JP2003207231A - Air conditioner - Google Patents
Air conditionerInfo
- Publication number
- JP2003207231A JP2003207231A JP2002008540A JP2002008540A JP2003207231A JP 2003207231 A JP2003207231 A JP 2003207231A JP 2002008540 A JP2002008540 A JP 2002008540A JP 2002008540 A JP2002008540 A JP 2002008540A JP 2003207231 A JP2003207231 A JP 2003207231A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- orifice
- dehumidifying operation
- indoor heat
- during
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/38—Expansion means; Dispositions thereof specially adapted for reversible cycles, e.g. bidirectional expansion restrictors
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、空気調和機に係
り、特に冷房サイクル除湿運転及び暖房サイクル除湿運
転が可能な空気調和機に好適なものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner, and particularly to an air conditioner capable of performing a cooling cycle dehumidifying operation and a heating cycle dehumidifying operation.
【０００２】[0002]
【従来の技術】従来の空気調和機としては、圧縮機、四
方弁、室外熱交換器、冷暖房用絞り装置、室内熱交換
器、及び除湿用絞り装置等を配管で接続して冷凍サイク
ルを形成している。その四方弁は、圧縮機から出た冷媒
流を室外熱交換器から室内熱交換器に流す冷房サイクル
と、圧縮機から出た冷媒流を室内熱交換器から室外側熱
交換器の順に流す暖房サイクルとに切り換える機能を有
している。また、その冷暖房用絞り装置は室外熱交換器
と室内熱交換器との間に設けている。さらには、その室
内熱交換器は、第１の室内熱交換器と第２の室内熱交換
器とに分割している。また、除湿用絞り装置は電磁開閉
弁とこれと並列に接続した絞り流路とから構成し、除湿
運転時に絞り作用を行なうように第１の室内側熱交換器
と第２の室内側熱交換器との間に設けている。2. Description of the Related Art As a conventional air conditioner, a refrigeration cycle is formed by connecting a compressor, a four-way valve, an outdoor heat exchanger, a cooling / heating expansion device, an indoor heat exchanger, a dehumidification expansion device, etc. with piping. is doing. The four-way valve has a cooling cycle in which the refrigerant flow from the compressor is passed from the outdoor heat exchanger to the indoor heat exchanger, and a heating cycle in which the refrigerant flow from the compressor is passed from the indoor heat exchanger to the outdoor heat exchanger. It has the function of switching to cycle. The cooling / heating expansion device is provided between the outdoor heat exchanger and the indoor heat exchanger. Furthermore, the indoor heat exchanger is divided into a first indoor heat exchanger and a second indoor heat exchanger. Further, the dehumidifying expansion device is composed of an electromagnetic on-off valve and a throttle flow path connected in parallel with the electromagnetic opening / closing valve, and the first indoor heat exchanger and the second indoor heat exchanger are arranged to perform a throttling operation during dehumidification operation. It is provided between the bowl and the bowl.
【０００３】そして、四方弁等の切換により、冷房サイ
クルによる第２の室内熱交換器、除湿用絞り装置及び第
1の室内熱交換器の順に冷媒を流す冷房サイクル除湿運
転と、暖房サイクルによる第1の室内側熱交換器、除湿
用絞り装置及び第２の室内側熱交換器の順に冷媒を流す
暖房サイクル除湿運転とを行なうことができるものであ
る。Then, by switching the four-way valve or the like, the second indoor heat exchanger in the cooling cycle, the dehumidifying expansion device, and the second
Cooling cycle dehumidification operation in which refrigerant is flowed in the order of 1 indoor heat exchanger, and heating cycle dehumidification in which refrigerant is flowed in the order of the first indoor heat exchanger, dehumidifying expansion device and second indoor heat exchanger in the heating cycle It is capable of driving.
【０００４】係る従来技術に関連するものとしては、例
えば特開昭５４−４７３５３号公報や特開２００１−８
２７６１号公報などが挙げられる。As for those related to the related art, for example, JP-A-54-47353 and JP-A-2001-8 are available.
2761 publication etc. are mentioned.
【０００５】[0005]
【発明が解決しようとする課題】しかし、上述した従来
の空気調和機には、冷房サイクルによる冷房気味の除湿
運転と暖房サイクルによる暖房気味の除湿運転とを行な
えるようにして広い温度範囲で除湿運転できるようにす
ることが示されているが、冷房サイクル除湿運転時と暖
房サイクル除湿運転時の絞り抵抗の大きさを変えること
については開示されておらず、さらに広い温度範囲で除
湿運転を行なえるようにすることが課題となっていた。
例えば、暖房サイクル除湿運転時に絞り抵抗を大きくし
て蒸発温度を低くしないと、冬期に室外温度が低くなっ
た時などに室外側熱交換器で室外空気から十分に吸熱す
ることができず、第２室内側熱交換器の加熱能力を高く
して室内吹き出し空気温度を高く保つことができないこ
ととなり、快適な除湿運転が行なえないという課題があ
った。However, the above-described conventional air conditioner has a dehumidifying operation in a wide temperature range by performing a dehumidifying operation with a cooling effect in a cooling cycle and a dehumidifying operation with a heating effect in a heating cycle. Although it has been shown that it can be operated, it does not disclose changing the amount of throttling resistance during the cooling cycle dehumidifying operation and the heating cycle dehumidifying operation, and the dehumidifying operation can be performed in a wider temperature range. The task was to do so.
For example, if the throttling resistance is not increased to reduce the evaporation temperature during the heating cycle dehumidifying operation, the outdoor heat exchanger cannot sufficiently absorb heat from the outdoor air when the outdoor temperature becomes low in winter, (2) The heating capacity of the indoor heat exchanger cannot be increased to keep the temperature of the air blown indoors high, and there is a problem that a comfortable dehumidifying operation cannot be performed.
【０００６】本発明の目的は、冷房サイクル除湿運転及
び暖房サイクル除湿運転のそれぞれに適切な絞り抵抗と
して広い温度範囲で快適に除湿運転が可能な空気調和機
を提供することにある。An object of the present invention is to provide an air conditioner which can be comfortably dehumidified in a wide temperature range as a throttle resistance suitable for each of the cooling cycle dehumidifying operation and the heating cycle dehumidifying operation.
【０００７】なお、本発明の前記以外の目的と有利点は
以下の記述から明らかにされる。The objects and advantages of the present invention other than the above will be apparent from the following description.
【０００８】[0008]
【課題を解決するための手段】前記目的を達成するため
の本発明の空気調和機は、圧縮機、冷房サイクルと暖房
サイクルを切り換える運転切換弁、室外熱交換器、冷房
運転及び暖房運転の時に絞り作用を行なう第１の絞り装
置、第１の室内熱交換器と第２の室内熱交換器とに熱的
に二分割された室内熱交換器、及びこの二分割された室
内熱交換器の間に除湿運転時に絞り作用を行なう第２の
絞り装置を備え、前記室内熱交換器を蒸発器、前記室外
熱交換器を凝縮器とした冷房運転と、前記室内熱交換器
を凝縮器、前記室外熱交換器を蒸発器とした暖房運転
と、前記第１の室内熱交換器を蒸発器、前記第２の熱交
換器を凝縮器、前記室外熱交換器を凝縮器とした冷房サ
イクル除湿運転と、前記第１の室内熱交換器を凝縮器、
前記第２の室内熱交換器を蒸発器、前記室外熱交換器を
蒸発器とした暖房サイクル除湿運転とが可能な空気調和
機において、前記第２の絞り装置は電磁開閉弁と絞り流
路とを並列にした流路で構成し、前記電磁開閉弁は、前
記冷房運転時及び前記暖房運転時に開路し、前記冷房サ
イクル除湿運転時及び前記暖房サイクル除湿運転時に閉
路するように構成し、前記絞り流路は、管路に固定され
且つオリフィス穴を有する固定オリフィスと、冷媒の流
れによって移動可能で且つオリフィス穴を有する可動オ
リフィスとを備え、前記可動オリフィスの移動によって
前記固定オリフィスとの組み合わせ状態が変わり前記冷
房サイクル除湿運転時より前記暖房サイクル除湿運転時
の絞り抵抗が大きくなる構成としたことにある。The air conditioner of the present invention for achieving the above object includes a compressor, an operation switching valve for switching between a cooling cycle and a heating cycle, an outdoor heat exchanger, a cooling operation and a heating operation. A first expansion device that performs a throttling action, an indoor heat exchanger that is thermally divided into a first indoor heat exchanger and a second indoor heat exchanger, and an indoor heat exchanger that is divided into two. A second throttling device that performs a throttling action during a dehumidifying operation is provided between, and the cooling operation is performed using the indoor heat exchanger as an evaporator and the outdoor heat exchanger as a condenser, and the indoor heat exchanger as a condenser. Heating operation using the outdoor heat exchanger as an evaporator, cooling cycle dehumidifying operation using the first indoor heat exchanger as an evaporator, the second heat exchanger as a condenser, and the outdoor heat exchanger as a condenser And a condenser for the first indoor heat exchanger,
In an air conditioner capable of performing a heating cycle dehumidifying operation using the second indoor heat exchanger as an evaporator and the outdoor heat exchanger as an evaporator, the second throttle device includes an electromagnetic opening / closing valve and a throttle passage. In parallel flow path, the electromagnetic on-off valve is configured to open during the cooling operation and the heating operation, and configured to close during the cooling cycle dehumidifying operation and the heating cycle dehumidifying operation, the throttle The flow path includes a fixed orifice that is fixed to the pipeline and has an orifice hole, and a movable orifice that is movable by the flow of the refrigerant and that has an orifice hole. The movement of the movable orifice changes the combination state with the fixed orifice. Instead, the throttle resistance during the heating cycle dehumidifying operation is larger than that during the cooling cycle dehumidifying operation.
【０００９】なお、本発明のその他の手段は以下の記述
から明らかにされる。Other means of the present invention will be clarified from the following description.
【００１０】[0010]
【発明の実施の形態】以下、本発明の空気調和機の複数
の実施例を図を用いて説明する。なお、第２実施例以降
の実施例においては第１実施例と共通する構成の一部を
省略すると共に、重複する説明を省略する。各実施例の
図における同一符号は同一物または相当物を示す。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A plurality of embodiments of the air conditioner of the present invention will be described below with reference to the drawings. In addition, in the second and subsequent embodiments, a part of the configuration common to the first embodiment will be omitted, and redundant description will be omitted. The same reference numerals in the drawings of each embodiment indicate the same or equivalent parts.
【００１１】まず、本発明の第1実施例の空気調和機を
図１から図５を用いて説明する。図１は本発明の第１実
施例の空気調和機を示す冷凍サイクルの構成図、図２は
図１の空気調和機の冷房サイクル除湿運転時における第
２の絞り装置の断面概略図、図３は図１の空気調和機の
第２の絞り装置の暖房サイクル除湿運転時の断面概略
図、図４は図１の空気調和機の冷房サイクル除湿運転時
の圧力エントロピー線図、図５は図１の空気調和機の暖
房サイクル除湿運転時の圧力エントロピー線図である。First, an air conditioner according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 5. 1 is a configuration diagram of a refrigeration cycle showing an air conditioner of a first embodiment of the present invention, FIG. 2 is a schematic sectional view of a second expansion device during a cooling cycle dehumidifying operation of the air conditioner of FIG. 1, FIG. 1 is a schematic cross-sectional view of the second expansion device of the air conditioner of FIG. 1 during the heating cycle dehumidifying operation, FIG. 4 is a pressure entropy diagram during the cooling cycle dehumidifying operation of the air conditioner of FIG. 1, and FIG. FIG. 7 is a pressure entropy diagram during the heating cycle dehumidifying operation of the air conditioner.
【００１２】図１において、１は圧縮機、２は冷房サイ
クルと暖房サイクルを切り換える四方弁、３は室外熱交
換器、４は冷房運転及び暖房運転の時に絞り作用を行な
う電動膨張弁等の第１の絞り装置、５は第１の室内熱交
換器、６は第２の室内熱交換器、７は除湿運転時に絞り
作用を行なう第２の絞り装置、１０は双方向で全開と全
閉状態が切換可能な電磁開閉弁、１１は流れ方向で流路
抵抗が異なる絞り流路を示す。室内熱交換器は第１の室
内熱交換器５と第２の室内熱交換器６とに二分割して構
成されている。四方弁２で切り換える冷房サイクルと
は、図１の実線矢印に示すように冷媒を流すサイクルで
あり、冷房運転と冷房サイクル除湿運転のサイクルを構
成する。また、暖房サイクルとは、図１の点線矢印に示
すよう冷媒を流すサイクルであり、暖房運転と暖房サイ
クル除湿運転のサイクルを構成する。In FIG. 1, reference numeral 1 is a compressor, 2 is a four-way valve for switching between a cooling cycle and a heating cycle, 3 is an outdoor heat exchanger, 4 is a motor-operated expansion valve, etc., which performs a throttle action during cooling operation and heating operation. 1 throttling device, 5 a first indoor heat exchanger, 6 a second indoor heat exchanger, 7 a second throttling device that performs a throttling action during dehumidifying operation, 10 bidirectionally fully open and fully closed Is a switchable solenoid on-off valve, and 11 is a throttle channel having different channel resistances in the flow direction. The indoor heat exchanger is divided into two, a first indoor heat exchanger 5 and a second indoor heat exchanger 6. The cooling cycle switched by the four-way valve 2 is a cycle in which a refrigerant flows as shown by the solid line arrow in FIG. 1, and constitutes a cycle of a cooling operation and a cooling cycle dehumidifying operation. The heating cycle is a cycle in which a refrigerant flows as indicated by a dotted arrow in FIG. 1, and constitutes a heating operation and a heating cycle dehumidifying operation.
【００１３】絞り装置７は電磁開閉弁１０と絞り装置１
１が並列に接続されて構成されている。電磁開閉弁１０
は、通電することにより流路を全開にし、通電を止める
ことにより流路を全閉するように形成されている。絞り
流路１１は、図２及び図３に示すように、拡大した管路
内に固定オリフィス２１，２２及び可動オリフィス２３
を設置したものである。The throttle device 7 includes an electromagnetic on-off valve 10 and a throttle device 1.
1 are connected in parallel. Solenoid valve 10
Is formed so that the flow path is fully opened by energizing and the flow path is fully closed by stopping energizing. As shown in FIGS. 2 and 3, the throttle channel 11 has fixed orifices 21 and 22 and a movable orifice 23 in an enlarged conduit.
Is installed.
【００１４】固定オリフィス２１，２２は、複数のオリ
フィス穴を有しており、所定間隔を有して管路内に固定
されている。固定オリフィス２１より固定オリフィス２
２のオリフィス穴の方が多く形成されている。可動オリ
フィス２３は、複数のオリフィス穴を有しており、固定
オリフィス２１，２２の間に位置して冷媒の流れによっ
て移動可能に配置されている。The fixed orifices 21 and 22 have a plurality of orifice holes and are fixed in the pipe line at a predetermined interval. From fixed orifice 21 to fixed orifice 2
The second orifice hole is formed more. The movable orifice 23 has a plurality of orifice holes, is located between the fixed orifices 21 and 22, and is movably arranged by the flow of the refrigerant.
【００１５】冷房サイクル除湿運転時には、図２の実線
矢印に示すように冷媒が流れるので、可動オリフィス２
３は固定オリフィス２２に押しつけられて固定オリフィ
ス２２と組み合わされる。これによって、固定オリフィ
ス２２のオリフィス穴の一部が可動オリフィス２３によ
って塞がれ、固定オリフィス２２のオリフィス穴と可動
オリフィス２３のオリフィス穴とが重なった部分を通し
て冷媒が流れることになる。したがって、冷媒は、固定
オリフィス２１のオリフィス穴を通過する際に絞られ、
さらに可動オリフィス２３と固定オリフィス２２の組み
合わせられたオリフィス穴を通過する際に絞られる。す
なわち、二段で減圧、膨張されるので、一段の減圧、膨
張されるものに比較して冷媒音による騒音の発生を抑制
することができる。そして、二段目の絞り抵抗部より一
段目の絞り抵抗部のオリフィス穴冷媒通過面積が大きく
なるように構成されている。これにより、さらに緩やか
に絞られることになるので、冷房サイクル除湿運転時に
おける冷媒音による騒音の発生を格段に抑制することが
できる。During the cooling cycle dehumidifying operation, the refrigerant flows as shown by the solid arrow in FIG.
3 is pressed against the fixed orifice 22 and combined with the fixed orifice 22. As a result, a part of the orifice hole of the fixed orifice 22 is blocked by the movable orifice 23, and the refrigerant flows through the portion where the orifice hole of the fixed orifice 22 and the orifice hole of the movable orifice 23 overlap. Therefore, the refrigerant is throttled when passing through the orifice hole of the fixed orifice 21,
Further, it is narrowed down when passing through an orifice hole in which the movable orifice 23 and the fixed orifice 22 are combined. That is, since the pressure is reduced and expanded in two stages, it is possible to suppress the generation of noise due to the refrigerant noise as compared with the case where the pressure is reduced and expanded in one stage. Further, the orifice hole refrigerant passage area of the first-stage throttle resistance portion is larger than that of the second-stage throttle resistance portion. As a result, the squeezing is performed more gently, so that the generation of noise due to the refrigerant noise during the cooling cycle dehumidifying operation can be significantly suppressed.
【００１６】暖房サイクル除湿運転時には、図３の点線
矢印に示すように冷媒が流れるので、可動オリフィス２
３は固定オリフィス２１に押しつけられて固定オリフィ
ス２１と組み合わされる。これによって、固定オリフィ
ス２１のオリフィス穴の一部が可動オリフィス２３によ
って塞がれ、固定オリフィス２１のオリフィス穴と可動
オリフィス２３のオリフィス穴とが重なった部分を通し
て冷媒が流れることになる。したがって、冷媒は、固定
オリフィス２２のオリフィス穴を通過する際に絞られ、
さらに可動オリフィス２３と固定オリフィス２１の組み
合わせられたオリフィス穴を通過する際に絞られる。す
なわち、二段で減圧、膨張されるので、一段の絞り抵抗
部を有するものに比較して騒音の発生を抑制することが
できる。そして、二段目の絞り抵抗部より一段目の絞り
抵抗部のオリフィス穴冷媒通過面積が大きくなるように
構成されている。これにより、さらに緩やかに絞られる
ことになるので、冷房サイクル除湿運転時における騒音
発生を格段に抑制することができる。また、暖房サイク
ル除湿運転における絞り抵抗は冷房サイクル除湿運転に
おける絞り抵抗より大きくなるように設定されている。During the heating cycle dehumidifying operation, the refrigerant flows as shown by the dotted arrow in FIG.
3 is pressed against the fixed orifice 21 and combined with the fixed orifice 21. As a result, a part of the orifice hole of the fixed orifice 21 is blocked by the movable orifice 23, and the refrigerant flows through the portion where the orifice hole of the fixed orifice 21 and the orifice hole of the movable orifice 23 overlap. Therefore, the refrigerant is throttled when passing through the orifice hole of the fixed orifice 22,
Further, it is narrowed down when passing through an orifice hole in which the movable orifice 23 and the fixed orifice 21 are combined. That is, since the pressure is reduced and expanded in two stages, it is possible to suppress the generation of noise as compared with the case where the diaphragm resistance unit in one stage is provided. Further, the orifice hole refrigerant passage area of the first-stage throttle resistance portion is larger than that of the second-stage throttle resistance portion. As a result, the squeezing is performed more gently, so that noise generation during the cooling cycle dehumidifying operation can be significantly suppressed. Further, the throttling resistance in the heating cycle dehumidifying operation is set to be larger than the throttling resistance in the cooling cycle dehumidifying operation.
【００１７】これらの圧縮機１、四方弁２、室外熱交換
器３、第１の絞り装置４、第１の室内熱交換器５、第２
の絞り装置７、第２の室内熱交換器６は、図１に示すよ
うに、冷媒配管により順次接続されて冷凍サイクルを構
成する。また、８は室外ファン、９は室内ファンであ
る。These compressor 1, four-way valve 2, outdoor heat exchanger 3, first expansion device 4, first indoor heat exchanger 5, second
As shown in FIG. 1, the expansion device 7 and the second indoor heat exchanger 6 are sequentially connected by a refrigerant pipe to form a refrigeration cycle. Further, 8 is an outdoor fan, and 9 is an indoor fan.
【００１８】次に、係る空気調和機の動作について説明
する。Next, the operation of the air conditioner will be described.
【００１９】冷房運転時には、冷媒は図１の実線矢印の
方向に流れる。圧縮機１で圧縮された冷媒は室外熱交換
器３で凝縮して室外空気へ放熱し、第１の絞り装置４に
よって減圧膨張し、室内熱交換器５、６で蒸発して室内
空気から吸熱して圧縮機１へ戻る。このとき第２の絞り
装置７は電磁開閉弁１０が全開状態となっているため、
冷媒はこの電磁開閉弁１０を通り、第２の絞り装置７は
絞り作用を行なわない。During the cooling operation, the refrigerant flows in the direction of the solid arrow in FIG. The refrigerant compressed by the compressor 1 is condensed by the outdoor heat exchanger 3 and radiates heat to the outdoor air, is decompressed and expanded by the first expansion device 4, is evaporated by the indoor heat exchangers 5 and 6, and absorbs heat from the indoor air. Then, it returns to the compressor 1. At this time, since the electromagnetic on-off valve 10 of the second expansion device 7 is in the fully open state,
The refrigerant passes through the electromagnetic opening / closing valve 10, and the second expansion device 7 does not perform the expansion action.
【００２０】冷房サイクル除湿運転時には、冷媒は図１
の実線矢印の方向に流れ、第１の絞り装置４を全開に
し、第２の絞り装置７を絞った状態にする。すなわち、
電磁開閉弁１０を全閉状態とし、冷媒は絞り流路１１の
みを通過して絞り作用を受ける。したがって、第１の室
内熱交換器５は冷媒が凝縮して室内空気へ放熱する加熱
器となり、第２の室内熱交換器６は冷媒が蒸発して室内
空気から吸熱する冷却器となる。このようにして、第１
の室内熱交換器５で加熱された空気と、第２の室内熱交
換器６で冷却、除湿された空気とが混合されて室内へ吹
き出される。このとき、圧縮機１の回転数や室外ファン
８の回転数を制御することにより、空気の温度を低下さ
せずに空気中の水分のみを取り除く等温除湿運転、空気
を加熱しながら水分を取り除く暖房気味除湿運転、空気
を冷やしながら除湿を行なう冷房気味除湿運転のいずれ
の運転も可能となる。During the dehumidifying operation in the cooling cycle, the refrigerant flow is as shown in FIG.
In the direction of the solid line arrow, the first expansion device 4 is fully opened and the second expansion device 7 is closed. That is,
With the electromagnetic on-off valve 10 fully closed, the refrigerant passes through only the throttle passage 11 and is subjected to the throttling action. Therefore, the first indoor heat exchanger 5 serves as a heater that condenses the refrigerant and radiates heat to the indoor air, and the second indoor heat exchanger 6 serves as a cooler that evaporates the refrigerant and absorbs heat from the indoor air. In this way, the first
The air heated by the indoor heat exchanger 5 and the air cooled and dehumidified by the second indoor heat exchanger 6 are mixed and blown out into the room. At this time, by controlling the rotation speed of the compressor 1 and the rotation speed of the outdoor fan 8, an isothermal dehumidifying operation for removing only moisture in the air without lowering the temperature of the air, a heating for removing moisture while heating the air Both the slightly dehumidifying operation and the air-cooling dehumidifying operation that dehumidifies while cooling the air can be performed.
【００２１】この冷房サイクル除湿運転の詳細を図４に
示すモリエル線図を用いて説明する。I〜IIで圧縮機１
により圧縮されて高温高圧になった気体状の冷媒は、室
外熱交換器３でII〜IIIに相当する熱を室外空気に放熱
して、点IIIに相当する分だけの冷媒を液状に変化す
る。この冷房サイクル除湿運転の場合には、室外ファン
８の回転数を低くして、室内空気を加熱するのに必要な
熱量を高温の気体状冷媒として残すこととしている。点
IIIの状態で室外熱交換器３を出た冷媒は、開放状態の
第１の絞り装置４で少し圧力が下がって点IVの状態とな
って第１の室内熱交換器５に入る。この第１の室内熱交
換器５で残されたIV〜Vに相当する熱を放出して室内空
気を加熱して第２の絞り装置７に入る。第２の絞り装置
７は電磁開閉弁１０が閉路しているので、冷媒は絞り流
路１１に入り、図２に示すように可動オリフィス２３を
固定オリフィス２２側に移動する。Details of the cooling cycle dehumidifying operation will be described with reference to the Mollier diagram shown in FIG. Compressor 1 from I to II
The gaseous refrigerant that has been compressed by and has become high temperature and high pressure radiates heat corresponding to II to III to the outdoor air in the outdoor heat exchanger 3 and changes the refrigerant corresponding to point III into a liquid state. . In the case of this cooling cycle dehumidifying operation, the number of rotations of the outdoor fan 8 is lowered so that the amount of heat required to heat the indoor air is left as a high-temperature gaseous refrigerant. point
The refrigerant that has left the outdoor heat exchanger 3 in the state of III is slightly reduced in pressure in the first expansion device 4 in the open state and enters the state of point IV into the first indoor heat exchanger 5. The heat corresponding to IV to V left in the first indoor heat exchanger 5 is released to heat the indoor air and enter the second expansion device 7. Since the electromagnetic on-off valve 10 of the second expansion device 7 is closed, the refrigerant enters the expansion passage 11 and moves the movable orifice 23 to the fixed orifice 22 side as shown in FIG.
【００２２】絞り流路１１で冷媒の圧力を下げるわけで
あるが、V〜VIに示すように二段階に分けて圧力を下げ
るようになっている。すなわち、冷媒は、冷媒の通過す
るオリフィス穴面積が大きな固定オリフィス２１を通っ
て圧力が下がり、次いで可動オリフィス２３と固定オリ
フィス２２とが組み合わされて冷媒の通過するオリフィ
ス穴の面積が小さな可動オリフィス２３、固定オリフィ
ス２２を通って圧力が大きく下がる。このように、複数
段で圧力が下がることにより、冷媒の圧力変化による騒
音の発生を抑制することができる。The pressure of the refrigerant is lowered in the throttle passage 11, but the pressure is lowered in two stages as shown in V to VI. That is, the pressure of the refrigerant is lowered through the fixed orifice 21 having a large orifice hole area through which the refrigerant passes, and then the movable orifice 23 and the fixed orifice 22 are combined so that the orifice hole through which the refrigerant passes has a small area. The pressure greatly drops through the fixed orifice 22. In this way, by reducing the pressure in multiple stages, it is possible to suppress the generation of noise due to the pressure change of the refrigerant.
【００２３】このようにして圧力の下がった冷媒は第２
の室内熱交換器６に入り、室内空気からVI〜Iに相当す
る熱を奪って室内空気を冷却すると共に、空気中の水分
を取り除き、室内空気を乾燥させ、冷媒自体は蒸発して
気体状に変化する。そして、気体状の冷媒は元の圧縮工
程I〜IIに戻る。The pressure-reduced refrigerant is the second
Enters the indoor heat exchanger 6 and cools the indoor air by removing heat corresponding to VI to I from the indoor air, removes moisture in the air, dries the indoor air, and evaporates the refrigerant itself into a gaseous state. Changes to. Then, the gaseous refrigerant returns to the original compression steps I to II.
【００２４】暖房運転時には、冷媒は図１の破線矢印の
方向に流れる。圧縮機１で圧縮された冷媒は室内熱交換
器５、６で凝縮して空気へ放熱し、第１の絞り装置４に
よって減圧膨張し、室外熱交換器３で蒸発して空気から
吸熱して圧縮機１へ戻る。このとき第２の絞り装置７は
電磁開閉弁１０が全開状態となっているため、冷媒はこ
の電磁開閉弁１０を通り、第２の絞り装置７は絞り作用
を行なわない。During the heating operation, the refrigerant flows in the direction of the broken line arrow in FIG. The refrigerant compressed in the compressor 1 is condensed in the indoor heat exchangers 5 and 6 and radiates heat to the air, is decompressed and expanded by the first expansion device 4, is evaporated in the outdoor heat exchanger 3 and absorbs heat from the air. Return to compressor 1. At this time, since the electromagnetic opening / closing valve 10 of the second expansion device 7 is in the fully open state, the refrigerant passes through the electromagnetic opening / closing valve 10 and the second expansion device 7 does not perform the expansion action.
【００２５】暖房サイクル除湿運転時には、冷媒は図１
の破線矢印の方向に流れる。第１の絞り装置４を全開に
し、第２の絞り装置７を絞った状態にする。すなわち電
磁開閉弁１０を全閉状態とし、冷媒は絞り流路１１のみ
を通過して絞り作用を受ける。したがって、第２の室内
熱交換器６は冷媒が凝縮して室内空気へ放熱する加熱器
となり、第１の室内熱交換器５は冷媒が蒸発して室内空
気から吸熱する冷却器となる。このようにして、室内熱
交換器５で冷却、除湿された空気と、室内熱交換器６で
加熱された空気とが室内へ混合されて吹き出される。During the heating cycle dehumidifying operation, the refrigerant is as shown in FIG.
Flows in the direction of the dashed arrow. The first expansion device 4 is fully opened and the second expansion device 7 is closed. That is, the electromagnetic on-off valve 10 is fully closed, and the refrigerant passes through only the throttle passage 11 and is subjected to the throttling action. Therefore, the second indoor heat exchanger 6 becomes a heater that condenses the refrigerant and radiates heat to the indoor air, and the first indoor heat exchanger 5 becomes a cooler that evaporates the refrigerant and absorbs heat from the indoor air. In this way, the air cooled and dehumidified by the indoor heat exchanger 5 and the air heated by the indoor heat exchanger 6 are mixed and blown out into the room.
【００２６】この暖房サイクル除湿運転の詳細を図５に
示すモリエル線図を用いて説明する。I〜IIで圧縮機１
により圧縮されて高温高圧になった気体状の冷媒は、ま
ず第２の室内熱交換器６に導かれII〜IIIに相当する熱
を放熱して、室内空気を加熱して第２の絞り装置７に入
る。第２の絞り装置７は電磁開閉弁１０が閉路している
ので、冷媒は絞り流路１１に入り、図３に示すように可
動オリフィス２３を固定オリフィス２１側に移動する。Details of the heating cycle dehumidifying operation will be described with reference to the Mollier diagram shown in FIG. Compressor 1 from I to II
The gaseous refrigerant that has been compressed by the high temperature and high pressure is first guided to the second indoor heat exchanger 6 to radiate the heat corresponding to II to III to heat the indoor air to generate the second expansion device. Enter 7. Since the electromagnetic on-off valve 10 of the second expansion device 7 is closed, the refrigerant enters the expansion passage 11 and moves the movable orifice 23 to the fixed orifice 21 side as shown in FIG.
【００２７】絞り流路１１で冷媒の圧力を下げるわけで
あるが、III〜IVに示すように二段階に分けて圧力を下
げるようになっている。すなわち、冷媒は、冷媒の通過
するオリフィス穴面積が大きな固定オリフィス２２を通
って圧力が下がり、次いで可動オリフィス２３と固定オ
リフィス２２とが組み合わされて冷媒の通過するオリフ
ィス穴の面積が小さな可動オリフィス２３、固定オリフ
ィス２２を通って圧力が大きく下がる。このように、複
数段で圧力が下がることにより、冷媒の圧力変化による
騒音の発生を抑制することができる。The pressure of the refrigerant is reduced in the throttle channel 11, but the pressure is reduced in two stages as shown in III to IV. That is, the pressure of the refrigerant decreases through the fixed orifice 22 having a large orifice hole area through which the refrigerant passes, and then the movable orifice 23 and the fixed orifice 22 are combined so that the orifice hole through which the refrigerant passes has a small area. The pressure greatly drops through the fixed orifice 22. In this way, by reducing the pressure in multiple stages, it is possible to suppress the generation of noise due to the pressure change of the refrigerant.
【００２８】このようにして圧力の下がった冷媒は第１
の室内熱交換器５に入り、室内空気からIV〜Vに相当す
る熱を奪って室内空気を冷却すると共に、空気中の水分
を取り除き、室内空気を乾燥させ、冷媒自体は蒸発して
気体状に変化する。The refrigerant whose pressure has decreased in this way is the first
Enters the indoor heat exchanger 5 and cools the indoor air by removing heat equivalent to IV to V from the indoor air, removes moisture in the air, dries the indoor air, and evaporates the refrigerant itself into a gaseous state. Changes to.
【００２９】次いで、冷媒は、開放状態の第１の絞り装
置４で少し圧力が下がって点VIの状態となって室外熱交
換器３に入り、室外熱交換器３でVI〜Iに相当する熱を
室外空気から吸熱して、圧縮機１に戻る。そして、気体
状の冷媒は圧縮工程I〜II以降の工程が繰り替えされ
る。Then, the pressure of the refrigerant slightly drops in the first expansion device 4 in the open state and enters the outdoor heat exchanger 3 at the point VI, and the outdoor heat exchanger 3 corresponds to VI to I. The heat is absorbed from the outdoor air and returns to the compressor 1. Then, for the gaseous refrigerant, the steps from compression step I to II are repeated.
【００３０】この暖房サイクル除湿運転では、室外熱交
換器３は蒸発器となって吸熱を行なうため、室内熱交換
器６の加熱能力が冷房サイクル除湿運転よりも大きい。
このとき、圧縮機１の回転数や室外ファン８の回転数を
制御することにより、室内空気を加熱しながら水分を取
り除く暖房気味除湿運転が可能である。In this heating cycle dehumidifying operation, since the outdoor heat exchanger 3 functions as an evaporator and absorbs heat, the heating capacity of the indoor heat exchanger 6 is larger than that in the cooling cycle dehumidifying operation.
At this time, by controlling the rotation speed of the compressor 1 and the rotation speed of the outdoor fan 8, it is possible to perform a heating-like dehumidifying operation for removing moisture while heating the indoor air.
【００３１】特に、絞り流路１１は暖房サイクル除湿運
転時の方が冷房サイクル除湿運転時より流路抵抗が大き
くなるように構成されているので、暖房サイクル除湿運
転時に蒸発器となる熱交換器が室内熱交換器５と室外熱
交換器３の両方で構成されて大きくなっても、過熱度を
維持する暖房サイクル除湿運転が可能である。そして、
暖房サイクル除湿運転時の流路抵抗を大きくして蒸発温
度が低くなるようにしてあるので、室外温度が低下して
も、室外空気から吸熱することが可能であり、これによ
り室内熱交換気６の加熱能力を高くでき、吹き出し温度
を高く保つことが出来る。In particular, the throttle channel 11 is constructed so that the channel resistance during the heating cycle dehumidifying operation is greater than that during the cooling cycle dehumidifying operation, so that the heat exchanger serving as an evaporator during the heating cycle dehumidifying operation. Even if the heat exchanger is constituted by both the indoor heat exchanger 5 and the outdoor heat exchanger 3 and becomes large, the heating cycle dehumidifying operation for maintaining the superheat degree is possible. And
Since the flow path resistance during the heating cycle dehumidifying operation is increased to lower the evaporation temperature, it is possible to absorb heat from the outdoor air even when the outdoor temperature decreases, and thus the indoor heat exchange air 6 The heating capacity can be increased and the blowing temperature can be kept high.
【００３２】次に、本発明の他の実施例を説明する。Next, another embodiment of the present invention will be described.
【００３３】図６は本発明の第２実施例に用いる絞り流
路１１の冷房サイクル除湿運転時における断概略図であ
る。実線矢印は冷媒の流れを示し、以下の図においても
同様である。この絞り流路１１は、第１実施例の固定オ
リフィス２１を単なるストッパ２４に変更したものであ
る。この絞り流路１１によれば、冷房サイクル除湿運転
時に二段階の絞り機能を有しないが、暖房サイクル除湿
運転時の絞り機能は同一であり、第１実施例より構造が
簡単で安価なものとすることができる。したがって、冷
房サイクル除湿運転時に冷媒による騒音の抑制の必要性
が低い場合に有効である。FIG. 6 is a schematic sectional view of the throttle channel 11 used in the second embodiment of the present invention during the cooling cycle dehumidifying operation. Solid arrows indicate the flow of the refrigerant, and the same applies to the following figures. This throttle channel 11 is obtained by changing the fixed orifice 21 of the first embodiment into a simple stopper 24. According to this throttle channel 11, although it does not have a two-stage throttle function during the cooling cycle dehumidifying operation, the throttle function during the heating cycle dehumidifying operation is the same, and the structure is simpler and less expensive than the first embodiment. can do. Therefore, it is effective when it is less necessary to suppress noise due to the refrigerant during the cooling cycle dehumidifying operation.
【００３４】図７は本発明の第３実施例に用いる絞り流
路１１の断概略図である。実線矢印は冷房サイクル除湿
運転時の冷媒の流れを示し、点線矢印は暖房サイクル除
湿運転時の冷媒の流れを示し、以下の図においても同様
である。この絞り流路１１は、冷媒の流れ方向に穴径が
異なるオリフィス穴を有する固定オリフィス２５を単独
で設置したものである。このオリフィス穴は二つの異な
る穴径の有した段部で構成している。この絞り流路１１
によれば、冷房サイクル除湿運転時より暖房サイクル除
湿運転時の絞り量の方が大きくなり、構造が極めて簡単
で安価にできる。FIG. 7 is a schematic sectional view of the throttle channel 11 used in the third embodiment of the present invention. The solid arrow indicates the flow of the refrigerant during the cooling cycle dehumidifying operation, and the dotted arrow indicates the flow of the refrigerant during the heating cycle dehumidifying operation. The same applies to the following figures. The throttle channel 11 is provided with a single fixed orifice 25 having orifice holes having different hole diameters in the flow direction of the refrigerant. The orifice hole is composed of a step having two different hole diameters. This throttle channel 11
According to this, the throttle amount during the heating cycle dehumidifying operation is larger than during the cooling cycle dehumidifying operation, and the structure can be extremely simple and inexpensive.
【００３５】図８は本発明の第４実施例に用いる絞り流
路１１の断概略図である。この絞り流路１１は、第３実
施例に比較してオリフィス穴を傾斜面で形成した点で相
違している。この絞り流路１１によれば、傾斜面のオリ
フィス穴により冷媒の変化を緩やかに行うことができ、
冷媒による騒音の抑制をさらに図ることができる。FIG. 8 is a schematic sectional view of the throttle channel 11 used in the fourth embodiment of the present invention. The throttle channel 11 is different from that of the third embodiment in that an orifice hole is formed by an inclined surface. According to this throttle channel 11, the change of the refrigerant can be performed gently by the orifice hole of the inclined surface,
The noise due to the refrigerant can be further suppressed.
【００３６】図９は本発明の第５実施例に用いる絞り流
路１１の冷房サイクル除湿運転時における断概略図であ
る。この絞り流路１１は、第１実施例における固定オリ
フィス２１、２２の両側に間隔をあけて多孔質体や金網
などからなるストレーナ２６、２７を設置したものであ
る。この絞り流路１１によれば、冷媒と共に流れてくる
ごみなどをストレーナ２６、２７で除去することがで
き、ごみなどによる固定オリフィス２１〜２３のオリフ
ィス穴の目詰まりや可動オリフィス２３の移動阻止を防
ぐことができる。FIG. 9 is a schematic sectional view of the throttle channel 11 used in the fifth embodiment of the present invention during the cooling cycle dehumidifying operation. The throttle channel 11 is provided with strainers 26 and 27 made of a porous material, a wire mesh or the like, which are spaced from each other on both sides of the fixed orifices 21 and 22 in the first embodiment. According to the throttle channel 11, dust and the like flowing along with the refrigerant can be removed by the strainers 26 and 27, so that clogging of the orifice holes of the fixed orifices 21 to 23 due to dust and the movement of the movable orifice 23 can be prevented. Can be prevented.
【００３７】図１０は本発明の第６実施例に用いる絞り
流路１１の冷房サイクル除湿運転時における断概略図で
ある。この絞り流路１１は、第２実施例におけるストッ
パ２４、固定オリフィス２２の両側に間隔をあけて多孔
質体や金網などからなるストレーナ２６、２７を設置し
たものである。この絞り流路１１によれば、冷媒と共に
流れてくるごみなどをストレーナ２６、２７で除去する
ことができ、ごみなどによる固定オリフィス２２、可動
オリフィス２３のオリフィス穴の目詰まりや可動オリフ
ィス２３の移動阻止を防ぐことができる。FIG. 10 is a schematic sectional view of the throttle channel 11 used in the sixth embodiment of the present invention during the cooling cycle dehumidifying operation. The throttle channel 11 is provided with strainers 26 and 27 made of a porous material, a wire mesh or the like at intervals on both sides of the stopper 24 and the fixed orifice 22 in the second embodiment. According to the throttle channel 11, dust and the like flowing along with the refrigerant can be removed by the strainers 26 and 27, clogging of the orifice holes of the fixed orifice 22 and the movable orifice 23 due to dust and the movement of the movable orifice 23. The prevention can be prevented.
【００３８】図１１は本発明の第７実施例に用いる絞り
流路１１の冷房サイクル除湿運転時における断概略図で
ある。この絞り流路１１は、第３実施例における固定オ
リフィス２５の両側に間隔をあけて多孔質体や金網など
からなるストレーナ２６、２７を設置したものである。
この絞り流路１１によれば、冷媒と共に流れてくるごみ
などをストレーナ２６、２７で除去することができ、ご
みなどによる固定オリフィス２５のオリフィス穴の目詰
まりを防ぐことができる。FIG. 11 is a schematic sectional view of the throttle channel 11 used in the seventh embodiment of the present invention during the cooling cycle dehumidifying operation. The throttle channel 11 is provided with strainers 26 and 27 made of a porous material, a wire mesh, or the like, which are spaced apart from each other on both sides of the fixed orifice 25 in the third embodiment.
According to the throttle channel 11, dust and the like that flow with the refrigerant can be removed by the strainers 26 and 27, and clogging of the orifice hole of the fixed orifice 25 due to dust and the like can be prevented.
【００３９】図１２は本発明の第８実施例に用いる絞り
流路１１の冷房サイクル除湿運転時における断概略図で
ある。この絞り流路１１は、第４実施例における固定オ
リフィス２５の両側に間隔をあけて多孔質体や金網など
からなるストレーナ２６、２７を設置したものである。
この絞り流路１１によれば、冷媒と共に流れてくるごみ
などをストレーナ２６、２７で除去することができ、ご
みなどによる固定オリフィス２５のオリフィス穴の目詰
まりを防ぐことができる。FIG. 12 is a schematic sectional view of the throttle channel 11 used in the eighth embodiment of the present invention during the cooling cycle dehumidifying operation. The throttle channel 11 is provided with strainers 26 and 27 made of a porous material, a wire mesh, or the like, which are spaced from each other on both sides of the fixed orifice 25 in the fourth embodiment.
According to the throttle channel 11, dust and the like that flow with the refrigerant can be removed by the strainers 26 and 27, and clogging of the orifice hole of the fixed orifice 25 due to dust and the like can be prevented.
【００４０】図１３は本発明の第９実施例に用いる絞り
流路１１の断概略図である。この絞り流路１１は、第８
実施例における固定オリフィス２５の穴径の狭い側のス
トレーナ２６の厚さを厚くしたものである。この絞り流
路１１によれば、固定オリフィス２５のオリフィス穴の
差による流通抵抗差にストレーナ２６、２７の流通抵抗
差を加えて冷房サイクル除湿運転と暖房サイクル除湿運
転の絞り抵抗の差とすることができるので、第８実施例
よりさらに冷房サイクル除湿運転と暖房サイクル除湿運
転の除湿運転性能を向上できる。FIG. 13 is a schematic sectional view of the throttle channel 11 used in the ninth embodiment of the present invention. This throttle channel 11 is
In the embodiment, the strainer 26 on the side where the hole diameter of the fixed orifice 25 is narrow is thickened. According to the throttle passage 11, the difference in flow resistance due to the difference in the orifice holes of the fixed orifice 25 is added to the difference in flow resistance between the strainers 26 and 27 to obtain the difference in throttle resistance between the cooling cycle dehumidifying operation and the heating cycle dehumidifying operation. Therefore, the dehumidifying operation performance of the cooling cycle dehumidifying operation and the heating cycle dehumidifying operation can be further improved as compared with the eighth embodiment.
【００４１】図１４は本発明の第１０実施例に用いる絞
り流路１１の断概略図である。この絞り流路１１は、第
８実施例における固定オリフィス２５の穴径の狭い側の
ストレーナ２６の目を細かくしたものである。この絞り
流路１１によれば、固定オリフィス２５のオリフィス穴
径の差による流通抵抗差にストレーナ２６、２７の流通
抵抗差を加えて冷房サイクル除湿運転と暖房サイクル除
湿運転の絞り抵抗の差とすることができるので、第８実
施例よりさらに冷房サイクル除湿運転と暖房サイクル除
湿運転の除湿運転性能を向上できる。FIG. 14 is a schematic sectional view of the throttle channel 11 used in the tenth embodiment of the present invention. The throttle channel 11 is formed by making the strainer 26 on the side of the fixed orifice 25 having a smaller hole diameter finer in the eighth embodiment. According to the throttle passage 11, the difference in flow resistance due to the difference in the orifice hole diameter of the fixed orifice 25 is added to the difference in flow resistance between the strainers 26 and 27 to obtain the difference in throttle resistance between the cooling cycle dehumidifying operation and the heating cycle dehumidifying operation. Therefore, the dehumidifying operation performance of the cooling cycle dehumidifying operation and the heating cycle dehumidifying operation can be further improved as compared with the eighth embodiment.
【００４２】図１５は本発明の第１１実施例に用いる絞
り流路１１の断概略図である。この絞り流路１１は、第
９実施例における固定オリフィス２５を削除し、ストレ
ーナ２６、２７の厚さの差をさらに大きくしたものであ
る。この絞り流路１１によれば、ストレーナ２６、２７
の流通抵抗差のみによって冷房サイクル除湿運転と暖房
サイクル除湿運転の絞り抵抗の差とすることができるの
で、第９実施例より構造を簡単にして安価なものとする
ことができる。FIG. 15 is a schematic sectional view of the throttle channel 11 used in the eleventh embodiment of the present invention. This throttle channel 11 is formed by eliminating the fixed orifice 25 in the ninth embodiment and further increasing the difference in thickness between the strainers 26 and 27. According to the throttle channel 11, the strainers 26, 27
Since the difference in the throttle resistance between the cooling cycle dehumidifying operation and the heating cycle dehumidifying operation can be obtained only by the difference in the flow resistance, the structure can be made simpler and less expensive than the ninth embodiment.
【００４３】図１６は本発明の第１２実施例に用いる絞
り流路１１の断概略図である。この絞り流路１１は、第
１０実施例における固定オリフィス２５を削除し、スト
レーナ２６、２７の目の密度の差をさらに大きくしたも
のである。この絞り流路１１によれば、ストレーナ２
６、２７の流通抵抗差のみによって冷房サイクル除湿運
転と暖房サイクル除湿運転の絞り抵抗の差とすることが
できるので、第１０実施例より構造を簡単にして安価な
ものとすることができる。FIG. 16 is a schematic sectional view of the throttle channel 11 used in the twelfth embodiment of the present invention. This throttle channel 11 is formed by eliminating the fixed orifice 25 in the tenth embodiment and further increasing the difference in the mesh density of the strainers 26 and 27. According to this throttle channel 11, the strainer 2
Since the difference in the throttle resistance between the cooling cycle dehumidifying operation and the heating cycle dehumidifying operation can be obtained only by the flow resistance difference of Nos. 6 and 27, the structure can be simplified and the cost can be reduced as compared with the tenth embodiment.
【００４４】[0044]
【発明の効果】以上の実施例の説明から明らかなよう
に、本発明によれば、冷房サイクル除湿運転及び暖房サ
イクル除湿運転のそれぞれに適切な絞り抵抗として広い
温度範囲で快適に除湿運転が可能な空気調和機を得るこ
とができる。As is apparent from the above description of the embodiments, according to the present invention, it is possible to comfortably perform dehumidification operation in a wide temperature range by using throttling resistance suitable for each of the cooling cycle dehumidification operation and the heating cycle dehumidification operation. It is possible to obtain a perfect air conditioner.
【図１】本発明の第１実施例の空気調和機を示す冷凍サ
イクルの構成図である。FIG. 1 is a configuration diagram of a refrigeration cycle showing an air conditioner according to a first embodiment of the present invention.
【図２】図１の空気調和機の冷房サイクル除湿運転時に
おける第２の絞り装置の断面概略図である。FIG. 2 is a schematic cross-sectional view of a second expansion device during a cooling cycle dehumidifying operation of the air conditioner of FIG.
【図３】図１の空気調和機の第２の絞り装置の暖房サイ
クル除湿運転時の断面概略図である。FIG. 3 is a schematic cross-sectional view of the second expansion device of the air conditioner of FIG. 1 during a heating cycle dehumidifying operation.
【図４】図１の空気調和機の冷房サイクル除湿運転時の
圧力エントロピー線図である。FIG. 4 is a pressure entropy diagram during a cooling cycle dehumidifying operation of the air conditioner of FIG. 1.
【図５】図１の空気調和機の暖房サイクル除湿運転時の
圧力エントロピー線図である。5 is a pressure entropy diagram during a heating cycle dehumidifying operation of the air conditioner of FIG.
【図６】本発明の第２実施例の空気調和機の冷房サイク
ル除湿運転時における第２の絞り装置の断面概略図であ
る。FIG. 6 is a schematic cross-sectional view of a second expansion device during the cooling cycle dehumidifying operation of the air conditioner of the second embodiment of the present invention.
【図７】本発明の第３実施例の空気調和機の第２の絞り
装置の断面概略図である。FIG. 7 is a schematic sectional view of a second expansion device of the air conditioner of the third embodiment of the present invention.
【図８】本発明の第４実施例の空気調和機の第２の絞り
装置の断面概略図である。FIG. 8 is a schematic cross-sectional view of a second throttle device of the air conditioner of the fourth embodiment of the present invention.
【図９】本発明の第５実施例の空気調和機の冷房サイク
ル除湿運転時における第２の絞り装置の断面概略図であ
る。FIG. 9 is a schematic cross-sectional view of a second expansion device during a cooling cycle dehumidifying operation of an air conditioner according to a fifth embodiment of the present invention.
【図１０】本発明の第６実施例の空気調和機の冷房サイ
クル除湿運転時における第２の絞り装置の断面概略図で
ある。FIG. 10 is a schematic cross-sectional view of a second expansion device during the cooling cycle dehumidifying operation of the air conditioner of the sixth embodiment of the present invention.
【図１１】本発明の第７実施例の空気調和機の第２の絞
り装置の断面概略図である。FIG. 11 is a schematic sectional view of a second expansion device of the air conditioner of the seventh embodiment of the present invention.
【図１２】本発明の第８実施例の空気調和機の第２の絞
り装置の断面概略図である。FIG. 12 is a schematic sectional view of a second throttle device of the air conditioner of the eighth embodiment of the present invention.
【図１３】本発明の第９実施例の空気調和機の第２の絞
り装置の断面概略図である。FIG. 13 is a schematic cross-sectional view of a second expansion device of the air conditioner of the ninth embodiment of the present invention.
【図１４】本発明の第１０実施例の空気調和機の第２の
絞り装置の断面概略図である。FIG. 14 is a schematic cross-sectional view of a second throttle device of the air conditioner of the tenth embodiment of the present invention.
【図１５】本発明の第１１実施例の空気調和機の第２の
絞り装置の断面概略図である。FIG. 15 is a schematic sectional view of a second expansion device of the air conditioner of the eleventh embodiment of the present invention.
【図１６】本発明の第１２実施例の空気調和機の第２の
絞り装置の断面概略図である。FIG. 16 is a schematic sectional view of a second throttle device of the air conditioner of the twelfth embodiment of the present invention.
１…圧縮機、２…四方弁、３…室外熱交換器、４…第１
の絞り装置、５…第１の室内熱交換器、６…第２の室内
熱交換器、７…第２の絞り装置、８…室外ファン、９…
室内ファン、１０…電磁開閉弁、１１…絞り流路、２０
…第２の絞り装置、２１、２２…固定オリフィス、２３
…可動オリフィス、２４…ストッパ、２５…固定オリフ
ィス、２６、２７…ストレーナ。1 ... Compressor, 2 ... Four-way valve, 3 ... Outdoor heat exchanger, 4 ... 1st
Expansion device, 5 ... first indoor heat exchanger, 6 ... second indoor heat exchanger, 7 ... second expansion device, 8 ... outdoor fan, 9 ...
Indoor fan, 10 ... Electromagnetic on-off valve, 11 ... Throttle passage, 20
... Second throttle device, 21, 22 ... Fixed orifice, 23
... Movable orifice, 24 ... Stopper, 25 ... Fixed orifice, 26, 27 ... Strainer.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 藤林 一朗 栃木県下都賀郡大平町大字富田800番地 株式会社日立栃木テクノロジー内 (72)発明者 森本 素生 栃木県下都賀郡大平町大字富田800番地 株式会社日立栃木テクノロジー内 ─────────────────────────────────────────────────── ─── Continued front page (72) Inventor Ichiro Fujibayashi 800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Hitachi Tochigi Technology Co., Ltd. (72) Inventor Sou Morimoto 800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi Hitachi Tochigi Technology Co., Ltd.
Claims (6)
り換える運転切換弁、室外熱交換器、冷房運転及び暖房
運転の時に絞り作用を行なう第１の絞り装置、第１の室
内熱交換器と第２の室内熱交換器とに熱的に二分割され
た室内熱交換器、及びこの二分割された室内熱交換器の
間に除湿運転時に絞り作用を行なう第２の絞り装置を備
え、 前記室内熱交換器を蒸発器、前記室外熱交換器を凝縮器
とした冷房運転と、前記室内熱交換器を凝縮器、前記室
外熱交換器を蒸発器とした暖房運転と、前記第１の室内
熱交換器を蒸発器、前記第２の熱交換器を凝縮器、前記
室外熱交換器を凝縮器とした冷房サイクル除湿運転と、
前記第１の室内熱交換器を凝縮器、前記第２の室内熱交
換器を蒸発器、前記室外熱交換器を蒸発器とした暖房サ
イクル除湿運転とが可能な空気調和機において、 前記第２の絞り装置は電磁開閉弁と絞り流路とを並列に
した流路で構成し、 前記電磁開閉弁は、前記冷房運転時及び前記暖房運転時
に開路し、前記冷房サイクル除湿運転時及び前記暖房サ
イクル除湿運転時に閉路するように構成し、 前記絞り流路は、管路に固定され且つオリフィス穴を有
する固定オリフィスと、冷媒の流れによって移動可能で
且つオリフィス穴を有する可動オリフィスとを備え、前
記可動オリフィスの移動によって前記固定オリフィスと
の組み合わせ状態が変わり前記冷房サイクル除湿運転時
より前記暖房サイクル除湿運転時の絞り抵抗が大きくな
るように構成したことを特徴とする空気調和機。1. A compressor, an operation switching valve that switches between a cooling cycle and a heating cycle, an outdoor heat exchanger, a first expansion device that performs a throttling action during cooling operation and heating operation, a first indoor heat exchanger, and a first indoor heat exchanger. An indoor heat exchanger that is thermally divided into two indoor heat exchangers, and a second expansion device that performs an expansion operation during dehumidifying operation between the indoor heat exchangers that are divided into two. A cooling operation in which the heat exchanger is an evaporator and the outdoor heat exchanger is a condenser, a heating operation in which the indoor heat exchanger is a condenser, and the outdoor heat exchanger is an evaporator, and the first indoor heat A cooling cycle dehumidifying operation in which the exchanger is an evaporator, the second heat exchanger is a condenser, and the outdoor heat exchanger is a condenser;
An air conditioner capable of performing a heating cycle dehumidifying operation in which the first indoor heat exchanger is a condenser, the second indoor heat exchanger is an evaporator, and the outdoor heat exchanger is an evaporator, The expansion device is configured by a flow path in which an electromagnetic opening / closing valve and a throttle flow path are arranged in parallel, the electromagnetic opening / closing valve is opened during the cooling operation and the heating operation, and during the cooling cycle dehumidifying operation and the heating cycle. The throttle channel is configured to be closed during dehumidification operation, and the throttle channel includes a fixed orifice fixed to the pipeline and having an orifice hole, and a movable orifice movable by the flow of the refrigerant and having the orifice hole. The combination state with the fixed orifice is changed by the movement of the orifice, and the throttle resistance during the heating cycle dehumidifying operation is larger than that during the cooling cycle dehumidifying operation. Air conditioner, characterized in that the.
二つ設け、前記可動オリフィスを前記二つの固定オリフ
ィスの間に配置し、前記冷房サイクル除湿運転時に一方
の固定オリフィスと組み合わせて二段の絞り抵抗部を形
成すると共に、前記暖房サイクル除湿運転時に他方の固
定オリフィスと組み合わせて二段の絞り抵抗部を形成す
るように構成したことを特徴とする空気調和機。2. The two fixed orifices according to claim 1, wherein the two fixed orifices are provided, the movable orifice is arranged between the two fixed orifices, and the two fixed orifices are combined with one of the fixed orifices during the cooling cycle dehumidifying operation. An air conditioner that is configured to form a resistance portion and to form a two-stage throttle resistance portion in combination with the other fixed orifice during the heating cycle dehumidifying operation.
び前記可動オリフィスは複数のオリフィス穴を有し、冷
房サイクル除湿運転時及び暖房サイクル除湿運転時の何
れにおいても二段目絞り抵抗部より一段目絞り抵抗部の
オリフィス穴冷媒通過面積が大きくなるように構成した
ことを特徴とする空気調和機。3. The fixed orifice and the movable orifice according to claim 2, wherein the fixed orifice and the movable orifice have a plurality of orifice holes, and the first stage from the second stage throttling resistor section in both the cooling cycle dehumidifying operation and the heating cycle dehumidifying operation. An air conditioner characterized in that an orifice hole refrigerant passage area of a throttle resistance portion is increased.
一つ設けると共に、前記可動オリフィスを一つ設け、前
記冷房サイクル除湿運転時に前記固定オリフィスと前記
可動オリフィスとを組み合わせて一段の絞り抵抗部を形
成すると共に、前記暖房サイクル除湿運転時に前記可動
オリフィスを固定オリフィスから離して二段の絞り抵抗
部を形成したことを特徴とする空気調和機。4. The fixed orifice according to claim 1, wherein one movable orifice is provided and one movable orifice is provided, and the fixed orifice and the movable orifice are combined to form a one-stage throttling resistance portion during the cooling cycle dehumidifying operation. An air conditioner characterized by being formed, and at the time of the heating cycle dehumidifying operation, the movable orifice is separated from a fixed orifice to form a two-stage throttle resistance portion.
切り換える運転切換弁、室外熱交換器、冷房運転及び暖
房運転の時に絞り作用を行なう第１の絞り装置、第１の
室内熱交換器と第２の室内熱交換器とに熱的に二分割さ
れた室内熱交換器、及びこの二分割された室内熱交換器
の間に除湿運転時に絞り作用を行なう第２の絞り装置を
備え、 前記室内熱交換器を蒸発器、前記室外熱交換器を凝縮器
とした冷房運転と、前記室内熱交換器を凝縮器、前記室
外熱交換器を蒸発器とした暖房運転と、前記第１の室内
熱交換器を蒸発器、前記第２の熱交換器を凝縮器、前記
室外熱交換器を凝縮器とした冷房サイクル除湿運転と、
前記第１の室内熱交換器を凝縮器、前記第２の室内熱交
換器を蒸発器、前記室外熱交換器を蒸発器とした暖房サ
イクル除湿運転とが可能な空気調和機において、 前記第２の絞り装置は電磁開閉弁と絞り流路とを並列に
した流路で構成し、 前記電磁開閉弁は、前記冷房運転時及び前記暖房運転時
に開路し、前記冷房サイクル除湿運転時及び前記暖房サ
イクル除湿運転時に閉路するように構成し、 前記絞り流路は、冷媒の流れ方向に穴径が異なるオリフ
ィス穴を有するオリフィスを備え、前記冷房サイクル除
湿運転時より前記暖房サイクル除湿運転時の絞り抵抗が
大きくなるように前記オリフィスを設置したことを特徴
とする空気調和機。5. A compressor, an operation switching valve that switches between a cooling cycle and a heating cycle, an outdoor heat exchanger, a first expansion device that performs a throttling action during cooling operation and heating operation, and a first indoor heat exchanger. An indoor heat exchanger thermally divided into a second indoor heat exchanger, and a second expansion device that performs an expansion operation during the dehumidifying operation between the indoor heat exchanger divided into two parts, A cooling operation in which the indoor heat exchanger is an evaporator and the outdoor heat exchanger is a condenser; a heating operation in which the indoor heat exchanger is a condenser and the outdoor heat exchanger is an evaporator; and the first indoor space A cooling cycle dehumidifying operation in which the heat exchanger is an evaporator, the second heat exchanger is a condenser, and the outdoor heat exchanger is a condenser;
An air conditioner capable of performing a heating cycle dehumidifying operation in which the first indoor heat exchanger is a condenser, the second indoor heat exchanger is an evaporator, and the outdoor heat exchanger is an evaporator, The expansion device is configured by a flow path in which an electromagnetic opening / closing valve and a throttle flow path are arranged in parallel, the electromagnetic opening / closing valve is opened during the cooling operation and the heating operation, and during the cooling cycle dehumidifying operation and the heating cycle. It is configured to be closed during dehumidification operation, the throttle channel is provided with an orifice having orifice holes having different hole diameters in the flow direction of the refrigerant, and the throttle resistance during the heating cycle dehumidification operation is higher than during the cooling cycle dehumidification operation. An air conditioner in which the orifice is installed so as to be large.
の両側に多孔質体や金網などからなるストレーナを設け
たことを特徴とする空気調和機。6. The air conditioner according to claim 1 or 5, wherein strainers made of a porous material, a wire net, or the like are provided on both sides of the front throttle channel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002008540A JP2003207231A (en) | 2002-01-17 | 2002-01-17 | Air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002008540A JP2003207231A (en) | 2002-01-17 | 2002-01-17 | Air conditioner |
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| Publication Number | Publication Date |
|---|---|
| JP2003207231A true JP2003207231A (en) | 2003-07-25 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2002008540A Pending JP2003207231A (en) | 2002-01-17 | 2002-01-17 | Air conditioner |
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| Country | Link |
|---|---|
| JP (1) | JP2003207231A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101676646B (en) * | 2008-09-19 | 2013-01-23 | Tcl集团股份有限公司 | Control method of operating modes of air conditioner |
| JP2016133261A (en) * | 2015-01-19 | 2016-07-25 | ダイキン工業株式会社 | Refrigerant diversion structure |
-
2002
- 2002-01-17 JP JP2002008540A patent/JP2003207231A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101676646B (en) * | 2008-09-19 | 2013-01-23 | Tcl集团股份有限公司 | Control method of operating modes of air conditioner |
| JP2016133261A (en) * | 2015-01-19 | 2016-07-25 | ダイキン工業株式会社 | Refrigerant diversion structure |
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