JPH0533969A - Air conditioner - Google Patents
Air conditionerInfo
- Publication number
- JPH0533969A JPH0533969A JP3193037A JP19303791A JPH0533969A JP H0533969 A JPH0533969 A JP H0533969A JP 3193037 A JP3193037 A JP 3193037A JP 19303791 A JP19303791 A JP 19303791A JP H0533969 A JPH0533969 A JP H0533969A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- heat exchanger
- expansion valve
- temperature
- radiant
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は，室内熱交換器による対
流空気調和に併せて，輻射パネルによる輻射空気調和を
行うことのできる空気調和機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner capable of performing radiant air conditioning by a radiant panel in addition to convection air conditioning by an indoor heat exchanger.
【０００２】[0002]
【従来の技術】近年，冷暖房装置に対し，以前にも増し
て快適性が求められており，快適性を高める一つの手段
として輻射パネルの使用が注目されている。輻射パネル
の効果として，送風による騒音や風による不快感がない
こと，直接的に身体に作用するため空調効果が高いこと
などの利点がある。従来の輻射による空気調和を用いた
空気調和機の例を図７に示す。同図に示されるように，
室内熱交換器による対流に，輻射パネルによる輻射を併
せた空気調和を行う空気調和機である。このような従来
の空気調和機の構成は，圧縮機３１，室内熱交換器３
２，膨張弁３４，冷媒・ブライン熱交換器３５で構成さ
れる冷凍サイクル４５と，メインブライン回路用循環ポ
ンプ３６，輻射パネル４０，膨張タンク４１，輻射パネ
ル制御用三方混合弁４２で構成されるブラインサイクル
４６とからなっている。このように室内側にブラインサ
イクルを用いている理由は，冷房運転における輻射パネ
ル４０の結露対策にある。輻射パネル４０の表面温度が
室内空気の露点より低下すると，輻射パネル４０の表面
に結露が発生し実用に耐えない。そこで，室内空気の露
点温度と輻射パネル４０の表面温度を測定し，輻射パネ
ル４０の温度が室内空気の露点温度より低下しないよう
調節する手法が必要となるが，輻射パネル４０の熱媒体
にブラインを使用したブラインサイクルを用いると，容
易に輻射パネル４０の温度を調節することが可能とな
る。以下に上記構成の動作を説明する。まず，冷房運転
においては，冷凍サイクル４５における圧縮器３１から
吐出された高温高圧の冷媒は，四方弁４３から室外熱交
換器３２に入り，室外ファン３３によって外気と熱交換
して放熱し，凝縮液化したのち，膨張弁３４で減圧さ
れ，低圧の気液二相状態となって冷媒・ブライン熱交換
器３５に入り，ブラインサイクル４６側のブラインから
吸熱して蒸発気化し，低温低圧の蒸気となって圧縮機３
１に吸入されるサイクルを繰り返す。2. Description of the Related Art In recent years, more and more comfort has been required for air conditioners, and the use of a radiation panel has attracted attention as one means for improving comfort. The effect of the radiation panel is that there are no noises and unpleasant sensations due to the air flow, and that the air conditioning effect is high because it directly affects the body. FIG. 7 shows an example of a conventional air conditioner that uses air conditioning by radiation. As shown in the figure,
It is an air conditioner that combines the convection of the indoor heat exchanger with the radiation of the radiation panel. The configuration of such a conventional air conditioner includes a compressor 31, an indoor heat exchanger 3
2, a refrigeration cycle 45 including an expansion valve 34 and a refrigerant / brine heat exchanger 35, a main brine circuit circulation pump 36, a radiation panel 40, an expansion tank 41, and a radiation panel control three-way mixing valve 42. It consists of a brine cycle 46. The reason why the brine cycle is used on the indoor side in this way is to prevent dew condensation on the radiation panel 40 during the cooling operation. When the surface temperature of the radiant panel 40 falls below the dew point of the room air, dew condensation occurs on the surface of the radiant panel 40, which is not practical. Therefore, it is necessary to measure the dew point temperature of the indoor air and the surface temperature of the radiant panel 40 and adjust the temperature of the radiant panel 40 so as not to fall below the dew point temperature of the indoor air. When the brine cycle using is used, the temperature of the radiation panel 40 can be easily adjusted. The operation of the above configuration will be described below. First, in the cooling operation, the high-temperature and high-pressure refrigerant discharged from the compressor 31 in the refrigeration cycle 45 enters the outdoor heat exchanger 32 from the four-way valve 43, exchanges heat with the outdoor air by the outdoor fan 33, radiates heat, and condenses. After liquefying, it is decompressed by the expansion valve 34, enters a low-pressure gas-liquid two-phase state, enters the refrigerant / brine heat exchanger 35, absorbs heat from the brine on the brine cycle 46 side, evaporates to vapor, and becomes low-temperature low-pressure vapor. Become a compressor 3
The cycle of inhaling 1 is repeated.
【０００３】一方，ブラインサイクル４６では，メイン
ブライン回路用循環ポンプ３６から吐出されたブライン
は，冷媒・ブライン熱交換器３５で冷凍サイクル４５側
の冷媒に放熱して冷却され，室内熱交換器３７に入る一
方，分岐して輻射パネル温度制御用三方混合弁４２を通
って輻射パネル４０に入る。この輻射パネル温度制御用
三方混合弁４２は，冷媒・ブライン熱交換器３５からの
冷却されたブラインと，輻射パネル４０を通り室内熱を
吸収し昇温したブラインとを混合し，輻射パネル４０が
結露しないよう２つのブラインの混合量を調節して温度
調節を行っている。輻射パネル４０には輻射パネル回路
用循環ポンプ３９が並列に設けられており，輻射パネル
温度制御用三方混合弁４２へ昇温したブラインを送給し
ている。室内熱交換器３７及び輻射パネル４０を出たブ
ラインはメインブライン回路用ポンプ３６に吸入される
サイクルを繰り返すことにより，室内熱交換器３７にお
いて室内ファン３８により対流冷房が行われ，輻射パネ
ル４０により輻射冷房が行われる。次に，暖房運転にお
いては，圧縮機３１から吐出された高温高圧の冷媒は，
四方弁４３からブライン熱交換器３５に入り，ブライン
サイクル４６側のブラインに放熱して凝縮液化し，膨張
弁３４で減圧され低圧の気液二相状態となって室外熱交
換器３２に入り，室外ファン３３により外気と熱交換し
て蒸発気化し，低温低圧の蒸気となって圧縮機３１に吸
入されるサイクルを繰り返す。一方，ブラインサイクル
４６では，メインブライン回路用循環ポンプ３６から吐
出されたブラインは，冷媒・ブライン熱交換器３５で冷
凍サイクル４５側の冷媒から吸熱して室内熱交換器３７
に入り，室内ファン３８により室内を対流暖房すると共
に，輻射パネル温度制御用三方混合弁４２から輻射パネ
ル４０に入り，輻射パネル４０により室内を輻射暖房す
る。輻射パネル４０の温度調節は，前記冷房運転時と同
様に輻射パネル回路用循環ポンプ３９によって戻される
ブラインと冷媒・ブライン熱交換器３５からのブライン
とを，輻射パネル温度制御用三方混合弁４２で混合して
行っている。On the other hand, in the brine cycle 46, the brine discharged from the main brine circuit circulation pump 36 radiates heat to the refrigerant on the refrigeration cycle 45 side in the refrigerant / brine heat exchanger 35 to be cooled, and the indoor heat exchanger 37. While entering, it branches and enters the radiation panel 40 through the radiation panel temperature controlling three-way mixing valve 42. The radiant panel temperature control three-way mixing valve 42 mixes the cooled brine from the refrigerant / brine heat exchanger 35 with the brine that has passed through the radiant panel 40 and has absorbed the indoor heat and has risen in temperature. The temperature is controlled by adjusting the mixing amount of the two brines to prevent dew condensation. The radiation panel 40 is provided with a radiation panel circuit circulation pump 39 in parallel, and feeds the heated brine to the radiation panel temperature control three-way mixing valve 42. By repeating the cycle in which the brine discharged from the indoor heat exchanger 37 and the radiation panel 40 is sucked into the main brine circuit pump 36, convection cooling is performed by the indoor fan 38 in the indoor heat exchanger 37, and the radiation panel 40 is used. Radiant cooling is performed. Next, in the heating operation, the high-temperature and high-pressure refrigerant discharged from the compressor 31 is
The four-way valve 43 enters the brine heat exchanger 35, radiates heat to the brine on the brine cycle 46 side to be condensed and liquefied, and is decompressed by the expansion valve 34 into a low-pressure gas-liquid two-phase state and enters the outdoor heat exchanger 32, The outdoor fan 33 exchanges heat with the outside air to evaporate and vaporize to become low-temperature and low-pressure vapor, which is sucked into the compressor 31 repeatedly. On the other hand, in the brine cycle 46, the brine discharged from the main brine circuit circulation pump 36 absorbs heat from the refrigerant on the refrigeration cycle 45 side in the refrigerant / brine heat exchanger 35, and the indoor heat exchanger 37.
The indoor fan 38 heats the room convectively, and the radiant panel temperature controlling three-way mixing valve 42 enters the radiant panel 40 to radiantly heat the room. The temperature of the radiant panel 40 is controlled by the three-way mixing valve 42 for controlling the radiant panel temperature by controlling the brine returned by the radiant panel circuit circulation pump 39 and the brine from the refrigerant / brine heat exchanger 35 in the same manner as during the cooling operation. It's mixed.
【０００４】[0004]
【発明が解決しようとする課題】上記従来例において
は，冷媒・ブライン熱交換器を介して冷媒とブラインと
の熱交換を行っているため，空気と冷媒との温度差が大
きくなり，冷凍サイクルの蒸発圧力が低下しＣＯＰが小
さくなる。また，ブラインサイクル側に２台の循環ポン
プを必要とするため，その電力消費分のＣＯＰが小さく
なる。このように従来例空気調和機においては，輻射を
利用した空気調和の特徴であるはずの省エネルギー性
（ＣＯＰ）が実現できず，強制対流式のみの空気調和機
のＣＯＰよりも劣るものであった。本発明，上記従来例
の課題を解決するため，ブラインサイクルを用いず，冷
凍サイクルのみで輻射と強制対流とを併用した空気調和
機を提供することを目的とする。In the above conventional example, since the heat exchange between the refrigerant and the brine is performed via the refrigerant / brine heat exchanger, the temperature difference between the air and the refrigerant becomes large, and the refrigeration cycle is increased. The vaporization pressure of is reduced and COP is reduced. Moreover, since two circulation pumps are required on the side of the brine cycle, the COP of the power consumption is reduced. As described above, in the conventional air conditioner, the energy saving (COP) that should be the characteristic of the air conditioner using radiation could not be realized, and it was inferior to the COP of only the forced convection air conditioner. .. In order to solve the problems of the present invention and the conventional example described above, it is an object of the present invention to provide an air conditioner that uses both radiation and forced convection only in a refrigeration cycle without using a brine cycle.
【０００５】[0005]
【課題を解決するための手段】上記目的を達成するため
に，本発明が採用する手段は，圧縮機，室外熱交換器，
第１の膨張弁，室内熱交換器を順次連結した冷凍サイク
ルにおける前記室内熱交換器による対流空気調和と，前
記冷凍サイクルを流れる冷媒の一部を用いる輻射パネル
による輻射空気調和とを行う空気調和機において，上記
輻射パネルに垂直方向の複数のヒートパイプを配設し，
該ヒートパイプの上端及び下端を連結管で接続すると共
に，所定量の冷媒を充填し，前記下端の連結管に加熱用
冷媒管を貫通させて前記第１の膨張弁と前記室内熱交換
器との間に配管し，前記上端の連結管に冷却用冷媒管を
貫通させて，該冷却用冷媒管の一方を第２の膨張弁を介
して前記室外熱交換器に接続し，該冷却用冷媒管の他方
を第３の膨張弁を介して前記圧縮機に接続してなること
を特徴とする空気調和機として構成される。In order to achieve the above object, the means adopted by the present invention are a compressor, an outdoor heat exchanger,
Air conditioning that performs convective air conditioning by the indoor heat exchanger in a refrigeration cycle in which a first expansion valve and an indoor heat exchanger are sequentially connected and radiant air conditioning by a radiant panel that uses a part of the refrigerant flowing in the refrigeration cycle In the machine, a plurality of vertical heat pipes are arranged on the radiation panel,
The upper end and the lower end of the heat pipe are connected by a connecting pipe, a predetermined amount of refrigerant is filled, and the connecting refrigerant pipe at the lower end is penetrated by a heating refrigerant pipe to connect the first expansion valve and the indoor heat exchanger. The cooling refrigerant pipe through the connecting pipe at the upper end, and one of the cooling refrigerant pipes is connected to the outdoor heat exchanger through a second expansion valve to provide the cooling refrigerant. The other of the pipes is connected to the compressor via a third expansion valve, and the air conditioner is configured.
【０００６】[0006]
【作用】本発明によれば，冷凍サイクルにおける室内熱
交換器の強制対流による空気調和を行う一方で，該冷凍
サイクルを流れる冷媒の一部を用いて輻射パネル内のヒ
ートパイプを作動させ，輻射による空気調和を行ってい
る。まず，冷房運転時においては，第２膨張弁による膨
張率が第１膨張弁による膨張率より低く設定されてお
り，室外熱交換器で凝縮液化した冷媒の一部が分岐し
て，第２の膨張分を通って前記輻射パネルの上端の連結
管内を通過するとき，輻射パネルが室内の熱を奪うこと
により蒸発し，上端の連結管側に移動している輻射パネ
ルのヒートポンプ内の冷媒を凝縮液化させる。液化した
該冷媒はヒートパイプ内を自然落下して下端の連結管側
に溜まり，輻射パネルの集熱で再び蒸発するサイクルを
繰り返す。この蒸発，液化のサイクルにより輻射パネル
は冷却され，室内を輻射冷房する。また，室外熱交換器
で凝縮液化した冷媒は第１の膨張弁側にも流れ，輻射パ
ネルの下端の連結管内を通過して室内熱交換器に入り，
室内ファンの強制対流による冷房を行う。冷媒が前記下
端の連結管内を通過するときには，輻射パネル内冷媒は
下端の連結管内では液化状態にあり，両冷媒間での熱交
換は殆ど行われない。輻射パネルの上端の連結管を通過
する間に熱交換して蒸発した冷媒と，室内熱交換器で室
内空気と熱交換して蒸発した冷媒とは圧縮機に吸入さ
れ，上記の冷凍サイクルを繰り返して対流冷房と輻射冷
房とが行われる。一方，暖房運転時においては，圧縮機
から吐出された高温高圧の冷媒は室内熱交換器で室内に
放熱すると共に，輻射パネルの下端の連結管内を通る間
に輻射パネルのヒートパイプ内の冷媒を加熱して蒸発さ
せる。蒸発した冷媒はヒートパイプを上昇する間に凝縮
し，輻射パネルを暖め輻射暖房が行われ，凝縮した冷媒
は自然落下して下端の連結管に戻り，再び蒸発するサイ
クルを繰り返す。輻射パネルで凝縮した冷媒は，第１の
膨張弁で気液二相状態になって室外熱交換器に至り，外
気と熱交換して蒸発気化し低温低圧の蒸気となって圧縮
機に吸入され，上記サイクルを繰り返して対流暖房と輻
射暖房とが行われる。According to the present invention, while performing air conditioning by forced convection of the indoor heat exchanger in the refrigeration cycle, a heat pipe in the radiation panel is operated by using a part of the refrigerant flowing in the refrigeration cycle to radiate the heat. Air conditioning is performed by. First, during the cooling operation, the expansion coefficient by the second expansion valve is set lower than the expansion coefficient by the first expansion valve, and a part of the refrigerant condensed and liquefied by the outdoor heat exchanger is branched to generate the second expansion valve. When passing through the expanded portion into the connecting pipe at the upper end of the radiant panel, the radiant panel absorbs heat in the room to evaporate and condense the refrigerant in the heat pump of the radiant panel moving to the upper connect pipe side. Liquefy. The liquefied refrigerant naturally falls in the heat pipe, accumulates at the lower end of the connecting pipe, and repeats the cycle of being evaporated again by the heat collection of the radiation panel. The radiation panel is cooled by this cycle of evaporation and liquefaction, and the room is radiantly cooled. The refrigerant condensed and liquefied in the outdoor heat exchanger also flows to the first expansion valve side, passes through the inside of the connecting pipe at the lower end of the radiation panel, and enters the indoor heat exchanger.
Cooling is performed by forced convection of the indoor fan. When the refrigerant passes through the connecting pipe at the lower end, the refrigerant in the radiation panel is in a liquefied state in the connecting pipe at the lower end, and heat exchange between the two refrigerants is hardly performed. The refrigerant that has undergone heat exchange and vaporization while passing through the connecting pipe at the upper end of the radiation panel and the refrigerant that has undergone heat exchange with indoor air in the indoor heat exchanger are sucked into the compressor, and the above refrigeration cycle is repeated. And convection cooling and radiation cooling are performed. On the other hand, during the heating operation, the high-temperature and high-pressure refrigerant discharged from the compressor radiates heat to the room by the indoor heat exchanger, and at the same time, the refrigerant in the heat pipe of the radiation panel is discharged while passing through the connecting pipe at the lower end of the radiation panel. Heat to evaporate. The evaporated refrigerant condenses while rising the heat pipe, warms the radiant panel and performs radiant heating, and the condensed refrigerant spontaneously falls back to the lower connecting pipe and repeats the cycle of evaporating again. The refrigerant condensed in the radiation panel enters the outdoor heat exchanger in a gas-liquid two-phase state by the first expansion valve, exchanges heat with the outside air to evaporate into low-temperature low-pressure vapor, and is sucked into the compressor. By repeating the above cycle, convection heating and radiant heating are performed.
【０００７】[0007]
【実施例】以下添付図面を参照して，本発明を具体化し
た実施例につき説明し，本発明の理解に供する。尚，以
下の実施例は本発明を具体化した一例であって，本発明
の技術的範囲を限定するものではない。まず，本発明の
第１実施例について説明する。ここに，図１は本発明の
第１実施例空気調和機の概略構成図，図２は輻射パネル
の構成を示す斜視図，図３は制御手順を示すフローチャ
ートである。図１において，圧縮機１，四方弁１０，室
外熱交換器２，第１の膨張弁７，室内熱交換器３が接続
されて冷凍サイクルが構成されている。この冷凍サイク
ルの前記第１の膨張弁７と室内熱交換器３との間に，輻
射パネル４の下ヘッダー管２２内を貫通する加熱用冷媒
管２４が配されている。さらに，前記室外熱交換器２と
第１の膨張弁７との間から分岐した配管が，第２の膨張
弁５，輻射パネル４の上ヘッダー管２１内を貫通する冷
却用冷媒管２３，第３の膨張弁６を経て，四方弁１０か
ら圧縮機１に接続されている。同図において，実線矢印
は冷房運転時の冷媒の流れを示し，点線矢印は暖房運転
時の冷媒の流れを示しており，この流れ方向は四方弁１
０の切替えによりなされる。上記冷凍サイクルにおける
要所に温度センサが配され，それぞれ制御器１１に入力
される。２７は室外熱交換器冷媒入口温度センサ，２６
は室外熱交換器冷媒出口温度センサ，１６は室内熱交換
器冷媒入口温度センサ，１７は室内熱交換器冷媒出口温
度センサ，１４は輻射パネル入口温度センサ，１５は輻
射パネル出口温度センサ，１３は室内露点温度センサ，
１２は輻射パネル表面温度センサである。また，８は室
外ファン，９は室内ファンである。図２は前記輻射パネ
ル４の構造を示し，輻射パネル４を裏面から見た斜視図
である。同図に示されるように，表面パネル１８の裏部
に複数のヒートパイプ１９が垂直方向に接合板２０によ
り取り付けられており，各ヒートパイプ１９の上端には
上ヘッダー管２１，下端には下ヘッダー管２２が接続さ
れ，各ヒートパイプ１９が上端，下端で連結される。さ
らに，上ヘッダー管２１には冷却用冷媒管２３，下ヘッ
ダー管２２には加熱用冷媒管２４が貫通装着され，各ヒ
ートパイプ１９及び上ヘッダー管２１，下ヘッダー管２
２は気密接合され，フロン等のヒートパイプ冷媒２５が
封入される。冷却用冷媒管２３及び加熱用冷媒管２４は
前記の如く冷凍サイクルの所定位置に接続され，冷媒が
流通する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the accompanying drawings for the understanding of the present invention. The following embodiments are examples of embodying the present invention and do not limit the technical scope of the present invention. First, a first embodiment of the present invention will be described. 1 is a schematic configuration diagram of the air conditioner of the first embodiment of the present invention, FIG. 2 is a perspective view showing the configuration of a radiation panel, and FIG. 3 is a flowchart showing a control procedure. In FIG. 1, a compressor 1, a four-way valve 10, an outdoor heat exchanger 2, a first expansion valve 7, and an indoor heat exchanger 3 are connected to form a refrigeration cycle. Between the first expansion valve 7 and the indoor heat exchanger 3 of this refrigeration cycle, a heating refrigerant pipe 24 penetrating the lower header pipe 22 of the radiation panel 4 is arranged. Further, a pipe branched from between the outdoor heat exchanger 2 and the first expansion valve 7 passes through the second expansion valve 5, the upper header pipe 21 of the radiation panel 4, and the cooling refrigerant pipe 23, The four-way valve 10 is connected to the compressor 1 via the expansion valve 6 of No. 3. In the figure, solid arrows indicate the flow of the refrigerant during the cooling operation, and dotted arrows indicate the flow of the refrigerant during the heating operation.
It is done by switching 0. Temperature sensors are arranged at important points in the refrigeration cycle and are input to the controller 11, respectively. 27 is an outdoor heat exchanger refrigerant inlet temperature sensor, 26
Is an outdoor heat exchanger refrigerant outlet temperature sensor, 16 is an indoor heat exchanger refrigerant inlet temperature sensor, 17 is an indoor heat exchanger refrigerant outlet temperature sensor, 14 is a radiant panel inlet temperature sensor, 15 is a radiant panel outlet temperature sensor, and 13 is Indoor dew point temperature sensor,
Reference numeral 12 is a radiation panel surface temperature sensor. Further, 8 is an outdoor fan, and 9 is an indoor fan. FIG. 2 shows the structure of the radiation panel 4, and is a perspective view of the radiation panel 4 seen from the back side. As shown in the figure, a plurality of heat pipes 19 are vertically attached to the back portion of the front panel 18 by a joining plate 20, and each heat pipe 19 has an upper header pipe 21 at the upper end and a lower end at the lower end. The header pipe 22 is connected, and each heat pipe 19 is connected at the upper end and the lower end. Further, a cooling refrigerant pipe 23 is penetratingly mounted on the upper header pipe 21, and a heating refrigerant pipe 24 is penetratingly mounted on the lower header pipe 22, and each heat pipe 19 and the upper header pipe 21 and the lower header pipe 2 are attached.
2 is airtightly joined, and a heat pipe refrigerant 25 such as CFC is enclosed. The cooling refrigerant pipe 23 and the heating refrigerant pipe 24 are connected to the predetermined positions of the refrigeration cycle as described above, and the refrigerant flows therein.
【０００８】上記構成になる空気調和機の動作を以下に
説明する。まず，室内熱交換器３による冷房・除湿と，
輻射パネル４による冷房を同時に行う対流・輻射冷房時
について説明する。このとき第２膨張弁７の膨張率が第
１膨張弁５の膨張率より低くなるように制御されてい
る。圧縮機１から吐出された高温高圧の冷媒は，四方弁
１０から室外熱交換器２に入り，室外ファン８によって
駆動された外気と熱交換して放熱し凝縮液化する。室外
熱交換器２を出た冷媒は，第１の膨張弁７と第２の膨張
弁５とに分岐して輻射パネル４内に流入するが，それぞ
れの流入量は後述する各膨張弁５，６，７の制御によっ
て決定される。第２の膨張弁５に流入した冷媒は，減圧
されて気液二相状態となって輻射パネル４の冷却用冷媒
管２３を通過する。輻射パネル４においては，表面パネ
ル１８の輻射及び自然対流により室内から集熱して，ヒ
ートパイプ１９内のヒートパイプ冷媒２５が蒸発し，上
ヘッダー管２１側に移動しているので，上ヘッダー管２
１内の冷却用冷媒管２３を通過する冷媒により蒸発した
ヒートパイプ冷媒２５は凝縮され，自然落下して下ヘッ
ダー管２２側に溜まり，再び表面パネル１８の集熱によ
って蒸発するサイクルを繰り返す。この蒸発，凝縮のサ
イクルにより輻射パネル４は冷却され，輻射冷房を行
う。冷却用冷媒管２３で蒸発した冷媒は，第３の膨張弁
６で減圧され四方弁１０を通って圧縮機１に吸入され
る。The operation of the air conditioner having the above structure will be described below. First, cooling and dehumidification by the indoor heat exchanger 3,
A convection / radiant cooling operation in which cooling is performed by the radiation panel 4 at the same time will be described. At this time, the expansion rate of the second expansion valve 7 is controlled to be lower than the expansion rate of the first expansion valve 5. The high-temperature and high-pressure refrigerant discharged from the compressor 1 enters the outdoor heat exchanger 2 through the four-way valve 10, exchanges heat with the outside air driven by the outdoor fan 8, radiates heat, and is condensed and liquefied. The refrigerant discharged from the outdoor heat exchanger 2 branches into the first expansion valve 7 and the second expansion valve 5 and flows into the radiant panel 4. It is determined by the control of 6, 7. The refrigerant that has flowed into the second expansion valve 5 is decompressed into a gas-liquid two-phase state and passes through the cooling refrigerant pipe 23 of the radiation panel 4. In the radiation panel 4, heat is collected from the room by radiation from the front panel 18 and natural convection, and the heat pipe refrigerant 25 in the heat pipe 19 is evaporated and moved to the upper header pipe 21 side.
The heat pipe refrigerant 25 evaporated by the refrigerant passing through the cooling refrigerant pipe 23 in 1 is condensed, spontaneously falls and collects on the lower header pipe 22 side, and the cycle of evaporating again by the heat collection of the surface panel 18 is repeated. The radiation panel 4 is cooled by this cycle of evaporation and condensation to perform radiation cooling. The refrigerant evaporated in the cooling refrigerant pipe 23 is decompressed by the third expansion valve 6 and is sucked into the compressor 1 through the four-way valve 10.
【０００９】一方，第１の膨張弁７に流入した冷媒は，
減圧されて気液二相状態となって輻射パネル４の加熱用
冷媒管２４を通過する。加熱用冷媒管２４が貫通する下
ヘッダー管２２においては，ヒートパイプ冷媒２５が液
状態で溜まっているため，この間での熱交換は殆ど行わ
れず，冷媒は室内熱交換器３にそのまま流入し，室内フ
ァン９によって駆動された室内空気と熱交換して蒸発気
化し，低温低圧の蒸気となって四方弁１０を通り圧縮機
１に吸入される。このとき，室内空気は強制対流により
冷却され冷房・除湿が行われる。上記冷房運転時におけ
る各膨張弁５，６，７の制御手順を，図３に示すフロー
チャートを用いて説明する。同図におけるＳ１〜Ｓ１９
は制御手順を示すステップである。各膨張弁５，６，７
の駆動はステッピングモータで行われ，制御器１１によ
り制御される。最初に各膨張弁５，６，７は初期化のた
め全閉にした後（Ｓ１），各膨張弁５，６，７を冷房運
転に適した初期弁開度にする（Ｓ２）。次に膨張弁制御
に必要な要所の温度データを測定する（Ｓ３）。測定デ
ータは，室内熱交換器冷媒入口温度Ｔhexi，室内熱交換
器冷媒出口温度Ｔhexo，輻射パネル冷媒入口温度Ｔpi，
輻射パネル冷媒出口温度Ｔpo，輻射パネル表面温度Ｔp
s，室内空気露点温度Ｔadの６点である。次に輻射パネ
ル４による輻射冷房の可否を判断する。結露を防ぐため
には，輻射パネル表面温度Ｔpsが室内空気露点温度Ｔad
より高いことが必要であるが，室内の温湿度分布，測定
精度を考慮して，Ｓ４において輻射パネル表面温度Ｔps
と室内空気露点温度Ｔadの温度差が２℃より高い場合
は，輻射パネル４による輻射冷房を行い，温度差が２℃
以下の場合は，Ｓ６に示すように第２の膨張弁５及び第
３の膨張弁６を全閉とし，室内熱交換器３によって除湿
運転が進み，前記Ｓ４の条件が満たされるので輻射冷房
は行われない。輻射冷房を開始する場合には，第２の膨
張弁５及び第３の膨張弁６の状態を調べた後（Ｓ５），
第２の膨張弁５，第３の膨張弁６を初期開度とする（Ｓ
８）。On the other hand, the refrigerant flowing into the first expansion valve 7 is
It is decompressed to become a gas-liquid two-phase state and passes through the heating refrigerant pipe 24 of the radiation panel 4. In the lower header pipe 22 through which the heating refrigerant pipe 24 penetrates, since the heat pipe refrigerant 25 is accumulated in a liquid state, heat exchange is hardly performed during this time, and the refrigerant flows into the indoor heat exchanger 3 as it is. The heat is exchanged with the indoor air driven by the indoor fan 9 to evaporate and vaporize into low-temperature low-pressure vapor, which is sucked into the compressor 1 through the four-way valve 10. At this time, the indoor air is cooled by forced convection to cool and dehumidify. The control procedure of the expansion valves 5, 6, 7 during the cooling operation will be described with reference to the flowchart shown in FIG. S1 to S19 in FIG.
Is a step showing a control procedure. Expansion valves 5, 6, 7
Is driven by a stepping motor and controlled by the controller 11. First, each expansion valve 5, 6, 7 is fully closed for initialization (S1), and then each expansion valve 5, 6, 7 is set to an initial valve opening degree suitable for cooling operation (S2). Next, temperature data of the essential points required for expansion valve control are measured (S3). The measured data are the indoor heat exchanger refrigerant inlet temperature Thexi, the indoor heat exchanger refrigerant outlet temperature Thexo, the radiation panel refrigerant inlet temperature Tpi,
Radiant panel refrigerant outlet temperature Tpo, Radiant panel surface temperature Tp
s and room air dew point temperature Tad are 6 points. Next, it is determined whether or not the radiation cooling by the radiation panel 4 is possible. In order to prevent dew condensation, the radiation panel surface temperature Tps is set to the indoor air dew point temperature Tad.
Although it needs to be higher, the radiation panel surface temperature Tps in S4 in consideration of the temperature and humidity distribution in the room and the measurement accuracy.
If the temperature difference between the indoor air dew point temperature Tad and the room air dew point temperature is higher than 2 ° C, the radiation panel 4 is used to perform radiant cooling, and
In the following cases, as shown in S6, the second expansion valve 5 and the third expansion valve 6 are fully closed, the dehumidifying operation proceeds by the indoor heat exchanger 3, and the condition of S4 is satisfied, so that the radiation cooling is performed. Not done When the radiation cooling is started, after checking the states of the second expansion valve 5 and the third expansion valve 6 (S5),
The second expansion valve 5 and the third expansion valve 6 are set to the initial opening (S
8).
【００１０】次に，輻射パネル冷媒出口温度Ｔpo，輻射
パネル冷媒入口温度Ｔpiの温度差が５℃より大きい場合
（Ｓ７），第２の膨張弁５の弁開度を大きくし（Ｓ
９），輻射パネル冷媒出口温度Ｔpo，輻射パネル冷媒入
口温度Ｔpiの温度差が２℃より小さい場合（Ｓ１０），
第２の膨張弁５の弁開度を小さくする（Ｓ１１）。次
に，第３の膨張弁６の制御を行う。結露を防ぐために第
３の膨張弁６は，輻射パネル表面温度Ｔps，室内空気露
点温度Ｔadによって制御される。制御条件は，室内の温
湿度分布，測定精度を考慮し，輻射パネル表面温度Ｔps
と室内空気露点温度Ｔadの温度差が５℃より高いとき
（Ｓ１２），第３の膨張弁６の弁開度を大きくし（Ｓ１
３），温度差が３℃より低いときには（Ｓ１４），第３
の膨張弁６の弁開度を小さくする（Ｓ１５）。次いで，
第１の膨張弁７の制御を行う。室内熱交換器冷媒出口温
度Ｔhexoと室内熱交換器冷媒入口温度Ｔhexiの温度差が
５℃より高いときは（Ｓ１６），第１の膨張弁７の弁開
度を大きくし（Ｓ１８），温度差が３℃より低くなると
（Ｓ１７），第１の膨張弁７の弁開度を小さくする（Ｓ
１９）。以上のように，第１の膨張弁７は室内熱交換器
３の過熱度（室内熱交換器冷媒出口温度−室内熱交換器
冷媒入口温度）によって制御するが，第２の膨張弁５は
輻射パネル４の冷媒出口の過熱度によって，輻射パネル
４の冷却用冷媒管２３を流れる冷媒の流量を制御してい
る。また，第３の膨張弁６は輻射パネル４の冷却用冷媒
管２３を流れる冷媒の温度を制御している。Next, when the temperature difference between the radiant panel refrigerant outlet temperature Tpo and the radiant panel refrigerant inlet temperature Tpi is larger than 5 ° C. (S7), the opening degree of the second expansion valve 5 is increased (S).
9), if the temperature difference between the radiation panel refrigerant outlet temperature Tpo and the radiation panel refrigerant inlet temperature Tpi is less than 2 ° C. (S10),
The valve opening degree of the second expansion valve 5 is reduced (S11). Next, the third expansion valve 6 is controlled. In order to prevent dew condensation, the third expansion valve 6 is controlled by the radiation panel surface temperature Tps and the room air dew point temperature Tad. The control conditions are the radiation panel surface temperature Tps considering the temperature and humidity distribution in the room and the measurement accuracy.
And the indoor air dew point temperature Tad is higher than 5 ° C. (S12), the valve opening degree of the third expansion valve 6 is increased (S1).
3), when the temperature difference is lower than 3 ° C (S14), the third
The valve opening degree of the expansion valve 6 is reduced (S15). Then,
The first expansion valve 7 is controlled. When the temperature difference between the indoor heat exchanger refrigerant outlet temperature Thexo and the indoor heat exchanger refrigerant inlet temperature Thexi is higher than 5 ° C (S16), the valve opening degree of the first expansion valve 7 is increased (S18), and the temperature difference is increased. Is lower than 3 ° C. (S17), the valve opening degree of the first expansion valve 7 is reduced (S17).
19). As described above, the first expansion valve 7 is controlled by the degree of superheat of the indoor heat exchanger 3 (indoor heat exchanger refrigerant outlet temperature-indoor heat exchanger refrigerant inlet temperature), while the second expansion valve 5 radiates. The superheat degree of the refrigerant outlet of the panel 4 controls the flow rate of the refrigerant flowing through the cooling refrigerant pipe 23 of the radiation panel 4. Further, the third expansion valve 6 controls the temperature of the refrigerant flowing through the cooling refrigerant pipe 23 of the radiation panel 4.
【００１１】次に，暖房運転時の動作について説明す
る。暖房運転時に冷媒の流れは，図１に点線の矢印で示
される。圧縮機１から吐出された高温高圧の冷媒は，四
方弁１０から室内熱交換器３に入り，室内ファン９によ
って駆動された室内空気と熱交換して放熱し，対流暖房
が行われる。室内熱交換器３を出た冷媒は，輻射パネル
４の加熱用冷媒管２４を通過するときに，下ヘッダー管
２２に溜まっているヒートパイプ冷媒２５を加熱し蒸発
させる。蒸発したヒートパイプ冷媒２５は，ヒートパイ
プ１９内を上昇する間に表面パネル１８から放熱して凝
縮し，下ヘッダー管２２に自然落下して戻り，再び蒸発
することを繰り返す。このとき表面パネル１８からの放
熱により輻射暖房が行われる。室内熱交換器３及び輻射
パネル４で凝縮した冷媒は，第１の膨張弁７で低圧の気
液二相状態となって室外熱交換器２に入り，室外ファン
８によって駆動された外気と熱交換して蒸発気化し，低
温低圧の蒸気となって四方弁１０を通って圧縮機１に吸
入される。暖房運転時の冷凍サイクルの制御は，室外熱
交換器冷媒出口温度センサ２６により室外熱交換器２の
冷媒蒸発温度を検知し，室外熱交換器冷媒入口温度セン
サ２７により冷媒出口温度を検知して冷媒過熱度を求
め，第１の膨張弁７を制御して室外熱交換器２から流出
する冷媒の過熱度を調節する。次いで，本発明の第２実
施例について説明する。ここに，図４は実施例空気調和
機の概略構成図，図５は運転状態を示す圧力−エンタル
ピ線図，図６は制御手順を示すフローチャートである。
図４において，圧縮機５１，室外熱交換器５２，開閉弁
６７，第１の膨張弁５７，室内熱交換器５３が順次連結
された冷凍サイクルを構成すると共に，前記開閉弁６７
を迂回して第２の膨張弁５６，輻射パネル５４，気液分
離器５５が接続され，気液分離器５５の気層部５５a は
第３の膨張弁を介して圧縮機５１に接続されている。気
液分離器５５には液面センサ６２が配され，その検出値
は制御器６１に入力される。Next, the operation during the heating operation will be described. The flow of the refrigerant during the heating operation is shown by a dotted arrow in FIG. The high-temperature and high-pressure refrigerant discharged from the compressor 1 enters the indoor heat exchanger 3 through the four-way valve 10, exchanges heat with the indoor air driven by the indoor fan 9 to radiate heat, and convection heating is performed. When the refrigerant exiting the indoor heat exchanger 3 passes through the heating refrigerant pipe 24 of the radiant panel 4, it heats and evaporates the heat pipe refrigerant 25 accumulated in the lower header pipe 22. The evaporated heat pipe refrigerant 25 radiates heat from the front panel 18 and condenses while rising in the heat pipe 19, spontaneously falls back to the lower header pipe 22, returns, and evaporates again. At this time, radiant heating is performed by heat radiation from the front panel 18. The refrigerant condensed in the indoor heat exchanger 3 and the radiant panel 4 enters the outdoor heat exchanger 2 in a low-pressure gas-liquid two-phase state by the first expansion valve 7 and is heated by the outdoor fan 8 and the outside air. It is exchanged and vaporized to become low-temperature and low-pressure vapor, which is sucked into the compressor 1 through the four-way valve 10. In the control of the refrigeration cycle during the heating operation, the outdoor heat exchanger refrigerant outlet temperature sensor 26 detects the refrigerant evaporation temperature of the outdoor heat exchanger 2, and the outdoor heat exchanger refrigerant inlet temperature sensor 27 detects the refrigerant outlet temperature. The degree of superheat of the refrigerant is obtained, and the first expansion valve 7 is controlled to adjust the degree of superheat of the refrigerant flowing out of the outdoor heat exchanger 2. Next, a second embodiment of the present invention will be described. Here, FIG. 4 is a schematic configuration diagram of the air conditioner of the embodiment, FIG. 5 is a pressure-enthalpy diagram showing an operating state, and FIG. 6 is a flowchart showing a control procedure.
In FIG. 4, a compressor 51, an outdoor heat exchanger 52, an opening / closing valve 67, a first expansion valve 57, and an indoor heat exchanger 53 constitute a refrigeration cycle, and the opening / closing valve 67 is formed.
The second expansion valve 56, the radiant panel 54, and the gas-liquid separator 55 are connected to bypass the air-conditioner, and the gas layer 55 a of the gas-liquid separator 55 is connected to the compressor 51 via the third expansion valve. ing. A liquid level sensor 62 is arranged in the gas-liquid separator 55, and the detected value is input to the controller 61.
【００１２】また，各要所には温度センサが配置され，
それぞれの検出温度は制御器６１に入力される。６３は
輻射パネル表面温度センサ，６４は室内露点温度セン
サ，６５は室内熱交換器冷媒入口温度センサ，６６は室
内熱交換器冷媒出口温度センサである。上記構成におけ
る室内熱交換器５３による対流冷房・除湿及び輻射パネ
ル５４による輻射冷房を同時に行う場合について説明す
る。まず，開閉弁６７は閉じた状態にする。圧縮機５１
から吐出された高温高圧の冷媒は室外熱交換器５２に入
り，室外ファン５９によって駆動される外気と熱交換し
て放熱し，凝縮液化したのち第２の膨張弁５６に入る。
第２の膨張弁５６で減圧され気液二相状態となった冷媒
は，輻射パネル５４に流入し，輻射パネル５４の表面で
輻射及び自然対流により室内から集熱し，冷媒の乾き度
（冷媒蒸気の質量／蒸気と液を合計した冷媒質量）が増
加する。輻射パネル５４から出た気液二相状態の冷媒は
気液分離器５５に流入し，冷媒は気層部５５a と液層部
５５b とに分離される。気液分離器５５の液層部５５b
から流出する冷媒液は，第１の膨張弁５７で減圧され，
気液二層状態となって室内熱交換器５３に入り，室内フ
ァン６０によって駆動される室内空気と熱交換して蒸発
気化し，低温低圧の蒸気となって圧縮機５１に吸入され
る。一方，気液分離器５５の気層部５５a から流出する
冷媒蒸気は第３の膨張弁５８により減圧され，圧縮機５
１に吸入される。A temperature sensor is arranged at each important point,
Each detected temperature is input to the controller 61. 63 is a radiation panel surface temperature sensor, 64 is an indoor dew point temperature sensor, 65 is an indoor heat exchanger refrigerant inlet temperature sensor, and 66 is an indoor heat exchanger refrigerant outlet temperature sensor. A case where convection cooling / dehumidification by the indoor heat exchanger 53 and radiant cooling by the radiant panel 54 are simultaneously performed in the above configuration will be described. First, the on-off valve 67 is closed. Compressor 51
The high-temperature and high-pressure refrigerant discharged from the outside enters the outdoor heat exchanger 52, exchanges heat with the outside air driven by the outdoor fan 59 to radiate heat, and is condensed and liquefied, and then enters the second expansion valve 56.
The refrigerant that has been decompressed by the second expansion valve 56 and has become a gas-liquid two-phase state flows into the radiation panel 54 and collects heat from the room by radiation and natural convection on the surface of the radiation panel 54, and the dryness of the refrigerant (refrigerant vapor). Mass / refrigerant mass that is the sum of vapor and liquid) increases. Gas-liquid two-phase refrigerant exiting the radiant panel 54 flows into the gas-liquid separator 55, the refrigerant is separated into a Kiso portion 55 a and the liquid layer portion 55 b. Liquid layer portion 55 b of the gas-liquid separator 55
The refrigerant liquid flowing out from the first expansion valve 57 is decompressed,
The gas-liquid two-layer state enters the indoor heat exchanger 53, heat-exchanges with the indoor air driven by the indoor fan 60 to evaporate, and becomes low-temperature and low-pressure vapor, which is sucked into the compressor 51. On the other hand, the refrigerant vapor flowing out from the gas layer 55 a of the gas-liquid separator 55 is decompressed by the third expansion valve 58, and the compressor 5
Inhaled to 1.
【００１３】上記冷凍サイクルにより，輻射パネル５４
で輻射冷房がなされ，室内熱交換器５３で対流冷房及び
除湿が行われる。このときの運転状態を圧力−エンタル
ピ線図に示すと，図５のようになる。行程Ａ−Ｂは圧縮
機５１の圧縮過程，行程Ｂ−Ｃは室外熱交換器５２の凝
縮過程，行程Ｃ−Ｄは第２の膨張弁５６の減圧過程，行
程Ｄ−Ｅは輻射パネル５４の蒸発過程，行程Ｅ−Ｆは気
液分離器５５での液への分離，行程Ｅ−Ｇは気液分離器
５５での気体への分離，行程Ｆ−Ｈは第１の膨張弁５７
の減圧過程，行程Ｈ−Ｉは室内熱交換器５３の蒸発過
程，行程Ｇ−Ｊは第３の膨張弁５８の減圧過程である。
輻射パネル５４の表面温度が室内露点温度より低くなる
恐れがある場合，室内熱交換器５３のみで冷房・除湿を
行う。このときには，開閉弁６７を開き，第２の膨張弁
５６及び第３の膨張弁５８は全閉とする。従って，室外
熱交換器５２から出た冷媒は，開閉弁６７から第１の膨
張弁５７に入り，減圧されて低温になった後，室内熱交
換器５３で蒸発し，対流冷房が行われる。次に制御手順
を図６のフローチャートを用いて説明する。同図におけ
るＳ１〜Ｓ１９は制御手順を示すステップである。ま
ず，最初に各膨張弁５６，５７，５８を初期化するため
全閉にし，開閉弁６７を閉じる（Ｓ１）。次に各膨張弁
５６，５７，５８を各々に適した初期弁開度にし（Ｓ
２），膨張弁制御に必要な各センサのデータを測定する
（Ｓ３）。測定データは，室内熱交換器冷媒入口温度Ｔ
hexi，室内熱交換器冷媒出口温度Ｔhexo，輻射パネル表
面温度Ｔps，室内空気露点温度Ｔad，気液分離器液面高
さＨslの５点である。By the above refrigeration cycle, the radiation panel 54
The radiant cooling is carried out, and the indoor heat exchanger 53 performs convective cooling and dehumidification. The operating state at this time is shown in the pressure-enthalpy diagram as shown in FIG. Steps A-B are the compression process of the compressor 51, steps B-C are the condensation process of the outdoor heat exchanger 52, steps C-D are the decompression process of the second expansion valve 56, and steps D-E are the radiation panel 54. Evaporation process, stroke E-F is separated into liquid in the gas-liquid separator 55, stroke E-G is separated into gas in the vapor-liquid separator 55, stroke F-H is the first expansion valve 57.
The decompression process, process H-I, is the evaporation process of the indoor heat exchanger 53, and process G-J is the decompression process of the third expansion valve 58.
When the surface temperature of the radiation panel 54 may be lower than the indoor dew point temperature, the indoor heat exchanger 53 alone is used for cooling and dehumidifying. At this time, the opening / closing valve 67 is opened, and the second expansion valve 56 and the third expansion valve 58 are fully closed. Therefore, the refrigerant discharged from the outdoor heat exchanger 52 enters the first expansion valve 57 from the opening / closing valve 67, is decompressed to a low temperature, and then is evaporated in the indoor heat exchanger 53 to perform convection cooling. Next, the control procedure will be described with reference to the flowchart of FIG. S1 to S19 in the figure are steps showing a control procedure. First, the expansion valves 56, 57 and 58 are fully closed to initialize them, and the on-off valve 67 is closed (S1). Next, each expansion valve 56, 57, 58 is set to an initial valve opening suitable for each (S
2) The data of each sensor required for expansion valve control is measured (S3). The measurement data is the indoor heat exchanger refrigerant inlet temperature T
hexi, indoor heat exchanger refrigerant outlet temperature Thexo, radiation panel surface temperature Tps, indoor air dew point temperature Tad, and gas-liquid separator liquid level height Hsl.
【００１４】次に，輻射パネル５４による冷房運転の可
否を判断する。結露を防ぐためには，輻射パネル表面温
度Ｔpsが室内空気露点温度Ｔadより高いことが必要であ
るが，室内の温湿度分布，測定精度を考慮し，Ｓ４に示
すように輻射パネル表面温度Ｔpsと室内空気露点温度Ｔ
adとの温度差が２℃より高い場合は，輻射パネル５４に
よる輻射冷房を実施し，前記温度差が２℃以下の場合
は，Ｓ６に示すように第２の膨張弁５６，第３の膨張弁
５８を全閉とし，開閉弁６７を開として，室内熱交換器
５３によって除湿運転が進み，前記Ｓ４の条件が満たさ
れるまで輻射冷房は行わない。輻射冷房を開始する場合
は，Ｓ５に示すように第２の膨張弁５６，第３の膨張弁
５８，開閉弁６７の状態を調べた後，Ｓ８に示すように
第２の膨張弁５６及び第３の膨張弁５８を初期開度，開
閉弁６７を閉とする。次に，Ｓ７に示すように気液分離
器液面高さＨslが下限値より小さい場合，Ｓ９のように
第２の膨張弁５６の弁開度を大きくし，Ｓ１０に示すよ
うに気液分離器液面高さＨslが上限より大きい場合，Ｓ
１１のように第２の膨張弁５６の弁開度を小さくする。
次に，第３の膨張弁５８の制御を行う。結露を防ぐため
に第３の膨張弁５８は，輻射パネル表面温度Ｔps，室内
空気露点温度Ｔadによって制御される。制御条件は室内
の温湿度分布，測定精度を考慮し，Ｓ１２に示すように
輻射パネル表面温度Ｔpsと室内空気露点温度Ｔadとの温
度差が５℃より高いとき，第３の膨張弁５８の弁開度を
大きくし，Ｓ１４に示すように前記温度差が３℃より低
いときは，Ｓ１５のように第３の膨張弁５８の弁開度を
小さくする。次に，第１の膨張弁５７の制御を行う。Ｓ
１６に示すように室内熱交換器冷媒出口温度Ｔhexoと室
内熱交換器冷媒入口温度Ｔhexiとの温度差が５℃より高
いときは，Ｓ１７のように第１の膨張弁５７の弁開度を
大きくし，Ｓ１８に示すように前記温度差が３℃より低
くなると，第１の膨張弁５７の弁開度を小さくする。以
上のように，第１の膨張弁５７は室内熱交換器５３の過
熱度（室内熱交換器冷媒出口温度−室内熱交換器冷媒入
口温度）によって制御するが，第２の膨張弁５６は気液
分離器液面高さＨslによって，輻射パネル５４から流出
する冷媒の液相・気相の流量を制御している。また，第
３の膨張弁５８は輻射パネル５４の冷媒温度を制御して
いる。Next, it is determined whether or not the cooling operation by the radiation panel 54 is possible. In order to prevent dew condensation, the radiation panel surface temperature Tps needs to be higher than the indoor air dew point temperature Tad, but considering the temperature and humidity distribution in the room and the measurement accuracy, the radiation panel surface temperature Tps and the indoor temperature are measured as shown in S4. Air dew point temperature T
When the temperature difference with ad is higher than 2 ° C, the radiation cooling is performed by the radiation panel 54, and when the temperature difference is 2 ° C or lower, the second expansion valve 56 and the third expansion valve 56 are expanded as shown in S6. The valve 58 is fully closed, the open / close valve 67 is opened, the dehumidifying operation is advanced by the indoor heat exchanger 53, and the radiant cooling is not performed until the condition of S4 is satisfied. When starting the radiation cooling, after checking the states of the second expansion valve 56, the third expansion valve 58, and the opening / closing valve 67 as shown in S5, as shown in S8, the second expansion valve 56 and the The expansion valve 58 of No. 3 is set to the initial opening and the opening / closing valve 67 is closed. Next, as shown in S7, when the liquid level height Hsl of the gas-liquid separator is smaller than the lower limit value, the valve opening of the second expansion valve 56 is increased as in S9, and the gas-liquid separation is performed as shown in S10. When the liquid level height Hsl is larger than the upper limit, S
As indicated by 11, the valve opening degree of the second expansion valve 56 is reduced.
Next, the third expansion valve 58 is controlled. In order to prevent dew condensation, the third expansion valve 58 is controlled by the radiation panel surface temperature Tps and the room air dew point temperature Tad. As for the control condition, when the temperature difference between the radiation panel surface temperature Tps and the room air dew point temperature Tad is higher than 5 ° C., as shown in S12, the temperature of the humidity distribution in the room and the measurement accuracy are taken into consideration. When the opening is increased and the temperature difference is lower than 3 ° C. as shown in S14, the valve opening of the third expansion valve 58 is decreased as in S15. Next, the control of the first expansion valve 57 is performed. S
As shown in 16, when the temperature difference between the indoor heat exchanger refrigerant outlet temperature Thexo and the indoor heat exchanger refrigerant inlet temperature Thexi is higher than 5 ° C, the valve opening degree of the first expansion valve 57 is increased as in S17. However, when the temperature difference becomes lower than 3 ° C. as shown in S18, the valve opening degree of the first expansion valve 57 is reduced. As described above, the first expansion valve 57 is controlled by the degree of superheat of the indoor heat exchanger 53 (indoor heat exchanger refrigerant outlet temperature-indoor heat exchanger refrigerant inlet temperature), but the second expansion valve 56 is The liquid separator liquid level height Hsl controls the flow rates of the liquid phase and the gas phase of the refrigerant flowing out from the radiation panel 54. The third expansion valve 58 controls the refrigerant temperature of the radiation panel 54.
【００１５】[0015]
【発明の効果】以上の説明のように本発明によれば，冷
凍サイクルにおける輻射パネルを流れる冷媒の温度を変
化させ，室内空気の露点に応じた輻射パネルの表面温度
を得ることができ，従来例に示したブラインサイクルに
よる空気調和の課題であった省エネルギー性を大幅に改
善できる効果を奏する。また，本発明になるヒートパイ
プ式の輻射パネルによれば，輻射パネルを通過させる冷
媒管の長さを短くできるので，輻射パネルの面積を大き
くしても冷媒の封入量は少なく，さらに輻射パネルをユ
ニット化し，複数のユニットを接続することも可能とな
り，輻射による空気調和の効果を生かすことができる。As described above, according to the present invention, the temperature of the refrigerant flowing through the radiation panel in the refrigeration cycle can be changed to obtain the surface temperature of the radiation panel according to the dew point of the room air. It is possible to significantly improve the energy saving, which was a problem of air conditioning by the brine cycle shown in the example. Further, according to the heat pipe type radiation panel of the present invention, since the length of the refrigerant pipe that passes through the radiation panel can be shortened, even if the area of the radiation panel is increased, the amount of refrigerant enclosed is small, and the radiation panel is further reduced. It becomes possible to connect multiple units by connecting the unit to the air conditioning effect due to radiation.
【図１】 本発明の第１実施例に係る空気調和機の概略
構成図。FIG. 1 is a schematic configuration diagram of an air conditioner according to a first embodiment of the present invention.
【図２】 第１実施例に係る輻射パネルの構造を示す斜
視図。FIG. 2 is a perspective view showing the structure of a radiation panel according to the first embodiment.
【図３】 第１実施例空気調和機の制御手順を示すフロ
ーチャート。FIG. 3 is a flowchart showing a control procedure of the air conditioner of the first embodiment.
【図４】 本発明の第２実施例に係る空気調和機の概略
構成図。FIG. 4 is a schematic configuration diagram of an air conditioner according to a second embodiment of the present invention.
【図５】 第２実施例空気調和機の動作状態を示す圧力
−エンタルピ線図。FIG. 5 is a pressure-enthalpy diagram showing the operating state of the air conditioner of the second embodiment.
【図６】 第２実施例空気調和機の制御手順を示すフロ
ーチャート。FIG. 6 is a flowchart showing a control procedure of the air conditioner of the second embodiment.
【図７】 従来例空気調和機の概略構成図。FIG. 7 is a schematic configuration diagram of a conventional air conditioner.
１，５１…圧縮機 ２，５２…室外熱
交換器 ３，５３…室内熱交換器 ４，５４…輻射パ
ネル ５，５６…第２の膨張弁 ６，５８…第３の
膨張弁 ７，５７…第１の膨張弁 １９…ヒートパイ
プ ２１…上ヘッダー管（上端連結管） ２２…下ヘッダー管（下端連結管） ２３…冷却用冷媒管 ２４…加熱用冷媒管 ２５…ヒートパイプ冷媒1, 51 ... Compressor 2, 52 ... Outdoor heat exchanger 3, 53 ... Indoor heat exchanger 4, 54 ... Radiation panel 5, 56 ... Second expansion valve 6, 58 ... Third expansion valve 7, 57 ... First expansion valve 19 ... Heat pipe 21 ... Upper header pipe (upper end connecting pipe) 22 ... Lower header pipe (lower end connecting pipe) 23 ... Cooling refrigerant pipe 24 ... Heating refrigerant pipe 25 ... Heat pipe refrigerant
───────────────────────────────────────────────────── フロントページの続き (72)発明者 吉田 陽 大阪市阿倍野区長池町22番22号シヤープ株 式会社内 (72)発明者 小谷 正則 大阪市阿倍野区長池町22番22号シヤープ株 式会社内 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Yo Yoshida, 22-22 Nagaikecho, Naganocho, Abeno-ku, Osaka City (72) Inventor Masanori Otani 22-22, Nagaikecho, Abeno-ku, Osaka City, Sharp Corporation
Claims (1)
室内熱交換器を順次連結した冷凍サイクルにおける前記
室内熱交換器による対流空気調和と，前記冷凍サイクル
を流れる冷媒の一部を用いる輻射パネルによる輻射空気
調和とを行う空気調和機において，上記輻射パネルに垂
直方向の複数のヒートパイプを配設し，該ヒートパイプ
の上端及び下端を連結管で接続すると共に，所定量の冷
媒を充填し，前記下端の連結管に加熱用冷媒管を貫通さ
せて前記第１の膨張弁と前記室内熱交換器との間に配管
し，前記上端の連結管に冷却用冷媒管を貫通させて，該
冷却用冷媒管の一方を第２の膨張弁を介して前記室外熱
交換器に接続し，該冷却用冷媒管の他方を第３の膨張弁
を介して前記圧縮機に接続してなることを特徴とする空
気調和機。Claims: 1. A compressor, an outdoor heat exchanger, a first expansion valve,
An air conditioner that performs convective air conditioning by the indoor heat exchanger in a refrigeration cycle in which indoor heat exchangers are sequentially connected and radiant air conditioning by a radiant panel that uses a part of the refrigerant flowing in the refrigeration cycle, A plurality of heat pipes in the vertical direction are connected to each other, the upper and lower ends of the heat pipes are connected by connecting pipes, a predetermined amount of refrigerant is filled, and the heating pipes are inserted into the connecting pipes at the lower end. Piping is provided between the first expansion valve and the indoor heat exchanger, a cooling refrigerant pipe is passed through the connecting pipe at the upper end, and one of the cooling refrigerant pipes is passed through a second expansion valve. An air conditioner connected to the outdoor heat exchanger, wherein the other side of the cooling refrigerant pipe is connected to the compressor via a third expansion valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3193037A JP2599518B2 (en) | 1991-08-01 | 1991-08-01 | Air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3193037A JP2599518B2 (en) | 1991-08-01 | 1991-08-01 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0533969A true JPH0533969A (en) | 1993-02-09 |
| JP2599518B2 JP2599518B2 (en) | 1997-04-09 |
Family
ID=16301118
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3193037A Expired - Fee Related JP2599518B2 (en) | 1991-08-01 | 1991-08-01 | Air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2599518B2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100854153B1 (en) * | 2007-01-26 | 2008-08-26 | 엘지전자 주식회사 | air conditioning system |
| KR100854154B1 (en) * | 2007-01-26 | 2008-08-26 | 엘지전자 주식회사 | air conditioning system |
| KR101250192B1 (en) * | 2006-01-04 | 2013-04-05 | 엘지전자 주식회사 | A heating structure used air-conditioner |
| JP2013245832A (en) * | 2012-05-23 | 2013-12-09 | Sharp Corp | Radiant type air conditioner |
| WO2016039346A1 (en) * | 2014-09-12 | 2016-03-17 | シャープ株式会社 | Radiation-type air conditioner |
| CN106839198A (en) * | 2016-12-29 | 2017-06-13 | 湖北兴致天下信息技术有限公司 | A kind of cooling double loop water-cooled heat-pipe air-cooling air conditioner integrated machine of computer room |
| CN107477741A (en) * | 2017-09-12 | 2017-12-15 | 北京工业大学 | A kind of compound annual cooling down system of convertible mode of operation |
-
1991
- 1991-08-01 JP JP3193037A patent/JP2599518B2/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101250192B1 (en) * | 2006-01-04 | 2013-04-05 | 엘지전자 주식회사 | A heating structure used air-conditioner |
| KR100854153B1 (en) * | 2007-01-26 | 2008-08-26 | 엘지전자 주식회사 | air conditioning system |
| KR100854154B1 (en) * | 2007-01-26 | 2008-08-26 | 엘지전자 주식회사 | air conditioning system |
| JP2013245832A (en) * | 2012-05-23 | 2013-12-09 | Sharp Corp | Radiant type air conditioner |
| WO2016039346A1 (en) * | 2014-09-12 | 2016-03-17 | シャープ株式会社 | Radiation-type air conditioner |
| JP2016057040A (en) * | 2014-09-12 | 2016-04-21 | シャープ株式会社 | Radiation type air conditioner |
| CN106839198A (en) * | 2016-12-29 | 2017-06-13 | 湖北兴致天下信息技术有限公司 | A kind of cooling double loop water-cooled heat-pipe air-cooling air conditioner integrated machine of computer room |
| CN107477741A (en) * | 2017-09-12 | 2017-12-15 | 北京工业大学 | A kind of compound annual cooling down system of convertible mode of operation |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2599518B2 (en) | 1997-04-09 |
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