JP2002277087A - Air conditioner - Google Patents
Air conditionerInfo
- Publication number
- JP2002277087A JP2002277087A JP2001075239A JP2001075239A JP2002277087A JP 2002277087 A JP2002277087 A JP 2002277087A JP 2001075239 A JP2001075239 A JP 2001075239A JP 2001075239 A JP2001075239 A JP 2001075239A JP 2002277087 A JP2002277087 A JP 2002277087A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- refrigerant
- outdoor
- refrigeration cycle
- outdoor heat
- 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.)
- Withdrawn
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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
-
- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- 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
- F25B39/00—Evaporators; Condensers
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/02—Increasing the heating capacity of a reversible cycle during cold outdoor conditions
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、冷凍サイクルを利
用した空気調和機に関し、特に施工性を改善し、省電力
及び地球環境保護を考慮したものに好適である。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner using a refrigeration cycle, and is particularly suitable for an air conditioner which improves workability, saves power and protects the global environment.
【０００２】[0002]
【従来の技術】空気調和機に蓄熱槽を設け、蓄熱槽内の
蓄熱媒体に冷熱を付与する冷凍サイクル回路と、液冷媒
を冷却するための熱交換器を設け、空調していない時
に、蓄熱槽の蓄熱媒体に蓄冷しておき、空調するときに
液冷媒を蓄熱槽に通して冷却し、能力向上や電力ピーク
カットをすることが知られ、例えば特開平1−174866 号
公報に記載されている。また、熱源装置を設け、液冷媒
を冷却または加熱して空調能力を増大させることが、特
開平5-126428号公報に記載されている。2. Description of the Related Art An air conditioner is provided with a heat storage tank, a refrigeration cycle circuit for applying heat to a heat storage medium in the heat storage tank, and a heat exchanger for cooling liquid refrigerant. It is known that cold storage is performed in a heat storage medium in a tank, and a liquid refrigerant is cooled by passing through a heat storage tank when air conditioning is performed, thereby improving the capacity and cutting off the power peak, for example, as described in JP-A-1-174866. I have. Japanese Patent Application Laid-Open No. HEI 5-126428 discloses that a heat source device is provided to cool or heat a liquid refrigerant to increase the air-conditioning capacity.
【０００３】[0003]
【発明が解決しようとする課題】一般に冷凍サイクルを
利用した空調機で高能力が要求される場合は、室外機容
量の大きな機種を選定する必要があり、上記従来技術の
ものでは、室外機の数が多い場合、蓄熱槽の数も多く必
要となり、広いスペースが必要となる。また、蓄熱を空
調機が稼働していないときに行うため、その蓄熱がなく
なったときには能力向上をすることができない。さら
に、熱源装置を設けたものでは、液冷媒を冷却するため
の施工が必要となるのみならず、熱源装置のスペースが
必要となる。Generally, when high performance is required for an air conditioner using a refrigeration cycle, it is necessary to select a model having a large outdoor unit capacity. When the number is large, the number of heat storage tanks is also large, and a large space is required. Further, since the heat storage is performed when the air conditioner is not operating, the capacity cannot be improved when the heat storage is exhausted. Further, in the case where the heat source device is provided, not only the construction for cooling the liquid refrigerant is required, but also the space for the heat source device is required.
【０００４】室外機の容量を大きくする場合は、室内機
と室外機とを接続する接続配管が太くなり、冷媒封入量
も多くなる。また、温暖化係数の低い冷媒には成績係数
の良い冷媒があり、地球環境保護だけでなく省電力に有
効であるが、それらは毒性、可燃性などを考慮する必要
があり、そのような冷媒が室内機側まで導くことは難し
いのが現状である。[0004] When the capacity of the outdoor unit is increased, the connection pipe connecting the indoor unit and the outdoor unit becomes large, and the amount of refrigerant charged also increases. In addition, refrigerants with a low global warming potential include refrigerants with a high coefficient of performance, which are effective not only for protecting the global environment but also for saving power.However, it is necessary to consider toxicity, flammability, etc. It is difficult at present to guide the vehicle to the indoor unit side.
【０００５】本発明の目的は、室外機の省スペースを図
り、封入冷媒量を減少させることにある。また、地球環
境保護と省電力に適したものを得ることにある。An object of the present invention is to save space in an outdoor unit and to reduce the amount of refrigerant charged. Another object of the present invention is to obtain a device suitable for global environmental protection and power saving.
【０００６】なお、本発明は上記目的、課題の少なくと
も一つを解決するものである。The present invention solves at least one of the above objects and problems.
【０００７】[0007]
【課題を解決するための手段】上記目的を達成するた
め、本発明は、圧縮機、室外熱交換器、室外ファン、減
圧装置、室内熱交換器を有し、それらを冷媒配管で結合
することによって主冷凍サイクルが構成される空気調和
機において、第2圧縮機、第2室外熱交換器、第2減圧装
置、第2熱交換器を冷媒配管で結合した第2冷凍サイクル
と、 室外熱交換器と減圧装置との間の冷媒と、第2減
圧装置と第２圧縮機との間の冷媒とで熱交換させる第2
熱交換器と、を備え、室外ファンで室外熱交換器と第2
室外熱交換器に空気を送るものである。In order to achieve the above object, the present invention comprises a compressor, an outdoor heat exchanger, an outdoor fan, a pressure reducing device, and an indoor heat exchanger, which are connected by refrigerant piping. A second refrigeration cycle in which a second compressor, a second outdoor heat exchanger, a second decompression device, and a second heat exchanger are connected by refrigerant piping in an air conditioner having a main refrigeration cycle Heat exchange between the refrigerant between the compressor and the decompression device and the refrigerant between the second decompression device and the second compressor.
A heat exchanger, and an outdoor fan with an outdoor fan and a second heat exchanger.
It sends air to the outdoor heat exchanger.
【０００８】これにより、第2の冷凍サイクルの冷熱源
と主冷凍サイクルの液冷媒とが熱交換されるので、冷房
時の蒸発側の比エンタルピ差を拡大して、冷媒循環量の
増大を抑制することができる。そして、冷媒循環量が減
少できるので冷媒配管を細くしても配管圧力損失の増大
がなく、冷媒配管を細くすることにより、冷媒封入量を
低減でき、施工性も改善される。また、第2の冷凍サイ
クルの冷媒はその量が少なくて良く、継手や配管を溶接
して密封も確実に行えるので、毒性や可燃性の恐れがあ
る冷媒を使用することも可能となる。よって、毒性や可
燃性が懸念されても温暖化係数が低く、成績係数が良い
冷媒を使用することができ、冷媒の選択範囲を広げるこ
とができる。As a result, heat is exchanged between the cold heat source of the second refrigeration cycle and the liquid refrigerant of the main refrigeration cycle, thereby increasing the specific enthalpy difference on the evaporation side during cooling and suppressing an increase in the amount of circulating refrigerant. can do. Since the amount of circulating refrigerant can be reduced, even if the refrigerant pipe is made thinner, there is no increase in pipe pressure loss. By making the refrigerant pipe thinner, the amount of refrigerant to be charged can be reduced and workability is improved. Further, the amount of the refrigerant in the second refrigeration cycle may be small, and the joints and the pipes can be welded and sealed securely, so that a refrigerant having a risk of toxicity or flammability can be used. Therefore, even if there is a concern about toxicity and flammability, a refrigerant having a low global warming coefficient and a good coefficient of performance can be used, and the range of refrigerant selection can be expanded.
【０００９】また、本発明は、第2室外熱交換器と第2熱
交換器とを冷媒配管で結合した第2冷凍サイクルと、室
外熱交換器と第2室外熱交換器に空気を送る室外ファン
と、第2室外熱交換器の下部に設けられた第2熱交換器
と、を備え、室外熱交換器と減圧装置との間の冷媒を第
2熱交換器で熱交換するものである。Further, the present invention provides a second refrigeration cycle in which a second outdoor heat exchanger and a second heat exchanger are connected by a refrigerant pipe, and an outdoor heat exchanger for sending air to the outdoor heat exchanger and the second outdoor heat exchanger. A fan and a second heat exchanger provided below the second outdoor heat exchanger, wherein the refrigerant between the outdoor heat exchanger and the pressure reducing device
The heat is exchanged in two heat exchangers.
【００１０】さらに、上記のものにおいて、第2室外熱
交換器は室外熱交換器の一部を利用したことが望まし
い。Further, in the above, it is desirable that the second outdoor heat exchanger uses a part of the outdoor heat exchanger.
【００１１】さらに、上記のものにおいて、主冷凍サイ
クルの冷媒と第2の冷凍サイクルの冷媒とは異なる冷媒
が封入されたことが望ましい。Further, in the above, it is preferable that a refrigerant different from the refrigerant of the main refrigeration cycle and the refrigerant of the second refrigeration cycle is filled.
【００１２】さらに、上記のものにおいて、第2の冷凍
サイクルの冷媒はアンモニア又はＨＣ系冷媒を用いたこ
とが望ましい。Further, in the above, it is desirable that ammonia or HC-based refrigerant is used as the refrigerant of the second refrigeration cycle.
【００１３】さらに、上記のものにおいて、主冷凍サイ
クルと第2の冷凍サイクルは、同一の室外機内に組み立
てられたことが望ましい。Further, in the above, it is desirable that the main refrigeration cycle and the second refrigeration cycle are assembled in the same outdoor unit.
【００１４】[0014]
【発明の実施の形態】本発明の一実施の形態を図１に示
し、室外機１と室内機３とが液管７とガス管９で結合さ
れた空気調和機である。室外機１は圧縮機１１、室外熱
交換器１３、室外ファン１５を有する主冷凍サイクルと
第２冷凍サイクル２で構成されている。室内機３は減圧
装置１６、室内熱交換器１７、室内ファン１８で構成さ
れている。FIG. 1 shows an embodiment of the present invention, which is an air conditioner in which an outdoor unit 1 and an indoor unit 3 are connected by a liquid pipe 7 and a gas pipe 9. The outdoor unit 1 includes a main refrigeration cycle having a compressor 11, an outdoor heat exchanger 13, and an outdoor fan 15, and a second refrigeration cycle 2. The indoor unit 3 includes a pressure reducing device 16, an indoor heat exchanger 17, and an indoor fan 18.
【００１５】室外機１内の第２冷凍サイクルは第２圧縮
機１１ａ、第２室外熱交換器１３ａ、第２減圧装置１４
ａおよび第２熱交換器２１で構成されている。室外熱交
換器１３及び第２室外熱交換器１３ａは図２に示すよう
に第２室外熱交換器１３ａ（黒丸）が室外熱交換器１３
の一部を利用して、室外ファン１５によって流れる室外
空気を利用して凝縮されるようになっている。このよう
に第２室外熱交換器１３ａを室外熱交換器１３に備えた
ことにより、室外ファン１５で両方の熱交換器に室外空
気を送ることができコンパクト化およびコスト低減が可
能になる。The second refrigeration cycle in the outdoor unit 1 includes a second compressor 11a, a second outdoor heat exchanger 13a, and a second pressure reducing device 14.
a and the second heat exchanger 21. As shown in FIG. 2, the outdoor heat exchanger 13 and the second outdoor heat exchanger 13a are replaced by the second outdoor heat exchanger 13a (black circles).
Is condensed by utilizing the outdoor air flowing by the outdoor fan 15 using a part of the outdoor fan. Since the second outdoor heat exchanger 13a is provided in the outdoor heat exchanger 13 in this manner, the outdoor fan 15 can send outdoor air to both heat exchangers, thereby making it possible to reduce the size and cost.
【００１６】次に、動作を図１で説明する。図１は冷房
運転を示したものである。圧縮機１１から吐出された高
圧ガス冷媒は室外熱交換器１３へ流れ、室外ファン１５
によって室外空気と熱交換され凝縮し液冷媒となる。一
方、第２冷凍サイクル２の第２圧縮機１１ａから吐出さ
れた高圧ガス冷媒は第２室外熱交換器１３ａへ流れ、室
外ファン１５によって室外空気と熱交換され凝縮し液冷
媒となり、第２減圧装置１４ａで減圧されて第２熱交換
器２１で、前記室外熱交換器１３から流れてくる液冷媒
と熱交換され、蒸発して第２圧縮機１１ａに吸入され
る。室外熱交換器１３から流れてきた液冷媒は第２熱交
換器で過冷却されて、液管７を流れ室内機３へ送られ
る。室内機３では、液冷媒は開度を小さくした減圧装置
１６で減圧され、室内熱交換器１７に入り、室内ファン
１８によって室内空気と熱交換される。このとき、室内
空気は冷却され、冷媒は蒸発し低圧ガス冷媒となってガ
ス管９を通って室外機１へ戻る。室外機１へ戻った低圧
ガス冷媒は圧縮機１１へ吸入される。この冷媒状態をモ
リエル線図上に示すと図３の実線のようになる。破線は
第２冷凍サイクルが作動しないときの状態であり、蒸発
側の比エンタルピ差は第２冷凍サイクルを作動させたと
きのほうが大きくなり能力が増大することがわかる。ま
た、第２冷凍サイクル２を運転しないときは、第２室外
熱交換器の分だけ伝熱面積が大きくなるので、若干では
あるが凝縮能力が増加するので、吐出圧力が下がり、成
績係数が良くなる。Next, the operation will be described with reference to FIG. FIG. 1 shows a cooling operation. The high-pressure gas refrigerant discharged from the compressor 11 flows to the outdoor heat exchanger 13 and the outdoor fan 15
The heat exchanges with the outdoor air and condenses into liquid refrigerant. On the other hand, the high-pressure gas refrigerant discharged from the second compressor 11a of the second refrigeration cycle 2 flows to the second outdoor heat exchanger 13a, and exchanges heat with the outdoor air by the outdoor fan 15 to be condensed to become a liquid refrigerant. The pressure is reduced by the device 14a, the heat is exchanged with the liquid refrigerant flowing from the outdoor heat exchanger 13 in the second heat exchanger 21, and the refrigerant is evaporated and sucked into the second compressor 11a. The liquid refrigerant flowing from the outdoor heat exchanger 13 is supercooled by the second heat exchanger, flows through the liquid pipe 7 and is sent to the indoor unit 3. In the indoor unit 3, the liquid refrigerant is decompressed by the decompression device 16 having a reduced opening, enters the indoor heat exchanger 17, and is exchanged with indoor air by the indoor fan 18. At this time, the indoor air is cooled, and the refrigerant evaporates to become a low-pressure gas refrigerant and returns to the outdoor unit 1 through the gas pipe 9. The low-pressure gas refrigerant returned to the outdoor unit 1 is sucked into the compressor 11. The state of the refrigerant on the Mollier diagram is as shown by the solid line in FIG. The broken line shows the state when the second refrigeration cycle does not operate, and it can be seen that the specific enthalpy difference on the evaporation side becomes larger when the second refrigeration cycle is operated and the capacity increases. Further, when the second refrigeration cycle 2 is not operated, the heat transfer area is increased by the amount of the second outdoor heat exchanger, so that the condensing capacity is slightly increased, so that the discharge pressure is lowered and the coefficient of performance is good. Become.
【００１７】また、冷媒循環量が減少できるので冷媒配
管を細くしても配管圧力損失の増大がなく、冷媒配管を
細くすることにより、冷媒封入量を低減でき、施工性も
改善される。さらに、第2の冷凍サイクルの冷媒はその
量が少なくて良く、継手や配管を溶接して密封も確実に
行えるので、毒性や可燃性の恐れがある冷媒を使用する
ことも可能となる。よって、毒性や可燃性が懸念されて
も温暖化係数が低く、成績係数が良い冷媒を使用するこ
とができ、冷媒の選択範囲を広げることができる。Further, since the amount of circulating refrigerant can be reduced, even if the refrigerant pipe is made thinner, there is no increase in pipe pressure loss. By making the refrigerant pipe thinner, the amount of refrigerant to be charged can be reduced and workability is improved. Furthermore, the amount of the refrigerant in the second refrigeration cycle may be small, and the joints and the pipes can be welded and sealed securely, so that it is possible to use a refrigerant having a risk of toxicity or flammability. Therefore, even if there is a concern about toxicity and flammability, a refrigerant having a low global warming coefficient and a good coefficient of performance can be used, and the range of refrigerant selection can be expanded.
【００１８】次に、他の実施の形態を図４に示す。図４
は第２熱交換器２１を室外熱交換器下部に設けたもの
で、他の構成および動作はは図１の実施例と同様であ
る。図５は室外熱交換器１３、第２室外熱交換器１３
ａ、第２減圧装置１４および第２熱交換器２１の配置を
示したもので第２熱交換器での熱交換を熱伝導と空気に
よる熱伝達の両方を利用している。Next, another embodiment is shown in FIG. FIG.
In the figure, the second heat exchanger 21 is provided below the outdoor heat exchanger, and other configurations and operations are the same as those of the embodiment of FIG. FIG. 5 shows the outdoor heat exchanger 13 and the second outdoor heat exchanger 13.
a, the arrangement of the second pressure reducing device 14 and the second heat exchanger 21 is shown, wherein heat exchange in the second heat exchanger utilizes both heat conduction and heat transfer by air.
【００１９】次に、さらに他の実施の形態を図６に示
す。図６は第２冷凍サイクル２を自然循環式の冷凍サイ
クルにしたものである。他の構成および動作は図１と同
様である。図７に図６の室外熱交換器部を示す。第２室
外熱交換器１３ａは室外熱交換器１３の上部に設けら
れ、第２熱交換器２１は室外熱交換器１３の下部に設け
られ、圧縮機を使用せずに、第２冷凍サイクルの冷媒が
自由落下によって自然に循環するように配置されてい
る。Next, still another embodiment is shown in FIG. FIG. 6 shows a configuration in which the second refrigeration cycle 2 is a natural circulation type refrigeration cycle. Other configurations and operations are the same as those in FIG. FIG. 7 shows the outdoor heat exchanger section of FIG. The second outdoor heat exchanger 13a is provided on the upper part of the outdoor heat exchanger 13, and the second heat exchanger 21 is provided on the lower part of the outdoor heat exchanger 13. The refrigerant is arranged to circulate naturally by free fall.
【００２０】次に、さらに他の実施の形態を図８に示
す。図８の第２冷凍サイクル２は図１と同様である。図
１と異なる点は、メインの冷凍サイクルが冷暖房切り替
えできるように、室外機１内に四方弁１２が取り付けら
れ、アキュムレータ１０が圧縮機１１の吸入側に、室外
減圧装置１４と液タンク８が室外熱交換器１３の液配管
側に取り付けられている。また、室内機３、４が２台と
なっており、室内機４の構成は室内機３と同様で減圧装
置２６、室内熱交換器２７および室内ファン２８で構成
されている。冷房運転時は、四方弁１２が実線側になっ
ている。また、室外減圧装置１４は開いて流路抵抗を減
らしている。そのほかの動作は図１と同様である。ま
た、過冷却された液冷媒は液配管7を通って室内機３、
４に供給され各室内を冷房した後、低圧ガス冷媒となっ
てガス管９を通って室外機１に送られる。室外機１に入
った低圧ガス冷媒は四方弁１２、アキュムレータ１０を
通って圧縮機１１に吸入される。Next, still another embodiment is shown in FIG. The second refrigeration cycle 2 of FIG. 8 is the same as that of FIG. The difference from FIG. 1 is that a four-way valve 12 is installed in the outdoor unit 1 so that the main refrigeration cycle can be switched between cooling and heating, an accumulator 10 is provided on the suction side of the compressor 11, and an outdoor pressure reducing device 14 and a liquid tank 8 are provided. It is attached to the liquid pipe side of the outdoor heat exchanger 13. Further, the number of the indoor units 3 and 4 is two, and the configuration of the indoor unit 4 is the same as that of the indoor unit 3 and includes a decompression device 26, an indoor heat exchanger 27, and an indoor fan 28. During the cooling operation, the four-way valve 12 is on the solid line side. The outdoor pressure reducing device 14 is opened to reduce the flow path resistance. Other operations are the same as those in FIG. The supercooled liquid refrigerant passes through the liquid pipe 7 and the indoor unit 3,
After being supplied to the cooling unit 4 and cooling each room, it becomes a low-pressure gas refrigerant and is sent to the outdoor unit 1 through the gas pipe 9. The low-pressure gas refrigerant that has entered the outdoor unit 1 is drawn into the compressor 11 through the four-way valve 12 and the accumulator 10.
【００２１】次に暖房動作を説明する。室外機１の四方
弁１２は破線側になっている。圧縮機から吐出された高
圧高温ガス冷媒はガス管９を通って各室内機３、４に入
る。各室内機３、４に入った冷媒は室内熱交換器１７、
１８で室内ファン１８、２８によって送られた室内空気
と熱交換されて凝縮されて液化される。このとき各室内
が暖房される。液化された冷媒は開度が大きく開かれた
室内減圧装置１６、２６を通って液配管７に送られ、室
外機１に入る。室外機１に入った液冷媒は第２熱交換器
２１で冷却されて液タンク８に入る。Next, the heating operation will be described. The four-way valve 12 of the outdoor unit 1 is on the broken line side. The high-pressure high-temperature gas refrigerant discharged from the compressor enters each of the indoor units 3 and 4 through the gas pipe 9. The refrigerant entering each indoor unit 3, 4 is supplied to the indoor heat exchanger 17,
At 18, heat is exchanged with the indoor air sent by the indoor fans 18 and 28, and the air is condensed and liquefied. At this time, each room is heated. The liquefied refrigerant is sent to the liquid pipe 7 through the indoor pressure reducing devices 16 and 26 whose opening degree is greatly opened, and enters the outdoor unit 1. The liquid refrigerant that has entered the outdoor unit 1 is cooled by the second heat exchanger 21 and enters the liquid tank 8.
【００２２】その後、室外減圧装置１４で減圧されて室
外熱交換器１３に入り、室外ファン１５によって送られ
た室外空気と熱交換されて蒸発する。蒸発した冷媒は四
方弁１２、アキュムレータ１０を通って、圧縮機１１に
吸入される。このとき、第２室外熱交換器１３ａは凝縮
器になっているので、室外熱交換器１３に送られる室外
空気は暖められているので、室外熱交換器１３の蒸発能
力は増大し、蒸発圧力は上昇し、これに伴って、吸入圧
力も上昇するので、冷媒循環量は増大し、暖房能力が増
加する。その様子をモリエル線図で図９に示す。実線が
本実施例の様子で、破線が第２冷凍サイクルを運転しな
い状態である。Thereafter, the pressure is reduced by the outdoor pressure reducing device 14 and enters the outdoor heat exchanger 13 where the heat is exchanged with the outdoor air sent by the outdoor fan 15 to evaporate. The evaporated refrigerant is sucked into the compressor 11 through the four-way valve 12 and the accumulator 10. At this time, since the second outdoor heat exchanger 13a is a condenser, the outdoor air sent to the outdoor heat exchanger 13 is warmed, so that the evaporation capacity of the outdoor heat exchanger 13 increases, and the evaporation pressure increases. Increases, and the suction pressure also increases. Accordingly, the amount of circulating refrigerant increases, and the heating capacity increases. FIG. 9 is a Mollier diagram showing this state. The solid line indicates the state of the present embodiment, and the broken line indicates a state where the second refrigeration cycle is not operated.
【００２３】次に、さらに他の実施の形態を図１０に示
す。図１０の第２冷凍サイクル２は、図８に対して第２
四方弁１２ａを設けたものである。また、室外減圧装置
１４は第２熱交換器２１の液配管７側に取り付けられて
いる。また液タンクは図８に対して取り除かれている。Next, still another embodiment is shown in FIG. The second refrigeration cycle 2 of FIG.
It is provided with a four-way valve 12a. The outdoor pressure reducing device 14 is attached to the liquid pipe 7 side of the second heat exchanger 21. Also, the liquid tank has been removed with respect to FIG.
【００２４】次に動作について説明する。冷房時は第２
冷凍サイクルの第２四方弁１２ａは実線側になってお
り、動作は図８と同様である。次に暖房動作を説明す
る。室外機１の四方弁１２は破線側になっており、第２
冷凍サイクル２の第２四方弁１２ａも破線側になってい
る。メイン冷凍サイクルの暖房動作は図８の場合と同様
である。Next, the operation will be described. Second for cooling
The second four-way valve 12a of the refrigeration cycle is on the solid line side, and the operation is the same as in FIG. Next, the heating operation will be described. The four-way valve 12 of the outdoor unit 1 is on the broken line side,
The second four-way valve 12a of the refrigeration cycle 2 is also on the broken line side. The heating operation of the main refrigeration cycle is the same as in the case of FIG.
【００２５】第２冷凍サイクル２の第２圧縮機から吐出
された高圧高温ガス冷媒は第２熱交換器２１には入り、
メイン冷凍サイクルの室外減圧装置１４で減圧された冷
媒と熱交換されて、第２冷凍サイクル２の冷媒は凝縮
し、第２減圧装置１４ａで減圧されて第２室外熱交換器
１３ａで室外空気と熱交換され、蒸発して第２圧縮機に
吸入される。メイン冷凍サイクルの室外減圧装置１４で
減圧された冷媒は第２熱交換器２１で熱交換され蒸発
し、室外熱交換器１３でさらに室外空気と熱交換されて
蒸発し、四方弁１２、アキュムレータ９を通って圧縮機
１１に吸入される。このように図１０の例では、暖房
時、メイン冷凍サイクルの蒸発能力が増大するので、蒸
発圧力は上昇し、これに伴って、吸入圧力も上昇し、冷
媒循環量は増大し、暖房能力が増加する。その様子をモ
リエル線図で図１１に示す。実線が本実施例の様子で、
破線が第２冷凍サイクルを運転しない状態である。The high-pressure high-temperature gas refrigerant discharged from the second compressor of the second refrigeration cycle 2 enters the second heat exchanger 21,
The refrigerant in the second refrigeration cycle 2 is condensed by heat exchange with the refrigerant depressurized in the outdoor decompression device 14 of the main refrigeration cycle, and decompressed in the second decompression device 14a and communicates with outdoor air in the second outdoor heat exchanger 13a. Heat is exchanged, evaporated and sucked into the second compressor. The refrigerant decompressed by the outdoor decompression device 14 of the main refrigeration cycle evaporates by exchanging heat in the second heat exchanger 21, further evaporates by exchanging heat with outdoor air in the outdoor heat exchanger 13, and the four-way valve 12, the accumulator 9. And is sucked into the compressor 11. As described above, in the example of FIG. 10, at the time of heating, the evaporating pressure of the main refrigeration cycle increases, so that the evaporating pressure increases, the suction pressure also increases, the refrigerant circulation amount increases, and the heating capacity increases. To increase. FIG. 11 shows this state in a Mollier diagram. The solid line shows the state of this embodiment,
The broken line indicates a state where the second refrigeration cycle is not operated.
【００２６】図１、図４、図６、図８および図１０に示
した例の第２冷凍サイクルの冷媒は、メイン冷凍サイク
ルの冷媒と異なる冷媒を採用しても冷媒同士が混合する
ことはない。The refrigerant of the second refrigeration cycle of the example shown in FIGS. 1, 4, 6, 8 and 10 does not mix with each other even if a refrigerant different from the refrigerant of the main refrigeration cycle is adopted. Absent.
【００２７】[0027]
【発明の効果】本発明によれば、室外機の省スペースを
図り、封入冷媒量を減少させ、地球環境保護と省電力に
適したものを得ることができる。According to the present invention, it is possible to save the space of the outdoor unit, reduce the amount of the charged refrigerant, and obtain a device suitable for global environmental protection and power saving.
【図１】本発明の一実施の形態を示す冷凍サイクル系統
図。FIG. 1 is a refrigeration cycle system diagram showing one embodiment of the present invention.
【図２】図１の室外熱交換器の構成図。FIG. 2 is a configuration diagram of the outdoor heat exchanger of FIG.
【図３】図１に示す冷凍サイクルの冷房時のモリエル線
図。FIG. 3 is a Mollier chart during cooling of the refrigeration cycle shown in FIG. 1;
【図４】本発明の他の実施の形態を示す冷凍サイクル系
統図。FIG. 4 is a refrigeration cycle system diagram showing another embodiment of the present invention.
【図５】図４の室外熱交換器および第２熱交換器の構成
図。FIG. 5 is a configuration diagram of an outdoor heat exchanger and a second heat exchanger of FIG. 4;
【図６】本発明のさらに他の実施の形態を示す冷凍サイ
クル系統図。FIG. 6 is a refrigeration cycle system diagram showing still another embodiment of the present invention.
【図７】図６の室外熱交換器、第２熱交換器および第２
冷凍サイクルの構成図。FIG. 7 shows the outdoor heat exchanger, the second heat exchanger and the second heat exchanger of FIG.
The block diagram of a refrigeration cycle.
【図８】本発明のさらに他の実施の形態を示す冷凍サイ
クル系統図。FIG. 8 is a refrigeration cycle system diagram showing still another embodiment of the present invention.
【図９】図８に示す冷凍サイクルの暖房時のモリエル線
図。FIG. 9 is a Mollier chart during heating of the refrigeration cycle shown in FIG. 8;
【図１０】本発明のさらに他の実施の形態を示す冷凍サ
イクル系統図。FIG. 10 is a refrigeration cycle system diagram showing still another embodiment of the present invention.
【図１１】図１０に示す冷凍サイクルの暖房時のモリエ
ル線図。FIG. 11 is a Mollier chart during heating of the refrigeration cycle shown in FIG. 10;
１…室外機、２…第２冷凍サイクル、３，４…室内機、
７…液配管、８…液タンク、９…ガス配管、１０…アキ
ュムレータ、１１…圧縮機、１１ａ…第２圧縮機、１３
…室外熱交換器、１３ａ…第２室外熱交換器、１４…室
外減圧装置、１４ａ…第２減圧装置、１５…室外ファ
ン、１６，２６…室内減圧装置、１７，２７…室内熱交
換器、１８，２８…室内ファン、２１…第２熱交換器。1: outdoor unit, 2: second refrigeration cycle, 3, 4: indoor unit,
7 liquid pipe, 8 liquid tank, 9 gas pipe, 10 accumulator, 11 compressor, 11a second compressor, 13
... outdoor heat exchanger, 13a ... second outdoor heat exchanger, 14 ... outdoor decompression device, 14a ... second decompression device, 15 ... outdoor fan, 16, 26 ... indoor decompression device, 17, 27 ... indoor heat exchanger 18, 28: indoor fan, 21: second heat exchanger.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 坪江 宏明 静岡県清水市村松390番地 株式会社日立 空調システム清水生産本部内 (72)発明者 内藤 宏治 静岡県清水市村松390番地 株式会社日立 空調システム清水生産本部内 (72)発明者 中村 憲一 静岡県清水市村松390番地 株式会社日立 空調システム清水生産本部内 Ｆターム(参考） 3L092 AA14 BA08 BA16 ──────────────────────────────────────────────────の Continued on the front page (72) Inventor Hiroaki Tsuboe 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture Hitachi Air Conditioning Systems Co., Ltd. Shimizu Production Headquarters (72) Inventor Koji Naito 390 Muramatsu, Shimizu-shi Shizuoka Prefecture Hitachi Air-conditioning Systems Co., Ltd. Shimizu Production Headquarters (72) Inventor Kenichi Nakamura 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture Hitachi Air Conditioning Systems Shimizu Production Headquarters F-term (reference) 3L092 AA14 BA08 BA16
Claims (6)
装置、室内熱交換器を有し、それらを冷媒配管で結合す
ることによって主冷凍サイクルが構成される空気調和機
において、 第2圧縮機、第2室外熱交換器、第2減圧装置、第2熱交換
器を冷媒配管で結合した第2冷凍サイクルと、 前記室外熱交換器と前記減圧装置との間の冷媒と、前記
第2減圧装置と前記第２圧縮機との間の冷媒とで熱交換
させる第2熱交換器と、 を備え、前記室外ファンで前記室外熱交換器と第2室外
熱交換器に空気を送ることを特徴とする空気調和機。An air conditioner comprising a compressor, an outdoor heat exchanger, an outdoor fan, a decompression device, and an indoor heat exchanger, wherein a main refrigeration cycle is configured by connecting them with a refrigerant pipe. A compressor, a second outdoor heat exchanger, a second decompression device, a second refrigeration cycle in which the second heat exchanger is connected by a refrigerant pipe, and a refrigerant between the outdoor heat exchanger and the decompression device; A second heat exchanger for exchanging heat with a refrigerant between the pressure reducing device and the second compressor, and sending air to the outdoor heat exchanger and the second outdoor heat exchanger with the outdoor fan. An air conditioner characterized by the following.
装置、室内熱交換器を有し、それらを冷媒配管で結合す
ることによって主冷凍サイクルが構成される空気調和機
において、 第2室外熱交換器と第2熱交換器とを冷媒配管で結合した
第2冷凍サイクルと、前記室外熱交換器と第2室外熱交換
器に空気を送る前記室外ファンと、 前記第2室外熱交換器の下部に設けられた第2熱交換器
と、を備え、 前記室外熱交換器と前記減圧装置との間の冷媒を前記第
2熱交換器で熱交換することを特徴とする空気調和機。2. An air conditioner having a compressor, an outdoor heat exchanger, an outdoor fan, a decompression device, and an indoor heat exchanger, wherein a main refrigeration cycle is configured by connecting them with a refrigerant pipe. A second refrigeration cycle in which an outdoor heat exchanger and a second heat exchanger are connected by a refrigerant pipe, the outdoor fan that sends air to the outdoor heat exchanger and the second outdoor heat exchanger, and the second outdoor heat exchange. A second heat exchanger provided at a lower part of the heat exchanger, wherein the refrigerant between the outdoor heat exchanger and the pressure reducing device is supplied to the second heat exchanger.
An air conditioner characterized by exchanging heat with two heat exchangers.
記第2室外熱交換器は前記室外熱交換器の一部を利用し
たことを特徴とする空気調和機。3. The air conditioner according to claim 1, wherein the second outdoor heat exchanger utilizes a part of the outdoor heat exchanger.
記主冷凍サイクルの冷媒と前記第2の冷凍サイクルの冷
媒とは異なる冷媒が封入されたことを特徴とする空気調
和機。4. The air conditioner according to claim 1, wherein a refrigerant different from the refrigerant of the main refrigeration cycle and the refrigerant of the second refrigeration cycle is filled.
記第2の冷凍サイクルの冷媒はアンモニア又はＨＣ系冷
媒を用いたことを特徴とする空気調和機。5. The air conditioner according to claim 1, wherein the refrigerant of the second refrigeration cycle uses ammonia or an HC-based refrigerant.
記主冷凍サイクルと前記第2の冷凍サイクルは、同一の
室外機内に組み立てられたことを特徴とする空気調和
機。6. The air conditioner according to claim 1, wherein the main refrigeration cycle and the second refrigeration cycle are assembled in the same outdoor unit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001075239A JP2002277087A (en) | 2001-03-16 | 2001-03-16 | Air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001075239A JP2002277087A (en) | 2001-03-16 | 2001-03-16 | Air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2002277087A true JP2002277087A (en) | 2002-09-25 |
Family
ID=18932350
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001075239A Withdrawn JP2002277087A (en) | 2001-03-16 | 2001-03-16 | Air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2002277087A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2005114253A (en) * | 2003-10-08 | 2005-04-28 | Mitsubishi Electric Corp | Air conditioner |
| JP2007232245A (en) * | 2006-02-28 | 2007-09-13 | Mitsubishi Electric Corp | Refrigerating system and its operation method |
| JP2008530498A (en) * | 2005-03-14 | 2008-08-07 | ヨーク・インターナショナル・コーポレーション | HVAC system with powered supercooler |
| JP2009150620A (en) * | 2007-12-21 | 2009-07-09 | Toshiba Carrier Corp | Dual heat pump type air conditioning system |
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| KR20140058251A (en) * | 2012-11-06 | 2014-05-14 | 엘지전자 주식회사 | Integral air conditioning system for heating and cooling |
| KR20140059007A (en) * | 2012-11-07 | 2014-05-15 | 엘지전자 주식회사 | A combined refrigerating and air conditioning system |
| KR20140059008A (en) * | 2012-11-07 | 2014-05-15 | 엘지전자 주식회사 | A combined refrigerating and air conditioning system |
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2001
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005114253A (en) * | 2003-10-08 | 2005-04-28 | Mitsubishi Electric Corp | Air conditioner |
| JP4488712B2 (en) * | 2003-10-08 | 2010-06-23 | 三菱電機株式会社 | Air conditioner |
| JP2008530498A (en) * | 2005-03-14 | 2008-08-07 | ヨーク・インターナショナル・コーポレーション | HVAC system with powered supercooler |
| JP2007232245A (en) * | 2006-02-28 | 2007-09-13 | Mitsubishi Electric Corp | Refrigerating system and its operation method |
| JP2009150620A (en) * | 2007-12-21 | 2009-07-09 | Toshiba Carrier Corp | Dual heat pump type air conditioning system |
| KR101973203B1 (en) | 2012-09-24 | 2019-04-26 | 엘지전자 주식회사 | A united type system of air conditioning and cooling |
| CN103673123A (en) * | 2012-09-24 | 2014-03-26 | Lg电子株式会社 | Integral air conditioning system for heating and cooling |
| KR20140039586A (en) * | 2012-09-24 | 2014-04-02 | 엘지전자 주식회사 | A united type system of air conditioning and cooling |
| US9599379B2 (en) | 2012-09-24 | 2017-03-21 | Lg Electronics Inc. | Integral air conditioning system for heating and cooling |
| EP2711652A1 (en) * | 2012-09-24 | 2014-03-26 | LG Electronics Inc. | Integral air conditioning system for heating and cooling |
| KR20140058251A (en) * | 2012-11-06 | 2014-05-14 | 엘지전자 주식회사 | Integral air conditioning system for heating and cooling |
| KR102032178B1 (en) | 2012-11-06 | 2019-10-15 | 엘지전자 주식회사 | Integral air conditioning system for heating and cooling |
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| KR20140059008A (en) * | 2012-11-07 | 2014-05-15 | 엘지전자 주식회사 | A combined refrigerating and air conditioning system |
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| KR102014457B1 (en) | 2012-11-07 | 2019-10-21 | 엘지전자 주식회사 | A combined refrigerating and air conditioning system |
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