JP4016988B2 - Air heat source heat pump air conditioner for agricultural industry - Google Patents

Air heat source heat pump air conditioner for agricultural industry Download PDF

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JP4016988B2
JP4016988B2 JP2005014839A JP2005014839A JP4016988B2 JP 4016988 B2 JP4016988 B2 JP 4016988B2 JP 2005014839 A JP2005014839 A JP 2005014839A JP 2005014839 A JP2005014839 A JP 2005014839A JP 4016988 B2 JP4016988 B2 JP 4016988B2
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満津雄 森田
暢夫 浦田
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木村工機株式会社
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本発明は栽培室や倉庫、工場など農産業用の空気熱源ヒートポンプ式空調機に関するものである。   The present invention relates to an air heat source heat pump type air conditioner for agricultural industries such as cultivation rooms, warehouses and factories.

還気循環空調、換気しながらの空調、換気のみによる外気冷房または外気暖房、の各種パターンの運転に切換自在な空気熱源の一体型ヒートポンプ式空調機として特開2002−147791号のものがある。この空調機は給気側冷媒−空気熱交換器と熱源側冷媒−空気熱交換器へ送られる外気と還気をダンパにて風量制御し各種パターンの運転に切換えするものであるが、どのパターンの運転でも必ず熱源側冷媒−空気熱交換器を還気や外気が通過する構造となっている。   Japanese Patent Application Laid-Open No. 2002-147791 discloses an integrated heat pump air conditioner of an air heat source that can be switched to various patterns of operation such as return air circulation air conditioning, air conditioning while ventilating, outside air cooling or outside air heating only by ventilation. In this air conditioner, the outside air and return air sent to the air supply side refrigerant-air heat exchanger and the heat source side refrigerant-air heat exchanger are controlled by a damper to switch the operation to various patterns. In this operation, the return air and the outside air always pass through the heat source side refrigerant-air heat exchanger.

特開2002−147791号公報JP 2002-147791 A

このような構造の空調機を、24時間空調を行う促成栽培などに使用した場合、一日の気候変化に関係なく、栽培室内の温湿度を一日に何回も人工的に変化させる必要があるため、ヒートポンプを動かさずに換気のみによる外気冷房または外気暖房を行う回数と時間が必然的に多くなる。ところが、換気の際にも通過する必要のない空気抵抗の大きな熱源側冷媒−空気熱交換器に必ず還気が通るため、送風機に負荷がかかり動力費がかさむ問題がある。また、この空調機は、ケーシングと被空調空間をダクトでつなぎ給排気等をしているため、ダクト施工の分、設備コスト高となる問題がある。さらに、ケーシングが横長のため広い設置面積が必要となり、その分もコストが高くなる。そこで、ダクト無しで容易に設置できてコンパクトで、設備コストがかからず、温度ムラがなく、メンテナンスと風量制御が容易で、熱回収ができ低騒音な空調機を提供する。   When the air conditioner with such a structure is used for forced cultivation that performs air conditioning for 24 hours, it is necessary to artificially change the temperature and humidity in the cultivation room several times a day regardless of the daily climate change. Therefore, the number and time of performing outdoor air cooling or outdoor air heating only by ventilation without moving the heat pump inevitably increases. However, since return air always passes through the heat source side refrigerant-air heat exchanger having a large air resistance that does not need to pass even during ventilation, there is a problem that a load is applied to the blower and the power cost is increased. In addition, since this air conditioner connects the casing and the air-conditioned space with a duct to supply and exhaust air, etc., there is a problem that the equipment cost increases due to the construction of the duct. Furthermore, since the casing is horizontally long, a large installation area is required, which increases the cost. Therefore, an air conditioner that can be easily installed without a duct, is compact, does not incur equipment costs, has no temperature unevenness, is easy to maintain and controls the air flow, can recover heat, and is low in noise is provided.

本発明は、上記課題を解決するため、ケーシングを正面・背面方向に扁平状に形成し、このケーシングの正面側上端部に給気口を、背面側上端部に排気口を、各々形成すると共に、前記ケーシングの正面側下端部に還気取入口を形成し、かつ前記ケーシングの一側面下端部に第1外気取入口を、他側面下端部に第2外気取入口を、各々形成し、前記給気口と前記還気取入口と前記第1外気取入口に各々連通する給気側送風路と、前記排気口と前記還気取入口と前記第2外気取入口とに各々連通する熱源側送風路と、を前記ケーシング内に並列に立設し、給気側冷媒−空気熱交換器を前記給気側送風路に設け、熱源側冷媒−空気熱交換器と熱源側送風機とを前記熱源側送風路に設け、前記熱源側冷媒−空気熱交換器の風上側であって前記第2外気取入口と前記熱源側冷媒−空気熱交換器との間に配置されて前記還気取入口から前記熱源側冷媒−空気熱交換器への還気風量を制御する第2還気ダンパと、前記熱源側冷媒−空気熱交換器の風下側であって前記熱源側冷媒−空気熱交換器と前記熱源側送風機との間に配置されて前記熱源側冷媒−空気熱交換器をバイパスさせると共に前記還気取入口から前記排気口への還気風量を制御する第3還気ダンパと、を設けたことを最も主要な特徴とする。   In order to solve the above-mentioned problems, the present invention forms a casing in a flat shape in the front and back directions, and forms an air inlet at the front upper end of the casing and an exhaust outlet at the upper upper end of the casing. Forming a return air intake at the lower end of the front side of the casing, forming a first outside air intake at the lower end of one side of the casing, and forming a second outside air intake at the lower end of the other side, A heat source side communicating with the air supply side, the return air intake port, and the first outside air intake port, respectively, and an exhaust port, the return air intake port, and the second outside air intake port. And an air supply side refrigerant-air heat exchanger provided in the air supply side air passage, and a heat source side refrigerant-air heat exchanger and a heat source side air blower are connected to the heat source. Provided in the side air passage, on the windward side of the heat source side refrigerant-air heat exchanger, the second outside A second return air damper disposed between the intake port and the heat source side refrigerant-air heat exchanger to control the amount of return air from the return air intake port to the heat source side refrigerant-air heat exchanger; The heat source side refrigerant-air heat exchanger is disposed on the lee side between the heat source side refrigerant-air heat exchanger and the heat source side blower to bypass the heat source side refrigerant-air heat exchanger and return the heat source side refrigerant-air heat exchanger. The most important feature is that a third return air damper for controlling the amount of return air flow from the intake port to the exhaust port is provided.

請求項1の発明によれば、農産業用の被空調空間に対して循環空調、換気循環空調、換気(外気冷房、外気暖房)などの各種パターンの運転を行える。ヒートポンプを動かさない換気運転で、熱源側冷媒−空気熱交換器を通さずに排気できるので、熱源側送風機の負荷が減り動力費を節減でき、特に換気運転が多くなる農産業用で大きな省エネ効果を得られる。しかも外気と還気を混合して空調する換気循環運転では熱源側冷媒−空気熱交換器で熱回収ができて省エネとなり、その外気と還気の風量混合比調節も第2還気ダンパだけで行えるので制御が非常に簡単になる。栽培室や倉庫、工場などの縦壁の通風口に給気口と還気取入口を嵌合して空調機を設置するだけで被空調空間を空調できるので、ダクトが不要となり設備コストを低減できる。ケーシングが縦型で正面・背面方向に薄いので設置面積が小さくて済み、壁から外に張り出さず邪魔にならない。下から吸い込んで上から吹出すので気流分布が良くなり温調ムラを防止できる。ケーシングの両サイドから外気を取入れるようにしてあるので背面側から容易にメンテナンスできる。
請求項2の発明によれば、熱源側送風路の傾斜状上端仕切面に被さるように給気側送風路の上端部が折曲がって拡径するので反射減衰による減音作用が向上し、かつ給気口と排気口の部分が嵩高くならずコンパクトにでき吹出し範囲を幅広くとれ、熱源側送風路の傾斜状上端仕切面に沿ってスムーズに排気できて圧力損失の減少を図れる。
請求項3の発明によれば、給気側冷媒−空気熱交換器と熱源側冷媒−空気熱交換器の圧力損失が減少して熱交換効率が向上するので小型の送風機を用いることができ騒音低減を図れる。給気側冷媒−空気熱交換器と熱源側冷媒−空気熱交換器も小型化でき空調機をコンパクト化できる。
According to the first aspect of the present invention, various patterns of operation such as circulation air conditioning, ventilation circulation air conditioning, and ventilation (outside air cooling, outside air heating) can be performed on the air-conditioned space for the agricultural industry. Ventilation operation without moving the heat pump allows exhaust without passing through the heat source side refrigerant-air heat exchanger, reducing the load on the heat source side blower and reducing power costs, especially in the agricultural industry where ventilation operation increases. Can be obtained. Moreover, in the ventilation and circulation operation in which the outside air and the return air are mixed and air-conditioned, heat can be recovered with the heat source side refrigerant-air heat exchanger, which saves energy, and the air volume mixing ratio adjustment of the outside air and the return air can be adjusted only by the second return air damper. This makes it very easy to control. The air-conditioned space can be air-conditioned simply by fitting the air supply and return air inlets to the vertical wall vents in the cultivation room, warehouse, factory, etc., eliminating the need for ducts and reducing equipment costs it can. Since the casing is vertical and thin in the front and back directions, the installation area is small, and it does not protrude out of the wall and does not get in the way. Since air is sucked in from the bottom and blown out from the top, the air flow distribution is improved and temperature control unevenness can be prevented. Since outside air is taken in from both sides of the casing, maintenance can be easily performed from the back side.
According to the invention of claim 2, since the upper end portion of the air supply side air passage is bent and expanded in diameter so as to cover the inclined upper end partition surface of the heat source side air passage, the sound reduction effect due to reflection attenuation is improved, and The portions of the air supply port and the exhaust port can be made compact without being bulky, and the blowout range can be widened. The air can be smoothly exhausted along the inclined upper partition surface of the heat source side air passage so that the pressure loss can be reduced.
According to the invention of claim 3, since the pressure loss of the supply side refrigerant-air heat exchanger and the heat source side refrigerant-air heat exchanger is reduced and the heat exchange efficiency is improved, a small blower can be used and the noise is reduced. Reduction can be achieved. The supply-side refrigerant-air heat exchanger and the heat source-side refrigerant-air heat exchanger can also be miniaturized, and the air conditioner can be made compact.

図1〜図5は、本発明の農産業用空気熱源ヒートポンプ式空調機の一実施例を示しており、実線及び点線の白抜き矢印は送風方向を示す。この空調機は、ケーシング1と、ヒートポンプCと、を備えており、ケーシング1を正面・背面方向に扁平状に形成し、このケーシング1の正面側上端部に給気口2を、背面側上端部に排気口3を、各々形成すると共に、ケーシング1の正面側下端部に還気取入口4を形成し、かつケーシング1の一側面下端部に第1外気取入口5を、他側面下端部に第2外気取入口6を、各々形成する。栽培室や倉庫、工場などの被空調空間の縦壁に形成した上部通風口と下部通風口に、前記被空調空間内へ給気吹出し自在として給気口2を、前記被空調空間内から還気取入自在として還気取入口4を、各々配置し、前記縦壁の外面にケーシング1をその正面を面対向させて設置する(図2と図3参照)。この給気口2と還気取入口4と第1外気取入口5に各々連通する給気側送風路Aと、排気口3と還気取入口4と第2外気取入口6とに各々連通する熱源側送風路Bと、をケーシング1内に並列に立設する。給気側送風路Aには、第1外気取入口5からの外気と還気取入口4からの還気とが選択的に通風される給気側冷媒−空気熱交換器7と、加湿器16と、風量制御自在な給気側送風機9と、を設け、熱源側送風路Bには、第2外気取入口6からの外気と還気取入口4からの還気とが選択的に通風される熱源側冷媒−空気熱交換器8と、風量制御自在な吸込み式の熱源側送風機10と、を設ける。   FIGS. 1-5 has shown one Example of the air heat source heat pump type air conditioner for agricultural industries of this invention, and the solid line and the dotted white arrow show the ventilation direction. This air conditioner includes a casing 1 and a heat pump C. The casing 1 is formed in a flat shape in the front and rear directions, and the air supply port 2 is formed at the front upper end of the casing 1 and the rear upper end. The exhaust port 3 is formed in each part, the return air intake 4 is formed in the lower end on the front side of the casing 1, the first outside air intake 5 is formed in the lower end on one side of the casing 1, and the lower end on the other side The second outside air intakes 6 are respectively formed in The air supply port 2 is returned from the air-conditioned space so that the air can be blown into the air-conditioned space at the upper and lower vents formed in the vertical wall of the air-conditioned space such as a cultivation room, a warehouse, or a factory. The return air intakes 4 are respectively arranged so as to be freely entrapped, and the casing 1 is installed on the outer surface of the vertical wall with its front face facing (see FIGS. 2 and 3). The air supply side air passage A, which communicates with the air supply port 2, the return air intake 4, and the first outside air intake 5, and the exhaust port 3, the return air intake 4, and the second outside air intake 6, respectively. And the heat source side air passage B to be erected in parallel in the casing 1. In the air supply side air passage A, an air supply side refrigerant-air heat exchanger 7 through which the outside air from the first outside air intake 5 and the return air from the return air intake 4 are selectively ventilated, and a humidifier are provided. 16 and an air supply side blower 9 capable of controlling the air volume, and the heat source side air passage B is selectively ventilated with outside air from the second outside air intake 6 and return air from the return air inlet 4. A heat source side refrigerant-air heat exchanger 8 and a suction type heat source side blower 10 capable of controlling the air volume are provided.

ケーシング1には、熱源側冷媒−空気熱交換器8の風上側であって第2外気取入口6と熱源側冷媒−空気熱交換器8との間に配置されて還気取入口4から熱源側冷媒−空気熱交換器8への還気風量を制御する第2還気ダンパ15と、熱源側冷媒−空気熱交換器8の風下側であって熱源側冷媒−空気熱交換器8と熱源側送風機10との間に配置されて熱源側冷媒−空気熱交換器8をバイパスさせると共に還気取入口4から排気口3への還気風量を制御する第3還気ダンパ17と、第1外気取入口5から給気側冷媒−空気熱交換器7への外気風量を制御する外気ダンパ13と、還気取入口4から給気側冷媒−空気熱交換器7への還気風量を制御する第1還気ダンパ14と、を設けて、各種の運転制御装置等により風量制御を行う。各ダンパ13、14、15、17は、全閉・全開切換のみ又は任意風量可変自在の何れの構造であってもよい。ダンパ14、17、15はケーシング1の正面側下端部に横並びに配置し、これらと給気側送風路Aと熱源側送風路Bにまたがって還気取入口4を1つ設けて構造の簡略化とコストダウンを図っているが、還気取入口4を、ダンパ14、17、15に別々に1つずつ又は給気側送風路Aと熱源側送風路Bに別々に1つずつ設けてもよい。熱源側冷媒−空気熱交換器8は、その空気出入口面を第3還気ダンパ17から熱源側送風機10への気流方向と略平行になるように配置し、第2還気ダンパ15閉及び第3還気ダンパ17閉状態において外気が熱源側冷媒−空気熱交換器8を流れ(図6(a)参照)、第2還気ダンパ15開及び第3還気ダンパ17閉状態において還気と外気が熱源側冷媒−空気熱交換器8を流れ(図6(b)参照)、第2還気ダンパ15閉及び第3還気ダンパ17開状態において還気が熱源側冷媒−空気熱交換器8をバイパスして流れて外気が熱源側冷媒−空気熱交換器8に流れない(図6(c)参照)ようにし、外気と還気の送風切換えと風量調整をする。   The casing 1 is arranged on the windward side of the heat source side refrigerant-air heat exchanger 8 and between the second outside air intake 6 and the heat source side refrigerant-air heat exchanger 8, and from the return air intake 4 to the heat source. A second return air damper 15 that controls the amount of return air flow to the side refrigerant-air heat exchanger 8, and the lee side of the heat source side refrigerant-air heat exchanger 8 that is the heat source side refrigerant-air heat exchanger 8 and heat source. A third return air damper 17 disposed between the side air blower 10 and bypassing the heat source side refrigerant-air heat exchanger 8 and controlling the amount of return air from the return air intake 4 to the exhaust port 3; An outside air damper 13 that controls the amount of outside air from the outside air intake 5 to the supply side refrigerant-air heat exchanger 7 and a amount of return air that flows from the return air intake 4 to the supply side refrigerant-air heat exchanger 7 are controlled. The first return air damper 14 is provided, and air volume control is performed by various operation control devices and the like. Each of the dampers 13, 14, 15, and 17 may have any structure in which only the full-close / full-open switching is performed or the arbitrary air volume can be varied. The dampers 14, 17, and 15 are arranged side by side at the lower end on the front side of the casing 1, and a single return air intake 4 is provided across these, the air supply side air passage A and the heat source side air passage B, and the structure is simplified. However, the return air intake 4 is provided separately for each of the dampers 14, 17, and 15, or separately for the air supply side air passage A and the heat source side air passage B. Also good. The heat source side refrigerant-air heat exchanger 8 is arranged so that its air inlet / outlet surface is substantially parallel to the air flow direction from the third return air damper 17 to the heat source side blower 10, and the second return air damper 15 is closed and When the third return air damper 17 is closed, the outside air flows through the heat source side refrigerant-air heat exchanger 8 (see FIG. 6A), and when the second return air damper 15 is open and the third return air damper 17 is closed, The outside air flows through the heat source side refrigerant-air heat exchanger 8 (see FIG. 6B), and the return air is the heat source side refrigerant-air heat exchanger when the second return air damper 15 is closed and the third return air damper 17 is open. 8 is bypassed so that the outside air does not flow to the heat-source-side refrigerant-air heat exchanger 8 (see FIG. 6C), and the ventilation switching and the air volume adjustment of the outside air and the return air are performed.

熱源側送風路Bの上端仕切面12は背面側から正面側に向かって下傾させ、上端仕切面12とケーシング1内面にて形成された空間を給気側送風路Aとして利用する。排気口3は斜め下乃至下方に吹出す庇状に形成して、積雪対策を不要とする。ケーシング1の背面は、着脱又は開閉自在なメンテナンス用の外装板にて形成して、障害物のない背面側から内部を容易にメンテナンスできるようにする。なお、排気口3と給気口2は図例以外の形状構造のものに変更するも自由で、例えば、給気口3はパンカルーバーとして局所への吹出しを可能としてもよい。   The upper end partitioning surface 12 of the heat source side air passage B is inclined downward from the back side toward the front side, and the space formed by the upper end partitioning surface 12 and the inner surface of the casing 1 is used as the air supply side air passage A. The exhaust port 3 is formed in the shape of a bowl that blows obliquely downward or downward, eliminating the need for snow cover. The back surface of the casing 1 is formed of a maintenance exterior plate that can be attached or detached and opened and closed, so that the inside can be easily maintained from the back side without any obstacles. The exhaust port 3 and the air supply port 2 can be freely changed to shapes other than those shown in the figure. For example, the air supply port 3 may be locally blown out as a pan culver.

ヒートポンプCは、循環冷媒に対して蒸発・圧縮・凝縮・膨張の工程順を繰返し、この循環冷媒と熱交換する空気に対して冷媒蒸発工程で吸熱を冷媒凝縮工程で放熱を各々行うもので、循環冷媒の蒸発工程と凝縮工程であって互いに異なる工程を行う給気側冷媒−空気熱交換器7及び熱源側冷媒−空気熱交換器8と、循環冷媒を圧縮する圧縮機11と、循環冷媒を膨張させる膨張弁等の減圧機構18と、給気側冷媒−空気熱交換器7及び熱源側冷媒−空気熱交換器8の蒸発工程と凝縮工程を切換えるバルブ等の切換機構19と、を少なくとも備え、これらを冷媒が循環するように配管接続して成る。給気側冷媒−空気熱交換器7では循環冷媒で給気用空気を冷却又は加熱し、熱源側冷媒−空気熱交換器8では熱源用空気で循環冷媒を凝縮又は蒸発させる。給気側冷媒−空気熱交換器7と熱源側冷媒−空気熱交換器8のフィンチューブは圧損の少ない楕円管にするのが好ましいが円形管でもよい。また、この空調機は、ヒートポンプCと送風機9、10と加湿器16の各々の容量制御をすると共に給気側送風路入口空気温湿度に応じて給気側冷媒−空気熱交換器7の冷媒蒸発・冷媒凝縮を切換する制御手段(図示省略)を、備えている。   The heat pump C repeats the process sequence of evaporation, compression, condensation, and expansion for the circulating refrigerant, and performs heat absorption in the refrigerant condensation process for the heat exchanged with the circulating refrigerant in the refrigerant condensation process. A supply-side refrigerant-air heat exchanger 7 and a heat-source-side refrigerant-air heat exchanger 8 that perform the steps of evaporating and condensing the circulating refrigerant that are different from each other, a compressor 11 that compresses the circulating refrigerant, and the circulating refrigerant A decompression mechanism 18 such as an expansion valve for expanding the refrigerant, and a switching mechanism 19 such as a valve for switching between an evaporation process and a condensation process of the supply side refrigerant-air heat exchanger 7 and the heat source side refrigerant-air heat exchanger 8. These are connected by piping so that the refrigerant circulates. The supply side refrigerant-air heat exchanger 7 cools or heats the supply air with the circulating refrigerant, and the heat source side refrigerant-air heat exchanger 8 condenses or evaporates the circulating refrigerant with the heat source air. The fin tubes of the supply side refrigerant-air heat exchanger 7 and the heat source side refrigerant-air heat exchanger 8 are preferably elliptical tubes with little pressure loss, but may be circular tubes. The air conditioner controls the capacity of each of the heat pump C, the blowers 9 and 10 and the humidifier 16 and also the refrigerant of the supply side refrigerant-air heat exchanger 7 according to the supply side air passage inlet air temperature and humidity. Control means (not shown) for switching between evaporation and refrigerant condensation is provided.

図6に示すように、この空調機では、循環空調、換気循環空調、換気(外気冷房、外気暖房)などの各種パターンの運転を行える。図6(a)に示す循環空調運転では、外気ダンパ13と第2還気ダンパ15と第3還気ダンパ17を閉じ、第1還気ダンパ14を開にし、第1還気ダンパ14から取入れた被空調空間の還気を給気側冷媒−空気熱交換器7の循環冷媒で熱交換し、必要に応じて加湿器16を作動させて温湿度調整して給気口2から被空調空間へ給気し、第2外気取入口6から取入れた外気で熱源側冷媒−空気熱交換器8の循環冷媒を熱交換して吸熱又は放熱し排気口3から屋外へ排気する。図6(b)に示す換気循環空調運転では、外気ダンパ13と第2還気ダンパ15と第1還気ダンパ14を開にし、第3還気ダンパ17を閉じ、第1還気ダンパ14から取入れた還気と外気ダンパ13から取入れた外気を所定割合で混合して給気側冷媒−空気熱交換器7で熱交換し、必要に応じて加湿器16を作動させて温湿度調整して給気口2から被空調空間へ給気し、第2外気取入口6から取入れた外気と第2還気ダンパ15から取入れた還気を所定割合で混合して熱源側冷媒−空気熱交換器8の循環冷媒を熱回収しながら熱交換・熱回収し排気口3から屋外へ排気する。図6(c)に示す換気(外気冷房、外気暖房)運転では、ヒートポンプCを止めて、第1還気ダンパ14と第2還気ダンパ15を閉じ、外気ダンパ13と第3還気ダンパ17を開にして、外気ダンパ13から外気を取入れ、必要に応じて加湿器16を作動させて湿度調整して被空調空間に給気し、第3還気ダンパ17から取入れた還気を排気口3から屋外へ排気する。   As shown in FIG. 6, in this air conditioner, various patterns of operation such as circulation air conditioning, ventilation circulation air conditioning, and ventilation (outside air cooling, outside air heating) can be performed. In the circulating air-conditioning operation shown in FIG. 6A, the outside air damper 13, the second return air damper 15, and the third return air damper 17 are closed, the first return air damper 14 is opened, and the first return air damper 14 is taken in. The return air in the air-conditioned space is heat-exchanged with the circulating refrigerant in the air-supply side refrigerant-air heat exchanger 7 and, if necessary, the humidifier 16 is operated to adjust the temperature and humidity so that the air-conditioned space is supplied from the air supply port 2. Then, the outside air taken in from the second outside air intake 6 exchanges heat with the circulating refrigerant in the heat source side refrigerant-air heat exchanger 8 to absorb or dissipate the heat and exhaust it from the exhaust port 3 to the outside. In the ventilation / circulation air-conditioning operation shown in FIG. 6B, the outside air damper 13, the second return air damper 15, and the first return air damper 14 are opened, the third return air damper 17 is closed, and the first return air damper 14 is opened. The introduced return air and the outside air taken in from the outside air damper 13 are mixed at a predetermined ratio, heat exchange is performed by the supply side refrigerant-air heat exchanger 7, and the humidifier 16 is operated as necessary to adjust the temperature and humidity. The heat source side refrigerant-air heat exchanger is configured by supplying air to the air-conditioned space from the air supply port 2 and mixing the outside air taken in from the second outside air intake 6 and the return air taken in from the second return air damper 15 at a predetermined ratio. While the heat of the circulating refrigerant 8 is recovered, the heat is exchanged and recovered and exhausted from the exhaust port 3 to the outside. In the ventilation (outside air cooling, outside air heating) operation shown in FIG. 6C, the heat pump C is stopped, the first return air damper 14 and the second return air damper 15 are closed, and the outside air damper 13 and the third return air damper 17 are closed. Is opened, the outside air is taken in from the outside air damper 13, the humidifier 16 is operated as necessary to adjust the humidity to supply air to the air-conditioned space, and the return air taken in from the third return air damper 17 is discharged to the exhaust port. Exhaust from 3 to the outdoors.

本発明の実施例を示す正面図。The front view which shows the Example of this invention. 図1の側面図。The side view of FIG. 図1の平面図。The top view of FIG. 一部を破断して示す上部の斜視図。The upper part perspective view which fractures | ruptures and shows. ヒートポンプの簡略説明図。The simplified explanatory drawing of a heat pump. 運転パターンの簡略説明図。The simplified explanatory drawing of an operation pattern.

符号の説明Explanation of symbols

1 ケーシング
2 給気口
3 排気口
4 還気取入口
5 第1外気取入口
6 第2外気取入口
7 給気側冷媒−空気熱交換器
8 熱源側冷媒−空気熱交換器
10 熱源側送風機
12 上端仕切面
13 外気ダンパ
14 第1還気ダンパ
15 第2還気ダンパ
17 第3還気ダンパ
A 給気側送風路
B 熱源側送風路
DESCRIPTION OF SYMBOLS 1 Casing 2 Air supply port 3 Exhaust port 4 Return air intake 5 1st external air intake 6 2nd external air intake 7 Supply air side refrigerant | coolant-air heat exchanger 8 Heat source side refrigerant | coolant-air heat exchanger 10 Heat source side air blower 12 Upper end partition surface 13 Outside air damper 14 First return air damper 15 Second return air damper 17 Third return air damper A Supply side air passage B Heat source side air passage

Claims (3)

ケーシング1を正面・背面方向に扁平状に形成し、このケーシング1の正面側上端部に給気口2を、背面側上端部に排気口3を、各々形成すると共に、前記ケーシング1の正面側下端部に還気取入口4を形成し、かつ前記ケーシング1の一側面下端部に第1外気取入口5を、他側面下端部に第2外気取入口6を、各々形成し、前記給気口2と前記還気取入口4と前記第1外気取入口5に各々連通する給気側送風路Aと、前記排気口3と前記還気取入口4と前記第2外気取入口6とに各々連通する熱源側送風路Bと、を前記ケーシング1内に並列に立設し、給気側冷媒−空気熱交換器7を前記給気側送風路Aに設け、熱源側冷媒−空気熱交換器8と熱源側送風機10とを前記熱源側送風路Bに設け、前記熱源側冷媒−空気熱交換器8の風上側であって前記第2外気取入口6と前記熱源側冷媒−空気熱交換器8との間に配置されて前記還気取入口4から前記熱源側冷媒−空気熱交換器8への還気風量を制御する第2還気ダンパ15と、前記熱源側冷媒−空気熱交換器8の風下側であって前記熱源側冷媒−空気熱交換器8と前記熱源側送風機10との間に配置されて前記熱源側冷媒−空気熱交換器8をバイパスさせると共に前記還気取入口4から前記排気口3への還気風量を制御する第3還気ダンパ17と、を設けたことを特徴とする農産業用空気熱源ヒートポンプ式空調機。   The casing 1 is formed in a flat shape in the front / rear direction, an air supply port 2 is formed at the front upper end portion of the casing 1, and an exhaust port 3 is formed at the upper end portion of the rear side. The return air intake 4 is formed at the lower end, the first outside air intake 5 is formed at the lower end of one side of the casing 1, and the second outside air intake 6 is formed at the lower end of the other side. An air supply side air passage A communicating with the inlet 2, the return air inlet 4, and the first outside air inlet 5, the exhaust port 3, the return air inlet 4, and the second outside air inlet 6. Heat source side air passages B communicating with each other are arranged in parallel in the casing 1, and an air supply side refrigerant-air heat exchanger 7 is provided in the air supply side air passage A, so that the heat source side refrigerant-air heat exchange is provided. The heat source side air blower 10 is provided in the heat source side air passage B, and the heat source side refrigerant-air heat exchanger 8 is on the windward side. Thus, the amount of return air flow from the return air intake 4 to the heat source side refrigerant-air heat exchanger 8 is arranged between the second outside air intake 6 and the heat source side refrigerant-air heat exchanger 8. The second return air damper 15 to be controlled and the leeward side of the heat source side refrigerant-air heat exchanger 8 and disposed between the heat source side refrigerant-air heat exchanger 8 and the heat source side blower 10 and Agricultural industry characterized by including a third return air damper 17 that bypasses the heat source side refrigerant-air heat exchanger 8 and controls the amount of return air from the return air inlet 4 to the exhaust port 3. Air heat source heat pump air conditioner. 熱源側送風路Bの上端仕切面12を背面側から正面側に向かって下傾させ、前記上端仕切面12とケーシング1内面にて形成された空間を給気側送風路Aとして利用した請求項1記載の農産業用空気熱源ヒートポンプ式空調機。   The upper end partition surface 12 of the heat source side air passage B is inclined downward from the back side toward the front side, and the space formed by the upper end partition surface 12 and the inner surface of the casing 1 is used as the air supply side air passage A. The air heat source heat pump type air conditioner for agricultural industry according to 1. 給気側冷媒−空気熱交換器7と熱源側冷媒−空気熱交換器8のフィンチューブを楕円管にした請求項1又は2記載の農産業用空気熱源ヒートポンプ式空調機。   The air heat source heat pump type air conditioner for agricultural industry according to claim 1 or 2, wherein fin tubes of the supply side refrigerant-air heat exchanger 7 and the heat source side refrigerant-air heat exchanger 8 are elliptical tubes.
JP2005014839A 2005-01-21 2005-01-21 Air heat source heat pump air conditioner for agricultural industry Active JP4016988B2 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105444325A (en) * 2015-12-21 2016-03-30 苏州贝艾尔净化科技有限公司 Fresh air purification system with axial-flow fans

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Publication number Priority date Publication date Assignee Title
US9121620B2 (en) * 2013-10-31 2015-09-01 Robert M. Rohde Energy efficient HVAC system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105444325A (en) * 2015-12-21 2016-03-30 苏州贝艾尔净化科技有限公司 Fresh air purification system with axial-flow fans

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