JP2999763B2 - Multi type air conditioner - Google Patents
Multi type air conditionerInfo
- Publication number
- JP2999763B2 JP2999763B2 JP10337699A JP33769998A JP2999763B2 JP 2999763 B2 JP2999763 B2 JP 2999763B2 JP 10337699 A JP10337699 A JP 10337699A JP 33769998 A JP33769998 A JP 33769998A JP 2999763 B2 JP2999763 B2 JP 2999763B2
- Authority
- JP
- Japan
- Prior art keywords
- condenser
- compressor
- cooling cycle
- refrigerant
- control valve
- 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.)
- Expired - Fee Related
Links
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Other Air-Conditioning Systems (AREA)
- Air Conditioning Control Device (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、空気調和機に関
し、より詳細には２つの圧縮器を用いて冷却能力を可変
させることのできるマルチ型の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, and more particularly, to a multi-type air conditioner capable of changing a cooling capacity by using two compressors.
【０００２】[0002]
【従来の技術】一般に、空気調和機は、圧縮器、凝縮
器、減圧装置、及び蒸発器からなり、室内の温度及び湿
度を適正に調節する装置である。そして、マルチ型の空
気調和機は、大容量の冷房サイクルと小容量の冷房サイ
クルとを並列連結して２つの空間を同時或いは個々に空
気調和させる空気調和機である。即ち、マルチ型の空気
調和機は、第１室を冷房する比較的に大容量の第１冷房
サイクルと、前記第１冷房サイクルと並列連結され、第
２室を冷房する小容量の第２冷房サイクルとからなる。2. Description of the Related Art Generally, an air conditioner comprises a compressor, a condenser, a decompression device, and an evaporator, and is a device for properly controlling the temperature and humidity in a room. The multi-type air conditioner is an air conditioner in which a large-capacity cooling cycle and a small-capacity cooling cycle are connected in parallel to air-condition two spaces simultaneously or individually. That is, the multi-type air conditioner has a relatively large-capacity first cooling cycle for cooling the first room, and a small-capacity second cooling system for cooling the second room connected in parallel with the first cooling cycle. It consists of a cycle.
【０００３】図３は従来のマルチ型の空気調和機の構成
を概略的に示す構成図である。同図を参照して従来のマ
ルチ型の空気調和機を説明する。まず、第１冷房サイク
ルの構成について説明する。第１冷房サイクルは、低圧
の冷媒を圧縮する第１圧縮器２と、前記第１圧縮器２で
高圧圧縮された冷媒を凝縮させて液体状態の冷媒として
作る第１凝縮器４と、前記第１凝縮器４で凝縮された高
圧の冷媒を減圧させる毛細管や膨張弁等の第１減圧装置
６と、前記第１減圧装置６からでる液体冷媒を蒸発させ
て第１室内の熱を吸収して第１室を冷房する第１蒸発器
１０とから構成される。更に、前記第１凝縮器４と第１
減圧装置６との間には冷媒の流量を調節する第１制御弁
８が設けられる。また、前記第１制御弁８と並列設置さ
れた補助減圧装置（図示せず）は、冷媒の圧力を一層低
める。FIG. 3 is a configuration diagram schematically showing the configuration of a conventional multi-type air conditioner. A conventional multi-type air conditioner will be described with reference to FIG. First, the configuration of the first cooling cycle will be described. The first cooling cycle includes a first compressor 2 that compresses a low-pressure refrigerant, a first condenser 4 that condenses the refrigerant that has been high-pressure compressed by the first compressor 2 to produce a refrigerant in a liquid state, 1 A first decompression device 6 such as a capillary tube or an expansion valve for decompressing the high-pressure refrigerant condensed in the condenser 4, and a liquid refrigerant from the first decompression device 6 is evaporated to absorb heat in the first chamber. And a first evaporator 10 for cooling the first chamber. Further, the first condenser 4 and the first condenser 4
A first control valve 8 for adjusting the flow rate of the refrigerant is provided between the pressure reducing device 6 and the pressure reducing device 6. An auxiliary pressure reducing device (not shown) installed in parallel with the first control valve 8 further lowers the pressure of the refrigerant.
【０００４】第２冷房サイクルについて説明する。第２
冷房サイクルは、第１冷房サイクルと同様に、第２圧縮
器２ａ、第２凝縮器４ａ、第２減圧装置６ａ、及び第２
蒸発器１０ａから構成される。更に、第１冷房サイクル
とは違い、冷媒の流量を調節する第２制御弁８ａが、第
２減圧装置６ａと第２蒸発器１０ａとの間に設けられて
いる。しかし、第２制御弁８ａは、第１冷房サイクルと
同様に、第２凝縮器４ａと第２減圧装置６ａとの間に設
けられてもよい。[0004] The second cooling cycle will be described. Second
The cooling cycle includes a second compressor 2a, a second condenser 4a, a second pressure reducing device 6a, and a second
It comprises an evaporator 10a. Further, unlike the first cooling cycle, a second control valve 8a for adjusting the flow rate of the refrigerant is provided between the second pressure reducing device 6a and the second evaporator 10a. However, like the first cooling cycle, the second control valve 8a may be provided between the second condenser 4a and the second pressure reducing device 6a.
【０００５】一方、前記第１冷房サイクルと前記第２冷
房サイクルとは相互連結されている。これを以下に説明
する。第１凝縮器４の出口側にはカップリング３０が設
けられる。前記カップリング３０は、連結管５２を介し
て第２凝縮器４ａの出口側に連結される。そして、前記
連結管５２の所定の位置には第１冷房サイクルと第２冷
房サイクルとの間の冷媒の流れを制御する第３制御弁５
０が設けられる。更に、第１蒸発器１０と第１圧縮器２
との間にはアキュムレータ４０が設けられ、これにより
第２蒸発器１０ａと第２圧縮器２ａとの間を流れる冷媒
は前記アキュムレータ４０を経由して流れる。すなわ
ち、第１蒸発器１０及び第２蒸発器１０ａから流出され
た冷媒は、前記アキュムレータ４０で第１圧縮器２及び
第２圧縮器２ａに分岐される。On the other hand, the first cooling cycle and the second cooling cycle are interconnected. This will be described below. A coupling 30 is provided on the outlet side of the first condenser 4. The coupling 30 is connected to an outlet side of the second condenser 4a via a connection pipe 52. A third control valve 5 for controlling the flow of the refrigerant between the first cooling cycle and the second cooling cycle is provided at a predetermined position of the connecting pipe 52.
0 is provided. Further, the first evaporator 10 and the first compressor 2
Between the second evaporator 10a and the second compressor 2a, the refrigerant flows through the accumulator 40. That is, the refrigerant flowing out of the first evaporator 10 and the second evaporator 10a is branched by the accumulator 40 into the first compressor 2 and the second compressor 2a.
【０００６】次に、上記のように構成された従来のマル
チ型の空気調和機の作用を説明する。まず、第１室と第
２室を同時運転する場合には、第１冷房サイクルと第２
冷房サイクルの動作のために第１制御弁８及び第２制御
弁８ａは開放され、第３制御弁５０は閉鎖される。これ
により、第１冷房サイクル、第２冷房サイクルがそれぞ
れ動作されることにより、第１室、第２室がそれぞれ冷
房される。更に、第１蒸発器１０及び第２蒸発器１０ａ
から吐出された冷媒がアキュムレータ４０に集まって分
岐されるが、この際第１圧縮器２の容量が第２圧縮器２
ａよりも大きいため、相対的に多い量の冷媒が第１圧縮
器２へ流れるようになる。Next, the operation of the conventional multi-type air conditioner configured as described above will be described. First, when the first and second rooms are operated simultaneously, the first cooling cycle and the second
For the operation of the cooling cycle, the first control valve 8 and the second control valve 8a are opened, and the third control valve 50 is closed. As a result, the first cooling cycle and the second cooling cycle are operated to cool the first chamber and the second chamber, respectively. Further, the first evaporator 10 and the second evaporator 10a
Is discharged from the accumulator 40 and is branched. At this time, the capacity of the first compressor 2 is reduced by the second compressor 2.
Since it is larger than a, a relatively large amount of refrigerant flows to the first compressor 2.
【０００７】一方、第２室のみを冷房する場合には第２
冷房サイクルさえ動作すればよいため、第２制御弁８ａ
は開放され、第１制御弁８及び第３制御弁５０は閉鎖さ
れる。すなわち、第２制御弁８ａは開放されている状態
なので、冷媒が第２冷房サイクルの内部を循環して第２
室を冷却させる。この際、第１制御弁８は閉鎖されてい
るため、第１冷房サイクル内では冷媒が循環されない。
更に、第３制御弁５０も閉鎖されているため、第２凝縮
器４ａから吐出された冷媒が第１冷房サイクルに流れな
くなる。On the other hand, when only the second room is cooled, the second
Since only the cooling cycle needs to be operated, the second control valve 8a
Is opened, and the first control valve 8 and the third control valve 50 are closed. That is, since the second control valve 8a is open, the refrigerant circulates inside the second cooling cycle and
Allow the room to cool. At this time, since the first control valve 8 is closed, the refrigerant is not circulated in the first cooling cycle.
Further, since the third control valve 50 is also closed, the refrigerant discharged from the second condenser 4a does not flow to the first cooling cycle.
【０００８】一方、第１室のみを冷房する場合には、第
１冷房サイクルを動作させる。のみならず、第２室より
も大きい第１室の冷却能力を向上させるために、第２冷
房サイクルの一部の構成要素、つまり第２圧縮器２ａ及
び第２凝縮器４ａを第１冷房サイクルと連係させて動作
させる。詳細に説明すれば以下の通りである。第２蒸発
器１０ａの動作を防ぐべく第２制御弁８ａは閉鎖される
が、第２冷房サイクルの第２圧縮器２ａ及び第２凝縮器
４ａを利用するべく第３制御弁５０は開放される。勿
論、第１冷房サイクルを動作させるべく第１制御弁８も
開放される。従って、第１蒸発器１０から吐出された冷
媒の一部はアキュムレータ４０で分岐されて第２圧縮器
２ａに流れるし、残りは第１圧縮器２に流れるようにな
る。第２圧縮器２ａで圧縮された冷媒は第２凝縮器４ａ
で凝縮される。第２制御弁８ａは閉鎖された状態で、第
３制御弁５０は開放された状態であるため、第２凝縮器
４ａで凝縮された冷媒は第２蒸発器１０ａに流れずに連
結管５２を介してカップリング３０に流れるようにな
る。すなわち、第２凝縮器４ａから排出された冷媒と第
１凝縮器４から排出された冷媒とがカップリング３０で
合って第１蒸発器１０に流れる。このように、第１蒸発
器１０に流れる冷媒の量を増加させることができるの
で、冷却能力も向上する。On the other hand, when cooling only the first room, the first cooling cycle is operated. In addition, in order to improve the cooling capacity of the first chamber that is larger than the second chamber, some components of the second cooling cycle, that is, the second compressor 2a and the second condenser 4a are connected to the first cooling cycle. Operate in conjunction with. The details are as follows. The second control valve 8a is closed to prevent the operation of the second evaporator 10a, but the third control valve 50 is opened to use the second compressor 2a and the second condenser 4a in the second cooling cycle. . Of course, the first control valve 8 is also opened to operate the first cooling cycle. Therefore, part of the refrigerant discharged from the first evaporator 10 is branched by the accumulator 40 and flows to the second compressor 2a, and the rest flows to the first compressor 2. The refrigerant compressed by the second compressor 2a is supplied to the second condenser 4a
Condensed. Since the second control valve 8a is closed and the third control valve 50 is open, the refrigerant condensed in the second condenser 4a does not flow to the second evaporator 10a but flows through the connecting pipe 52. The fluid flows to the coupling 30 through the coupling. That is, the refrigerant discharged from the second condenser 4a and the refrigerant discharged from the first condenser 4 are coupled by the coupling 30 and flow to the first evaporator 10. As described above, since the amount of the refrigerant flowing through the first evaporator 10 can be increased, the cooling capacity is also improved.
【０００９】[0009]
【発明が解決しようとする課題】しかし、従来のマルチ
型の空気調和機は以下のような問題点があった。 （１）第２室のみを冷房するために第２冷房サイクルの
みを動作させる場合に、第１冷房サイクルは動作しない
ものの、第１冷房サイクル内の冷媒は第２圧縮器２ａに
吸入されるため、冷媒の量が多すぎて第２圧縮器２ａの
性能が低下する。このため、全体的な冷房性能も低下す
る。 （２）第１室のみを冷房或いは第１室及び第２室を同時
冷房する場合には、第１圧縮器２及び第２圧縮器２ａの
両方が起動する。この際、電圧降下に起因して第１圧縮
器２及び第２圧縮器２ａが起動されないことを防止する
ために、第１圧縮器２及び第２圧縮器２ａは順次的に起
動する。しかしながら、第１圧縮器２が先起動する場
合、第１凝縮器４の出口端には高圧がかかり、このよう
な高圧が第２圧縮器２ａの吐出端にかかるようになる。
このため、第２圧縮器２ａが圧力不均衡に因って起動さ
れないこともある。逆に、第２圧縮器２ａが先起動する
場合にも、同様な理由により第１圧縮器２が起動されな
い問題点があった。 （３）容量の大きい方、つまり第１冷房サイクルは、室
外温度が少し高くても別問題ない。しかし、容量の小さ
い方は過負荷に敏感であるため、室外温度が少しだけ高
くても、或いは冷媒が追加又は排出されても圧縮器の過
負荷保護装置が動作するようになって圧縮器の動作が停
止する。このため、空気調和機の運転率が低下し、頻繁
な運転停止に起因して第２圧縮器２ａの寿命が短縮され
る。However, the conventional multi-type air conditioner has the following problems. (1) When only the second cooling cycle is operated to cool only the second chamber, the first cooling cycle does not operate, but the refrigerant in the first cooling cycle is sucked into the second compressor 2a. Also, the amount of the refrigerant is too large, and the performance of the second compressor 2a is reduced. For this reason, the overall cooling performance also decreases. (2) When only the first chamber is cooled or the first and second chambers are simultaneously cooled, both the first compressor 2 and the second compressor 2a are activated. At this time, the first compressor 2 and the second compressor 2a are sequentially activated in order to prevent the first compressor 2 and the second compressor 2a from being activated due to the voltage drop. However, when the first compressor 2 is started first, high pressure is applied to the outlet end of the first condenser 4, and such high pressure is applied to the discharge end of the second compressor 2a.
For this reason, the second compressor 2a may not be started due to pressure imbalance. Conversely, when the second compressor 2a is activated first, there is a problem that the first compressor 2 is not activated for the same reason. (3) In the larger cooling capacity, that is, the first cooling cycle, there is no problem even if the outdoor temperature is slightly higher. However, since the smaller capacity is more sensitive to overload, even if the outdoor temperature is slightly higher, or the refrigerant is added or discharged, the overload protection device of the compressor operates and the compressor is activated. Operation stops. For this reason, the operating rate of the air conditioner is reduced, and the life of the second compressor 2a is shortened due to frequent shutdown.
【００１０】本発明は、上記の問題点を解決するために
なされたものであり、その目的は、運転性能及び冷却性
能を向上させることのできるマルチ型の空気調和機を提
供することにある。[0010] The present invention has been made to solve the above problems, and an object of the present invention is to provide a multi-type air conditioner capable of improving operating performance and cooling performance.
【００１１】[0011]
【課題を解決するための手段】上記目的を達成するため
の本発明は、第１圧縮器、第１凝縮器、第１減圧装置、
及び第１蒸発器が順次連結されて第１室を冷却する第１
冷房サイクルと、第２圧縮器、第２凝縮器、第２減圧装
置、及び第２蒸発器が順次連結されて第２室を冷却する
第２冷房サイクルと、前記第１、第２蒸発器と前記第
１、第２圧縮器との間に設けられ、冷媒を分岐させるア
キュムレータと、前記第１凝縮器の出口に設けられるカ
ップリングと、前記カップリングと前記第２凝縮器の出
口側とを連結する連結管とを備えるマルチ型の空気調和
機であって、前記第２冷房サイクルのみの動作時に前記
第１冷房サイクルの冷媒が前記第２冷房サイクルに流入
されないように、前記第１蒸発器と前記アキュムレータ
との間には第４制御弁が設けられることを特徴とする。According to the present invention, there is provided a first compressor, a first condenser, a first pressure reducing device,
And a first evaporator sequentially connected to cool the first chamber.
A cooling cycle, a second cooling cycle in which a second compressor, a second condenser, a second decompression device, and a second evaporator are sequentially connected to cool a second chamber; and the first and second evaporators. An accumulator provided between the first and second compressors to branch the refrigerant, a coupling provided at an outlet of the first condenser, and an outlet side of the coupling and the second condenser. A multi-type air conditioner comprising: a connecting pipe for connecting the first evaporator so that refrigerant of the first cooling cycle does not flow into the second cooling cycle when only the second cooling cycle is in operation. A fourth control valve is provided between the first control valve and the accumulator.
【００１２】また、前記第１凝縮器から排出される冷媒
が、前記第２凝縮器に向かって逆流されないように、前
記連結管の所定の位置には第２チェック弁が設けられ
る。そして、前記アキュムレータと前記第１圧縮器との
間には冷媒の逆流を防止する第１チェック弁が設けられ
ることが好ましい。更に、前記第２凝縮器と前記第２蒸
発器との間には、補助減圧装置及び補助制御弁が前記第
２減圧装置及び第２制御弁と並列設置されることが好ま
しい。このように構成すれば、マルチ型の空気調和機の
運転性能及び冷却性能を向上させることができる。Further, a second check valve is provided at a predetermined position of the connecting pipe so that the refrigerant discharged from the first condenser does not flow backward toward the second condenser. It is preferable that a first check valve for preventing a backflow of the refrigerant is provided between the accumulator and the first compressor. Further, between the second condenser and the second evaporator, an auxiliary pressure reducing device and an auxiliary control valve are preferably installed in parallel with the second pressure reducing device and the second control valve. With this configuration, the operation performance and the cooling performance of the multi-type air conditioner can be improved.
【００１３】[0013]
【発明の実施の形態】以下、本発明の好適な実施の形態
を添付図面を参照して説明する。図１は本発明の一実施
の形態を示す構成図であり、これを参照して本発明のマ
ルチ型の空気調和機を説明する。従来と同様な構成要素
は同じ名称及び同じ符号を付けてその説明を省略する。
まず、第２室のみの冷房時に、第１冷房サイクル内の冷
媒が第２圧縮器２ａに流入されないように、第１蒸発器
１０とアキュムレータ４０との間に冷媒流れ制御用の第
４制御弁１０６が設けられる。そして、第１室のみの運
転時に、第１冷房サイクルの第１凝縮器４から流出され
た冷媒が第２冷房サイクルへ流入されて第２圧縮器２ａ
の吐出端に高圧がかかることを防止するために、第１冷
房サイクルと第２冷房サイクルとを連結する連結管５２
の所定の位置には冷媒逆流防止用の第２チェック弁１０
２が設けられる。前記第２チェック弁１０２は、第２凝
縮器４ａの出口側と第３制御弁５０との間に設けられる
ことが好ましい。また、アキュムレータ４０と第１圧縮
器２との間には冷媒逆流防止用の第１チェック弁１０４
が設けられることが好ましい。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the accompanying drawings. FIG. 1 is a configuration diagram showing an embodiment of the present invention, and a multi-type air conditioner of the present invention will be described with reference to FIG. The same components as those in the related art are given the same names and the same reference numerals, and description thereof is omitted.
First, a fourth control valve for controlling a refrigerant flow between the first evaporator 10 and the accumulator 40 so that the refrigerant in the first cooling cycle does not flow into the second compressor 2a when only the second chamber is cooled. 106 is provided. Then, when only the first chamber is operated, the refrigerant flowing out of the first condenser 4 in the first cooling cycle flows into the second cooling cycle, and the second compressor 2a
Connection pipe 52 connecting the first cooling cycle and the second cooling cycle to prevent high pressure from being applied to the discharge end of
The second check valve 10 for preventing the backflow of the refrigerant is provided at a predetermined position.
2 are provided. The second check valve 102 is preferably provided between the outlet side of the second condenser 4a and the third control valve 50. Further, a first check valve 104 for preventing refrigerant backflow is provided between the accumulator 40 and the first compressor 2.
Is preferably provided.
【００１４】一方、図２に示すように、第２冷房サイク
ルにおいては、第２室の温度を感知し、第２冷房サイク
ルの過負荷状態の時に直ぐに前記第２冷房サイクルに冷
媒を補充するために、第２凝縮器４ａと第２蒸発器１０
ａとの間には補助減圧装置２０２と補助制御弁２０４が
設けられる。前記補助減圧装置２０２及び補助制御弁２
０４は前記第２減圧装置６ａと前記第２制御弁８ａと並
列設置される。On the other hand, as shown in FIG. 2, in the second cooling cycle, the temperature of the second chamber is sensed, and the refrigerant is replenished to the second cooling cycle immediately when the second cooling cycle is overloaded. The second condenser 4a and the second evaporator 10
The auxiliary pressure reducing device 202 and the auxiliary control valve 204 are provided between the auxiliary pressure reducing device 202 and the auxiliary pressure reducing device 202. The auxiliary pressure reducing device 202 and the auxiliary control valve 2
04 is installed in parallel with the second pressure reducing device 6a and the second control valve 8a.
【００１５】以下、上記のような本発明のマルチ型の空
気調和機の作用を図１、図２を参照して説明する。ま
ず、第１室と第２室の同時運転する場合には、第１冷房
サイクルを動作させるべく第１制御弁８と第４制御弁１
０６を開放し、第２冷房サイクルを動作させるべく第２
制御弁８ａを開放する。そして、第１冷房サイクル、第
２冷房サイクルを個々に運転するべく第３制御弁５０を
閉鎖する。これにより、冷媒は、第１冷房サイクル、第
２冷房サイクルを各々循環しながら第１室及び第２を各
々冷房する。Hereinafter, the operation of the multi-type air conditioner of the present invention as described above will be described with reference to FIGS. First, when the first and second chambers are operated simultaneously, the first control valve 8 and the fourth control valve 1 are operated to operate the first cooling cycle.
06 to release the second cooling cycle.
The control valve 8a is opened. Then, the third control valve 50 is closed to individually operate the first cooling cycle and the second cooling cycle. Thereby, the refrigerant cools the first chamber and the second while circulating through the first cooling cycle and the second cooling cycle, respectively.
【００１６】一方、過負荷のかからない正常条件下で
は、補助制御弁２０４は閉鎖された状態である。このた
め、冷媒は、第２圧縮器２ａ、第２凝縮器４ａ、第２減
圧装置６ａ、及び第２蒸発器１０ａを循環しながら第２
室を冷却する。しかし、温度感知センサ（図示せず）が
外気の温度を感知し、感知された室外側の温度が一定温
度以上、例えば４２℃以上である場合には、第２冷房サ
イクルを流れる冷媒の量を補充するために補助制御弁２
０４を開放する。これにより、冷媒が、第２減圧装置６
ａ及び第２制御弁６ａだけでなく補助減圧装置２０２、
補助制御弁２０４を介しても流れる。このように、冷媒
の流量を増大させることで冷媒不足現象を前もって防止
することができる。結局、第２冷房サイクルを循環する
冷媒の不足現象を防止して、過負荷保護装置の動作を防
止し、これによってマルチ型の空気調和機を継続的に円
滑に作動させることができる。On the other hand, under a normal condition in which no overload is applied, the auxiliary control valve 204 is in a closed state. For this reason, the refrigerant circulates through the second compressor 2a, the second condenser 4a, the second decompression device 6a, and the second evaporator 10a, and
Cool the room. However, when a temperature sensor (not shown) detects the temperature of the outside air and the detected outdoor temperature is equal to or higher than a predetermined temperature, for example, equal to or higher than 42 ° C., the amount of the refrigerant flowing through the second cooling cycle is reduced. Auxiliary control valve 2 to refill
Release 04. Thereby, the refrigerant is supplied to the second pressure reducing device 6
a and the second control valve 6a as well as the auxiliary pressure reducing device 202,
It also flows through the auxiliary control valve 204. In this way, the refrigerant shortage phenomenon can be prevented in advance by increasing the flow rate of the refrigerant. As a result, the shortage of the refrigerant circulating in the second cooling cycle is prevented, and the operation of the overload protection device is prevented, whereby the multi-type air conditioner can be continuously and smoothly operated.
【００１７】次に、第２室のみを冷房する場合について
説明する。この時は、従来と同様に第２冷房サイクルさ
え動作すればよいため、第２制御弁８ａは開放され、第
１制御弁８及び第３制御弁５０は閉鎖される。単に、本
発明のマルチ型の空気調和機では第４制御弁１０６も閉
鎖される。このため、第１冷房サイクル内の冷媒が第２
圧縮器２ａへ流入されることが効率よく防止される。従
って、第１冷房サイクル内に過多な冷媒が循環すること
が防止されるので、空気調和機の性能低下が防止され
る。Next, a case where only the second chamber is cooled will be described. At this time, since only the second cooling cycle needs to be operated as in the conventional case, the second control valve 8a is opened, and the first control valve 8 and the third control valve 50 are closed. Simply, in the multi-type air conditioner of the present invention, the fourth control valve 106 is also closed. For this reason, the refrigerant in the first cooling cycle
Flow into the compressor 2a is efficiently prevented. Therefore, since excessive refrigerant is prevented from circulating in the first cooling cycle, performance degradation of the air conditioner is prevented.
【００１８】次に、第１室のみを冷房する場合について
説明する。第１室のみを運転する場合には、従来と同様
に、主に第１冷房サイクルを動作させるし、冷却能力を
向上させるために第２冷房サイクルの第２圧縮器２ａ及
び第２凝縮器４ａをも動作させる。すなわち、第１冷房
サイクルの動作のために第１制御弁８は開放される。
又、冷媒が第２蒸発器１０ａには流れずに第２圧縮器２
ａ及び第２凝縮器４ａにのみ流れるように、第２制御弁
８ａは閉鎖され、第３制御弁５０は開放される。従っ
て、第１蒸発器１０から吐出された冷媒の一部はアキュ
ムレータ４０で分岐されて第２圧縮器２ａ及び第２凝縮
器４ａを経由してカップリング３０で第１凝縮器からの
冷媒と合って第１蒸発器１０に流れる。この際、電圧降
下に因って圧縮器が起動されないことがないように、第
１圧縮器２及び第２圧縮器２ａが順次的に起動する。第
１圧縮器２が起動する場合、前記第１圧縮器２で圧縮さ
れた冷媒は第１凝縮器４で凝縮されてカップリング３０
に向かって排出される。従って、第１圧縮器２の動作に
よる高圧が、第２圧縮器２ａ側にかかるようになる。し
かし、本発明では、前記連結管５２に設けられた第２チ
ェック弁１０２により、第１圧縮器４から流入された冷
媒が第２冷房サイクルへ逆流されることが防止される。
従って、第２圧縮器２ａが、第１圧縮器２の起動による
高圧に因って起動されないことがない。Next, a case where only the first room is cooled will be described. When only the first chamber is operated, as in the prior art, the first cooling cycle is mainly operated, and the second compressor 2a and the second condenser 4a of the second cooling cycle are used in order to improve the cooling capacity. Also work. That is, the first control valve 8 is opened for the operation of the first cooling cycle.
Also, the refrigerant does not flow to the second evaporator 10a and the second compressor 2
The second control valve 8a is closed and the third control valve 50 is opened so that only the fluid flows into the second condenser 4a and the second condenser 4a. Therefore, a part of the refrigerant discharged from the first evaporator 10 is branched by the accumulator 40 and matches the refrigerant from the first condenser by the coupling 30 via the second compressor 2a and the second condenser 4a. And flows to the first evaporator 10. At this time, the first compressor 2 and the second compressor 2a are sequentially activated so that the compressor is not activated due to the voltage drop. When the first compressor 2 is started, the refrigerant compressed by the first compressor 2 is condensed by the first condenser 4 and the coupling 30
It is discharged toward. Therefore, the high pressure generated by the operation of the first compressor 2 is applied to the second compressor 2a. However, in the present invention, the second check valve 102 provided in the connection pipe 52 prevents the refrigerant flowing from the first compressor 4 from flowing back to the second cooling cycle.
Therefore, the second compressor 2a is not activated due to the high pressure caused by the activation of the first compressor 2.
【００１９】[0019]
【発明の効果】上述したような本発明のマルチ型の空気
調和機の効果は以下の通りである。 （１）第２室の冷房時に、第１冷房サイクル内の冷媒が
第２冷房サイクルへ逆流して冷媒量があまりに多くなっ
て圧縮器の性能が低下する、ことが防止されるので、空
気調和機の性能低下が効率よく防止される。 （２）第１圧縮器２及び第２圧縮器２ａの順次起動時
に、先起動した圧縮器による高圧に起因して他の圧縮器
が起動されない、ことが防止されるので、空気調和機の
運転性能及び冷却性能が向上する。 （３）容量の小さい第２冷房サイクルが過負荷条件であ
る時に過負荷保護装置が作動して圧縮器が運転停止され
る、ことが防止されるので、空気調和機の運転率が向上
するとともに、第２圧縮器２ａの寿命短縮が防止され
る。本発明は、上記において一実施形態のみを説明した
が、これに限らず、請求範囲を逸脱しない範囲内で本発
明の属する技術分野において通常の知識を有する者によ
って変形可能であることはいうまでもない。The effects of the multi-type air conditioner of the present invention as described above are as follows. (1) During cooling of the second chamber, it is prevented that the refrigerant in the first cooling cycle flows backward to the second cooling cycle and the amount of the refrigerant is excessively increased, thereby lowering the performance of the compressor. The performance of the machine is efficiently prevented from deteriorating. (2) When the first compressor 2 and the second compressor 2a are sequentially started, it is prevented that another compressor is not started due to the high pressure of the previously started compressor, so that the operation of the air conditioner is prevented. Performance and cooling performance are improved. (3) Since the overload protection device is prevented from operating and the compressor being shut down when the second cooling cycle having a small capacity is under the overload condition, the operation rate of the air conditioner is improved. The life of the second compressor 2a is not shortened. Although the present invention has been described with reference to only one embodiment, the present invention is not limited to this embodiment. Needless to say, the present invention can be modified by persons having ordinary knowledge in the technical field to which the present invention belongs without departing from the scope of the claims. Nor.
【図１】本発明のマルチ型の空気調和機の実施の形態を
示す構成図である。FIG. 1 is a configuration diagram showing an embodiment of a multi-type air conditioner of the present invention.
【図２】本発明のマルチ型の空気調和機の他の実施の形
態を示す構成図である。FIG. 2 is a configuration diagram showing another embodiment of the multi-type air conditioner of the present invention.
【図３】従来のマルチ型の空気調和機の構成を概略的に
示す構成図である。FIG. 3 is a configuration diagram schematically showing a configuration of a conventional multi-type air conditioner.
２…第１圧縮器 ２ａ…第２圧縮器 ４…第１凝縮器 ４ａ…第２凝縮器 ６…第１減圧装置 ６ａ…第２減圧装置 ８…第１制御弁 ８ａ…第２制御弁 １０…第１蒸発器 １０ａ…第２蒸発器 ３０…カップリング ４０…アキュムレータ ５０…第３制御弁 ５２…連結管 １０２…第２チェック弁 １０４…第１チェック弁 １０６…第４制御弁 ２０２…補助減圧装置 ２０４…補助制御弁 2 1st compressor 2a 2nd compressor 4 1st condenser 4a 2nd condenser 6 1st decompression device 6a 2nd decompression device 8 ... 1st control valve 8a ... 2nd control valve 10 ... First evaporator 10a Second evaporator 30 Coupling 40 Accumulator 50 Third control valve 52 Connecting pipe 102 Second check valve 104 First check valve 106 Fourth control valve 202 Auxiliary pressure reducing device 204: auxiliary control valve
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 平６−249527（ＪＰ，Ａ) 実開 昭57−54865（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F25B 1/00 F25B 13/00 ＷＰＩ（ＤＩＡＬＯＧ)──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-6-249527 (JP, A) JP-A-57-54865 (JP, U) (58) Fields investigated (Int. Cl. 7 , DB name) F25B 1/00 F25B 13/00 WPI (DIALOG)
Claims (4)
置、及び第１蒸発器が順次連結されて第１室を冷却する
第１冷房サイクルと、第２圧縮器、第２凝縮器、第２減
圧装置、及び第２蒸発器が順次連結されて第２室を冷却
する第２冷房サイクルと、前記第１、第２蒸発器と前記
第１、第２圧縮器との間に設けられ、冷媒を分岐させる
アキュムレータと、前記第１凝縮器の出口に設けられる
カップリングと、前記カップリングと前記第２凝縮器の
出口側とを連結する連結管とを備えるマルチ型の空気調
和機であって、 前記第２冷房サイクルのみの動作時に前記第１冷房サイ
クルの冷媒が前記第２冷房サイクルへ流入されないよう
に、前記第１蒸発器と前記アキュムレータとの間には第
４制御弁が設けられることを特徴とするマルチ型の空気
調和機。1. A first cooling cycle in which a first compressor, a first condenser, a first decompression device, and a first evaporator are sequentially connected to cool a first chamber, a second compressor, and a second condenser. A second cooling cycle for cooling the second chamber by sequentially connecting the heat exchanger, the second decompression device, and the second evaporator, and between the first and second evaporators and the first and second compressors. A multi-type air conditioner provided with an accumulator for branching a refrigerant, a coupling provided at an outlet of the first condenser, and a connecting pipe connecting the coupling and an outlet side of the second condenser. A fourth control valve between the first evaporator and the accumulator so that the refrigerant of the first cooling cycle does not flow into the second cooling cycle during the operation of only the second cooling cycle. Multi-type air conditioning characterized by being provided with .
記第２凝縮器に向かって逆流されないように、前記連結
管の所定の位置には第２チェック弁が設けられることを
特徴とする請求項１記載のマルチ型の空気調和機。2. A second check valve is provided at a predetermined position of the connection pipe so that refrigerant discharged from the first condenser does not flow backward toward the second condenser. The multi-type air conditioner according to claim 1.
の間には冷媒逆流防止用の第１チェック弁が設けられる
ことを特徴とする請求項１又は２記載のマルチ型の空気
調和機。3. The multi-type air conditioner according to claim 1, wherein a first check valve for preventing a backflow of the refrigerant is provided between the accumulator and the first compressor.
置、及び第１蒸発器が順次連結されて第１室を冷却する
第１冷房サイクルと、第２圧縮器、第２凝縮器、第２減
圧装置、及び第２蒸発器が順次連結されて第２室を冷却
する第２冷房サイクルと、前記第１、第２蒸発器と前記
第１、第２圧縮器との間に設けられ、冷媒を分岐させる
アキュムレータと、前記第１凝縮器の出口に設けられる
カップリングと、前記カップリングと前記第２凝縮器の
出口側とを連結する連結管とを備えるマルチ型の空気調
和機であって、 前記第２凝縮器と前記第２蒸発器との間には補助減圧装
置及び補助制御弁が前記第２減圧装置及び第２制御弁と
並列設置されており、外気の温度が所定値以上の場合に
は前記補助制御弁が開放されて冷媒が補充されることを
特徴とするマルチ型の空気調和機。4. A first cooling cycle in which a first compressor, a first condenser, a first decompression device, and a first evaporator are sequentially connected to cool a first chamber, a second compressor, and a second condenser. A second cooling cycle for cooling the second chamber by sequentially connecting the heat exchanger, the second decompression device, and the second evaporator, and between the first and second evaporators and the first and second compressors. A multi-type air conditioner provided with an accumulator for branching a refrigerant, a coupling provided at an outlet of the first condenser, and a connecting pipe connecting the coupling and an outlet side of the second condenser. An auxiliary pressure reducing device and an auxiliary control valve are installed in parallel with the second pressure reducing device and the second control valve between the second condenser and the second evaporator, and the temperature of the outside air is reduced. When the pressure is equal to or more than a predetermined value, the auxiliary control valve is opened and the refrigerant is replenished. Multi-type air conditioner of that.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR63360/1997 | 1997-11-27 | ||
| KR63359/1997 | 1997-11-27 | ||
| KR1019970063360A KR100239463B1 (en) | 1997-11-27 | 1997-11-27 | Refrigerating cycle for multi type air conditioner |
| KR1019970063359A KR100239476B1 (en) | 1997-11-27 | 1997-11-27 | Refrigerating cycle for multi type air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH11325641A JPH11325641A (en) | 1999-11-26 |
| JP2999763B2 true JP2999763B2 (en) | 2000-01-17 |
Family
ID=26633202
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10337699A Expired - Fee Related JP2999763B2 (en) | 1997-11-27 | 1998-11-27 | Multi type air conditioner |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP2999763B2 (en) |
| CN (1) | CN1161566C (en) |
| ES (1) | ES2169958B1 (en) |
| IT (1) | IT1303183B1 (en) |
| TR (1) | TR199802448A2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105910238B (en) * | 2016-05-13 | 2019-03-08 | 广东美的暖通设备有限公司 | Multi-online air-conditioning system and its communication means and communication device |
| CN109477696B (en) * | 2016-09-09 | 2021-04-09 | 株式会社电装 | Equipment temperature adjusting device |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2839343B2 (en) * | 1990-08-10 | 1998-12-16 | 株式会社日立製作所 | Multi air conditioner |
| JPH06201176A (en) * | 1992-12-28 | 1994-07-19 | Toshiba Corp | Air-conditioner |
| JP3060770B2 (en) * | 1993-02-26 | 2000-07-10 | ダイキン工業株式会社 | Refrigeration equipment |
| JP3092421B2 (en) * | 1993-12-22 | 2000-09-25 | ダイキン工業株式会社 | Multi-room air conditioner |
-
1998
- 1998-11-26 TR TR1998/02448A patent/TR199802448A2/en unknown
- 1998-11-27 CN CNB981249949A patent/CN1161566C/en not_active Expired - Fee Related
- 1998-11-27 IT IT1998TO000999A patent/IT1303183B1/en active IP Right Grant
- 1998-11-27 JP JP10337699A patent/JP2999763B2/en not_active Expired - Fee Related
- 1998-11-27 ES ES009802499A patent/ES2169958B1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| CN1161566C (en) | 2004-08-11 |
| IT1303183B1 (en) | 2000-10-30 |
| TR199802448A3 (en) | 2000-02-21 |
| ES2169958A1 (en) | 2002-07-16 |
| ITTO980999A0 (en) | 1998-11-27 |
| TR199802448A2 (en) | 2000-02-21 |
| ES2169958B1 (en) | 2003-11-01 |
| JPH11325641A (en) | 1999-11-26 |
| CN1231400A (en) | 1999-10-13 |
| ITTO980999A1 (en) | 2000-05-27 |
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