor unit 2. In this case, the heat exchange efficiency is higher when the outdoor heat exchanger 27 of the outdoor unit 2 acts as a condenser. However, in order to reduce the influence of the driving power of the blower 29 and the noise of the outdoor unit 2, an exhaust heat recovery machine is used. It is necessary that the 16 heat recovery heat exchangers 18 function as condensers. At this time, if the exhaust gas temperature is too high, the high-pressure gas pressure will increase further, and normal operation cannot be maintained. Therefore, the heat recovery heat exchanger 18 of the exhaust heat recovery machine 16 is made to act as a condenser until the exhaust temperature becomes equal to or higher than a predetermined temperature with respect to the high-pressure saturation temperature, and the exhaust temperature reaches the predetermined temperature. If exceeded, the electric expansion valve 19 of the exhaust heat recovery machine 16 is closed, and the outdoor heat exchanger 27 of the outdoor unit 2 is put into an operating state in which it acts as a main condenser (in FIG. 5, step 3 (S3) discrimination operation). reference).

排熱回収機１６から室外機２への主熱交換作用（主凝縮器又は主蒸発器として作用する状態）の移行を急激に行うと圧力変動が大きく、熱交換能力に悪影響を及ぼすため、圧縮機２４の高圧の吐出圧力の飽和温度Ｔｃと排熱回収機１６の吸込温度Ｔｘとの差に応じて、排熱回収機１６の電動膨張弁１９の動作目標値であるＳＨｍ（スーパーヒート目標値）およびＳＣｍ（サブクール目標値）を変化させ、これにより、電動膨張弁１９の開度を変化させるようにする。冷房時および暖房時におけるＳＨｍ（スーパーヒート目標値）、ＳＣｍ（サブクール目標値）の一例を、それぞれ、表４、表５に示す。

表４

Figure 0005194517

表５
Figure 0005194517
When the transition of the main heat exchange action (the state acting as the main condenser or main evaporator) from the exhaust heat recovery machine 16 to the outdoor unit 2 is suddenly performed, the pressure fluctuation is large and the heat exchange capacity is adversely affected. According to the difference between the saturation temperature Tc of the high discharge pressure of the machine 24 and the suction temperature Tx of the exhaust heat recovery machine 16, the operation target value of the electric expansion valve 19 of the exhaust heat recovery machine 16 is SHm (superheat target value). ) And SCm (subcool target value) are changed, whereby the opening degree of the electric expansion valve 19 is changed. Tables 4 and 5 show examples of SHm (superheat target value) and SCm (subcool target value) during cooling and heating, respectively.

Table 4
Figure 0005194517

Table 5
Figure 0005194517

各排熱回収機１６（排熱回収機Ａ、Ｂ、Ｃ）の熱回収用熱交換器１８が蒸発器として作用する状態では、図１１に示すように、室外回収制御器２０は、排熱回収機１６の排気吸込口部に配置された吸込温度センサー２１、熱回収用熱交換器１８の蒸気側温度検出用のガス管温度センサー２２、熱回収用熱交換器１８の液側温度検出用の液管センサー２３および排気用送風機１７の運転信号を受けて熱回収用電動膨張弁１９に開度信号を送出するとともに室外機２の圧縮機２４の作動容量指令を送出しかつ分流コントローラー制御器４０に対し分流コントローラー１４の三方弁（切り換え弁）３２および電動膨張弁３３に作動指令を送出し、熱回収用熱交換器１８が予め定めたスーパーヒート目標値を維持するように制御する一方、熱回収用熱交換器１８が凝縮器として作用する状態では、予め定めたサブクール目標値を維持するように制御する。室外制御器２０は、熱回収用制御器３０から室外機２の圧縮機２４の作動指令を受けて、圧縮機２４の吸入圧力の飽和温度または吐出圧力の飽和温度が所定値となるように作動容量を制御する。   In the state where the heat recovery heat exchanger 18 of each exhaust heat recovery machine 16 (exhaust heat recovery machine A, B, C) acts as an evaporator, as shown in FIG. A suction temperature sensor 21 disposed at an exhaust suction port of the recovery machine 16, a gas pipe temperature sensor 22 for detecting a steam side temperature of the heat recovery heat exchanger 18, and a liquid side temperature detection of the heat recovery heat exchanger 18 In response to the operation signals of the liquid pipe sensor 23 and the exhaust fan 17, an opening degree signal is sent to the heat recovery electric expansion valve 19, an operating capacity command of the compressor 24 of the outdoor unit 2 is sent, and a shunt controller controller 40, an operation command is sent to the three-way valve (switching valve) 32 and the electric expansion valve 33 of the flow dividing controller 14, and the heat recovery heat exchanger 18 is controlled to maintain a predetermined superheat target value. Heat recovery heat Exchanger 18 is in a state which acts as a condenser, is controlled to maintain a predetermined subcooling target value. The outdoor controller 20 receives an operation command for the compressor 24 of the outdoor unit 2 from the heat recovery controller 30 and operates so that the saturation temperature of the suction pressure or the saturation temperature of the discharge pressure of the compressor 24 becomes a predetermined value. Control the capacity.

排気には、用途により腐食性ガスが含まれる場合がある。一般的な建物では、排気は便所から行われるが、アンモニアや硫化水素成分等により熱交換器のアルミや銅材料が腐食する恐れがある。また、工場排気においても酸性ガス等の腐食性ガスが含まれる場合がある。そのため、特に、排熱回収機１６の熱回収用熱交換器１８には、エポキシ樹脂を電着塗装し、耐腐食性を高めるようにする。   Exhaust gas may contain corrosive gas depending on the application. In a general building, exhaust is performed from a toilet, but there is a risk that the aluminum or copper material of the heat exchanger may be corroded by ammonia or hydrogen sulfide components. In addition, corrosive gas such as acidic gas may be contained in factory exhaust. Therefore, in particular, the heat recovery heat exchanger 18 of the exhaust heat recovery machine 16 is electrodeposited with an epoxy resin so as to enhance the corrosion resistance.

実施の形態２．
排熱回収機１６と室内空調用の室内機３５との併用は、室内機３５が停止しているときには有効活用ができない。一方、図１２に示すように、外気処理機４６は、室内機３５と同様、外気処理用熱交換器４７と電動膨張弁４８と送風機４９を備え、常時運転されることに着目し、排熱回収機１６と併用することで有効活用を実現したものである。図１２の空気調和装置は、図１（実施の形態１）のものと比べ、吸気ファン７に代えて外気処理機４６が配置され、冷暖同時型室外機２に代えて圧縮機４２、アキュムレーター４３、四方弁４４により構成される熱源機４１（図１３参照）が配置された点が異なり、その他の構成部分は等価なものであり、同一の数字符号を付して説明を省略する。図１２の空気調和装置において、外気処理機４６の熱交換器４７と排熱回収機（以下に、排気処理機ともいう）５１の熱回収用熱交換器５３は、互いに相異なる蒸発器または凝縮器として機能する状態とされる。すなわち、外気処理機４６の外気処理用熱交換器４７が凝縮器として機能する状態のときは、排気処理機５１の熱回収用熱交換器５３は蒸発器として機能する状態とされるようにする。外気処理機４６は、新鮮空気を取り入れるとか、室内を陽圧にするために、常時送風機４９を運転する必要があるが、除霜時は、冷風防止とか、外気処理機４６に搭載された加湿器の凍結防止のため、送風機４９を一時停止させる必要がある。そこで、排気処理機５１に蒸発性能を充足する熱交換器を設ける一方、排気処理機４６に電動膨張弁４８を設け、外気処理機４６の容量制御に応じて排気処理用熱交換器の熱交換容量を変化させる。 Embodiment 2. FIG.
The combined use of the exhaust heat recovery machine 16 and the indoor unit 35 for indoor air conditioning cannot be effectively used when the indoor unit 35 is stopped. On the other hand, as shown in FIG. 12, the outside air processing unit 46 is provided with an outside air processing heat exchanger 47, an electric expansion valve 48, and a blower 49 as in the case of the indoor unit 35. Effective use is realized by using it together with the recovery machine 16. The air conditioner of FIG. 12 is different from that of FIG. 1 (Embodiment 1) in that an outside air processing unit 46 is arranged instead of the intake fan 7, and a compressor 42 and an accumulator are substituted for the cooling / heating simultaneous type outdoor unit 2. 43 and the heat source machine 41 (refer FIG. 13) comprised by the four-way valve 44 differs, and other components are equivalent and attach | subject the same numerical code | symbol and abbreviate | omit description. In the air conditioner of FIG. 12, the heat exchanger 47 of the outside air processor 46 and the heat exchanger for heat recovery 53 of the exhaust heat recovery machine (hereinafter also referred to as exhaust treatment machine) 51 are different from each other in evaporator or condensation. It is assumed that it functions as a container. That is, when the outside air processing heat exchanger 47 of the outside air processing unit 46 functions as a condenser, the heat recovery heat exchanger 53 of the exhaust processing unit 51 is configured to function as an evaporator. . The outside air processing unit 46 needs to operate the blower 49 at all times in order to take in fresh air or to make the room have a positive pressure. It is necessary to temporarily stop the blower 49 in order to prevent freezing of the fan. Therefore, the exhaust treatment device 51 is provided with a heat exchanger that satisfies the evaporation performance, while the exhaust treatment device 46 is provided with an electric expansion valve 48, and the heat exchange of the exhaust treatment heat exchanger is performed according to the capacity control of the outside air treatment device 46. Change the capacity.

実施の形態２の空気調和装置における排熱回収機５１は、図１３に示すように、熱源機４１と、３つの二方弁（切り換え弁）５２、３つの熱回収用熱交換器５３（第１熱回収用熱交換器Ａ、第２熱回収用熱交換器Ｂ、第３熱回収用熱交換器Ｃ）および送風機５４により構成される。外気処理機４６が冷房運転、したがって、外気処理用熱交換器４７が蒸発器として機能する状態とされるとき、圧縮機４２の吐出圧力の飽和温度Ｔｃに応じて二方弁５２を切り換え制御され、排熱回収機５１の３つの熱回収用熱交換器５３（熱回収用熱交換器Ａ、Ｂ、Ｃ）による熱交換能力が７段階に切り替え可能とされる。   As shown in FIG. 13, the exhaust heat recovery machine 51 in the air conditioner of Embodiment 2 includes a heat source unit 41, three two-way valves (switching valves) 52, and three heat recovery heat exchangers 53 (first 1 heat recovery heat exchanger A, second heat recovery heat exchanger B, third heat recovery heat exchanger C) and blower 54. When the outside air processor 46 is in a cooling operation, and thus the outside air processing heat exchanger 47 is in a state of functioning as an evaporator, the two-way valve 52 is switched and controlled in accordance with the saturation temperature Tc of the discharge pressure of the compressor 42. The heat exchange capability of the three heat recovery heat exchangers 53 (heat recovery heat exchangers A, B, and C) of the exhaust heat recovery machine 51 can be switched to seven stages.

熱源機４１と排熱回収機５１とは、図１３に示すように、分離された形態のもの（分離型）であっても、図１５に示すように、一体化された形態のもの（一体型）であっても、同様の熱回収効果を得ることができる。分離型および一体型の何れにおいても排気のための送風機５４の風量は、排気により決定されるため、熱交換作動容量は複合熱回収用熱交換器（Ａ、Ｂ、Ｃ）５３の作動切り替えにより制御される。   As shown in FIG. 13, the heat source device 41 and the exhaust heat recovery device 51 are separated (one type) as shown in FIG. The same heat recovery effect can be obtained even with the body shape. In both the separated type and the integrated type, the air volume of the blower 54 for exhaust is determined by the exhaust, so that the heat exchange operating capacity is changed by switching the operation of the heat exchanger (A, B, C) 53 for combined heat recovery. Be controlled.

実施の形態２の空気調和装置においては、外気処理機４６の他に、図１６（分離型）、図１７（一体型）にそれぞれ示すように、室内機３５と複合またはマルチ接続したものであってもよい。   In the air conditioner of the second embodiment, in addition to the outside air processor 46, as shown in FIG. 16 (separate type) and FIG. 17 (integrated type), the indoor unit 35 is combined or multi-connected. May be.

また、熱源機４１と、３つの室内機３５（第１室内機３、第２室内機４、第３室内機５）および排熱回収機５６とは、図１８に示すように、３つの室内機３、４、５および排熱回収機５６にそれぞれ対応する三方弁（切り換え弁）３２を介して冷暖同時型冷媒回路を構成することができる。   Further, the heat source unit 41, the three indoor units 35 (the first indoor unit 3, the second indoor unit 4, the third indoor unit 5) and the exhaust heat recovery unit 56 include three indoor units as shown in FIG. A cooling / heating simultaneous type refrigerant circuit can be configured through three-way valves (switching valves) 32 corresponding to the machines 3, 4, 5 and the exhaust heat recovery machine 56, respectively.

実施の形態３．
排気から排熱回収する、すなわち、熱再利用するものに限らず、図１９に示すように、排水管（排水回路）５９から排熱回収することができる。図１９の空気調和装置は、図１（実施の形態１）のものと比べ、排気から排熱回収する排熱回収機１６に代えて、排水回路５６から排熱回収する、実施の形態２の空気調和装置における排熱回収機５５と実質的に同様の排熱回収機５６が配置され点が異なり、その他の構成部分は等価なものであり、同一の数字符号を付して説明を省略する。 Embodiment 3 FIG.
The exhaust heat is recovered from the exhaust gas, that is, the heat is reused, and the exhaust heat can be recovered from the drain pipe (drain circuit) 59 as shown in FIG. The air conditioner of FIG. 19 is different from that of FIG. 1 (Embodiment 1) in that the exhaust heat is recovered from the drain circuit 56 instead of the exhaust heat recovery machine 16 that recovers exhaust heat from the exhaust. An exhaust heat recovery machine 56 that is substantially the same as the exhaust heat recovery machine 55 in the air conditioner is different in that the other components are equivalent, and the description is omitted with the same reference numerals. .

排熱回収機５６は、図２０に示すように、熱回収用熱交換器５７と、電動膨張弁５８と、二重管チューブとかプレートフィンチチューブ等を用いて形成される排水管５９とにより構成される。３つの室内機３５（第１室内機３、第２室内機４、第３室内機５）と排熱回収機５６とは、分流コントローラー１４および配管１５を介して室外機２と同一の冷媒系統（冷媒回路）が形成される。この構成により、排気からの排熱回収と併用することができる。   As shown in FIG. 20, the exhaust heat recovery machine 56 includes a heat recovery heat exchanger 57, an electric expansion valve 58, and a drain pipe 59 formed using a double pipe tube, a plate finch tube, or the like. Is done. The three indoor units 35 (the first indoor unit 3, the second indoor unit 4, the third indoor unit 5) and the exhaust heat recovery unit 56 are the same refrigerant system as the outdoor unit 2 through the flow dividing controller 14 and the pipe 15. (Refrigerant circuit) is formed. With this configuration, it can be used in combination with exhaust heat recovery from the exhaust.

冷暖同時型空気調和装置における室外機２と、外気処理機と排熱回収機とが一体化された排熱回収給排気ユニット６１とを用いて、図２１に示すように、排熱回収用空調システムを構成することができる。更に、図２２に示すように、全熱交換器と組み合わせた排熱回収給排気ユニット６３を用いて排熱回収用空調システムを構成することができる。   As shown in FIG. 21, exhaust heat recovery air conditioning is performed using the outdoor unit 2 and the exhaust heat recovery supply / exhaust unit 61 in which the outdoor air processing unit and the exhaust heat recovery unit are integrated in the cooling and heating simultaneous air conditioner. The system can be configured. Furthermore, as shown in FIG. 22, an exhaust heat recovery air conditioning system can be configured using an exhaust heat recovery supply / exhaust unit 63 combined with a total heat exchanger.

本発明の実施の形態１の空気調和装置の概略図である。It is the schematic of the air conditioning apparatus of Embodiment 1 of this invention. 図１の空気調和装置に用いることができる排熱回収機の概略図である。It is the schematic of the waste heat recovery machine which can be used for the air conditioning apparatus of FIG. 本発明の実施の形態１の冷暖同時型空気調和装置の冷媒回路図である。It is a refrigerant circuit figure of the heating-and-cooling simultaneous type air harmony device of Embodiment 1 of the present invention. 前記冷暖同時型空気調和装置における冷媒配管接続図である。It is a refrigerant | coolant piping connection diagram in the said heating / cooling simultaneous type air conditioning apparatus. 前記冷暖同時型空気調和装置の冷房時の圧縮機吐出圧力制御流れ図である。It is a compressor discharge pressure control flow chart at the time of air_conditioning | cooling of the said heating / cooling simultaneous type air conditioning apparatus. 前記冷暖同時型空気調和装置の冷房時の圧縮機吸込圧力制御流れ図である。It is a flowchart of the compressor suction pressure control at the time of air_conditioning | cooling of the said cooling / heating simultaneous type air conditioning apparatus. 前記冷暖同時型空気調和装置の蒸発器のスーパーヒート制御流れ図である。It is a superheat control flowchart of the evaporator of the said heating-cooling simultaneous type | formula air conditioning apparatus. 前記冷暖同時型空気調和装置の凝縮器のサブクール制御流れ図である。It is a subcool control flowchart of the condenser of the said heating and cooling simultaneous type air conditioning apparatus. 前記冷暖同時型空気調和装置の暖房時の圧縮機吸込圧力制御流れ図である。It is a flowchart of the compressor suction pressure control at the time of the heating of the said heating / cooling simultaneous type air conditioning apparatus. 前記冷暖同時型空気調和装置の暖房時の圧縮機吐出圧力制御流れ図である。It is a compressor discharge pressure control flow chart at the time of heating of the above-mentioned cooling and heating simultaneous type air harmony device. 前記冷暖同時型空気調和装置の排熱回収機における信号流れ線図である。It is a signal flow diagram in an exhaust heat recovery machine of the above-mentioned cooling and heating simultaneous type air harmony device. 本発明の実施の形態２の空気調和装置の概略図である。It is the schematic of the air conditioning apparatus of Embodiment 2 of this invention. 外気処理機と併用した熱源機分離型空気調和装置の冷媒配管接続図である。It is a refrigerant piping connection diagram of a heat source unit separation type air harmony device used together with an outside air processing machine. 前記熱源機分離型空気調和装置の冷房時の圧縮機吐出圧力制御流れ図である。It is a compressor discharge pressure control flow chart at the time of cooling of the heat source unit separation type air harmony device. 外気処理機と併用した熱源機一体型空気調和装置の冷媒配管接続図である。It is a refrigerant piping connection diagram of a heat source unit integrated air conditioner used in combination with an outside air processing unit. 外気処理機および室内機を併用した熱源機分離型空気調和装置の冷媒配管接続図である。It is a refrigerant piping connection diagram of a heat source unit separation type air harmony device which used an outside air processing machine and an indoor unit together. 外気処理機および室内機を併用した熱源機一体型空気調和装置の冷媒配管接続図である。It is a refrigerant piping connection diagram of a heat source unit integrated air conditioner using both an outside air processing unit and an indoor unit. 排熱回収機および室内機を併用した冷暖同時型空気調和装置の冷媒配管接続図である。It is a refrigerant piping connection diagram of a cooling and heating simultaneous type air conditioner using an exhaust heat recovery machine and an indoor unit together. 排水からの排熱回収機を備えた空気調和装置の概略図である。It is the schematic of the air conditioning apparatus provided with the waste heat recovery machine from waste_water | drain. 排水からの排熱回収機と排水回路との冷媒回路図である。It is a refrigerant circuit diagram of a waste heat recovery machine from waste water and a drain circuit. 外気処理機と排熱回収機とを一体化した冷暖同時型空気調和装置の概略図である。It is the schematic of the heating / cooling simultaneous type | formula air conditioning apparatus which integrated the outside air processing machine and the exhaust heat recovery machine. 外気処理機と排熱回収機と全熱交換器とを併用した冷暖同時型空気調和装置の概略図である。It is the schematic of the cooling-heating simultaneous type | formula air conditioning apparatus which used together an external air processing machine, a waste heat recovery machine, and a total heat exchanger.

符号の説明Explanation of symbols

２ 室外機
３ 第１室内機（Ａ）
４ 第２室内機（Ｂ）
５ 第３室内機（Ｃ）
６ ダクト
１１ 第１排熱回収機（Ａ）
１２ 第２排熱回収機（Ｂ）
１３ 第３排熱回収機（Ｃ）
１４ 分流コントローラー
１５ 配管
１６ 排熱回収機
１７ 送風機
１８ 熱回収用熱交換器
１９ 電動膨張弁
２０ 熱回収制御器
２４ 圧縮機
２５ アキュムレーター
２６ 四方弁
２７ 室外熱交換器
２８ 逆止弁
３０ 室外制御器
３５ 室内機
４０ 分流コントローラー制御器
４６ 外気処理機
５１ 排熱回収機
５５ 排熱回収機
５７ 熱回収用熱交換器 2 Outdoor unit 3 First indoor unit (A)
4 Second indoor unit (B)
5 Third indoor unit (C)
6 Duct 11 First exhaust heat recovery machine (A)
12 Second exhaust heat recovery machine (B)
13 Third exhaust heat recovery machine (C)
14 Split flow controller 15 Piping 16 Waste heat recovery machine 17 Blower 18 Heat recovery heat exchanger 19 Electric expansion valve 20 Heat recovery controller 24 Compressor 25 Accumulator 26 Four-way valve 27 Outdoor heat exchanger 28 Check valve 30 Outdoor controller 35 Indoor unit 40 Shunt controller controller 46 Outside air processor 51 Waste heat recovery machine 55 Waste heat recovery machine 57 Heat exchanger for heat recovery

Claims (5)

圧縮機、四方弁及び室外熱交換器を搭載した室外機と、電動膨張弁及び室内熱交換器を搭載した室内機と、熱回収用熱交換器及び電動膨張弁を搭載して排気ダクトに配置された熱回収機とにより構成された空気調和装置において、
前記熱回収用熱交換器が蒸発器として作用するときは予め定めたスーパーヒート目標値を維持する一方、凝縮器として作用するときは予め定めたサブクール目標値を維持するように熱回収用電動膨張弁を制御する熱回収制御装置と、前記圧縮機における吸入圧力の飽和温度または吐出圧力の飽和温度が所定値となるように前記圧縮機の容量を制御する室外制御装置とを備え、
前記室内機が暖房運転中に前記室外機が除霜運転を行うとき、前記室内機の前記電動膨張弁を閉止して、前記熱回収用熱交換器を蒸発器として作用させることを特徴とする空気調和装置。 An outdoor unit equipped with a compressor, a four-way valve and an outdoor heat exchanger, an indoor unit equipped with an electric expansion valve and an indoor heat exchanger, a heat recovery heat exchanger and an electric expansion valve, and placed in the exhaust duct In the air conditioner configured by the heat recovery machine,
When the heat recovery heat exchanger acts as an evaporator, a predetermined superheat target value is maintained, whereas when the heat recovery heat exchanger acts as a condenser, a heat recovery electric expansion is maintained so as to maintain a predetermined subcool target value. A heat recovery control device that controls the valve, and an outdoor control device that controls the capacity of the compressor so that the saturation temperature of the suction pressure or the saturation temperature of the discharge pressure in the compressor becomes a predetermined value,
When the outdoor unit performs a defrosting operation while the indoor unit is in a heating operation, the electric expansion valve of the indoor unit is closed and the heat recovery heat exchanger functions as an evaporator. Air conditioner. 熱回収用熱交換器を通過する冷媒流体の一次側温度に応じてスーパーヒートまたはサブクール目標値を変更することを特徴とする請求項１に記載の空気調和装置。 The air conditioning apparatus according to claim 1, wherein the superheat or subcool target value is changed according to a primary temperature of the refrigerant fluid passing through the heat recovery heat exchanger. 室内機の室内熱交換器と熱回収機の熱回収用熱交換器とが各熱交換器と接続した三方弁を介して蒸発器または凝縮器として機能する状態に切り替え可能とし、前記室内機と前記熱回収機とは互いに異なる蒸発器または凝縮器として機能する状態に切り換える制御装置を備えたことを特徴とする請求項１または請求項２に記載の空気調和装置。 The indoor heat exchanger of the indoor unit and the heat exchanger for heat recovery of the heat recovery unit can be switched to a state of functioning as an evaporator or a condenser via a three-way valve connected to each heat exchanger, The air conditioner according to claim 1 or 2, further comprising a control device that switches to a state that functions as an evaporator or a condenser different from the heat recovery machine. 室内機が外気処理機として作用することを特徴とする請求項１または請求項２または請求項３に記載の空気調和装置。 The air conditioner according to claim 1, 2 or 3, wherein the indoor unit acts as an outside air processing unit. 室外機が複数の室外熱交換器にそれぞれ電磁弁を接続して構成した熱交換器を含み、冷房運転時には前記室外機の圧縮機における吐出圧力の飽和温度にて、暖房運転時には前記室外機の圧縮機における吸入圧力の飽和温度にて前記各室外熱交換器の容量を制御することを特徴とする請求項４に記載の空気調和装置。 The outdoor unit includes a heat exchanger configured by connecting solenoid valves to a plurality of outdoor heat exchangers, respectively, at the saturation temperature of the discharge pressure in the compressor of the outdoor unit during cooling operation, and of the outdoor unit during heating operation The air conditioner according to claim 4, wherein the capacity of each outdoor heat exchanger is controlled by a saturation temperature of the suction pressure in the compressor.
JP2007092436A 2007-03-30 2007-03-30 Air conditioner Expired - Fee Related JP5194517B2 (en)

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Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009250593A (en) * 2008-04-11 2009-10-29 Sumitomo Forestry Co Ltd Heat pump system for residence in cold area
JP2010266191A (en) * 2009-04-16 2010-11-25 Chubu Electric Power Co Inc Medium temperature regulating system
JP5424705B2 (en) * 2009-05-01 2014-02-26 三菱電機株式会社 Refrigeration air conditioner
JP5877632B2 (en) * 2010-06-07 2016-03-08 三菱電機株式会社 Air conditioner
JP2012202627A (en) * 2011-03-25 2012-10-22 Sanki Eng Co Ltd Waste heat recovery air conditioning system
JP5988646B2 (en) * 2012-03-28 2016-09-07 三菱電機株式会社 Three-way valve and air conditioner equipped with the three-way valve
JP5939082B2 (en) * 2012-08-09 2016-06-22 ダイキン工業株式会社 Operation method of heat pump type air conditioner
US9879893B2 (en) 2014-01-21 2018-01-30 GD Midea Heating & Venting Equipment Co., Ltd. Air conditioning system, method for controlling air conditioning system, and outdoor apparatus of air conditioning system
CN104791946B (en) * 2014-01-21 2018-06-05 广东美的暖通设备有限公司 Air-conditioning system and its control method, the outdoor unit of air-conditioning system
CN104791943B (en) * 2014-01-21 2017-08-29 广东美的暖通设备有限公司 Air-conditioning system and its control method, the outdoor unit of air-conditioning system
CN108731293B (en) * 2017-04-18 2021-01-05 青岛海尔新能源电器有限公司 Heat pump unit electronic expansion valve control method and heat pump water heater
CN108759029B (en) * 2018-06-19 2020-11-03 安徽美芝精密制造有限公司 Air conditioning system, control method of air conditioning system and air conditioner
JP7433409B2 (en) * 2020-02-17 2024-02-19 三菱電機株式会社 Refrigeration cycle equipment
CN111550904B (en) * 2020-04-13 2021-10-15 宁波奥克斯电气股份有限公司 Electronic expansion valve control method and device and air conditioner
CN113685969B (en) * 2021-07-26 2023-03-21 重庆海尔空调器有限公司 Method and device for controlling defrosting of air conditioner and air conditioner
CN114893902B (en) * 2022-04-25 2023-09-19 青岛海信日立空调系统有限公司 Air conditioning system and control method thereof
CN114838420B (en) * 2022-05-07 2023-09-29 青岛海信日立空调系统有限公司 Fresh air humidifying device
CN114791151B (en) * 2022-05-16 2023-11-24 美的集团武汉暖通设备有限公司 Control method and device for electronic expansion valve of air conditioner, air conditioner and storage medium

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0320573A (en) * 1989-06-19 1991-01-29 Sanyo Electric Co Ltd Air-conditioning apparatus
JPH03260563A (en) * 1990-03-12 1991-11-20 Sanyo Electric Co Ltd Air conditioner
JP2753177B2 (en) * 1992-04-30 1998-05-18 松下精工株式会社 Heat recovery type multi air conditioner
JPH0996469A (en) * 1995-09-29 1997-04-08 Daikin Ind Ltd Air conditioner
JP4396521B2 (en) * 2002-10-30 2010-01-13 三菱電機株式会社 Air conditioner

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