JP3228135B2 - Refrigeration equipment - Google Patents
Refrigeration equipmentInfo
- Publication number
- JP3228135B2 JP3228135B2 JP19338696A JP19338696A JP3228135B2 JP 3228135 B2 JP3228135 B2 JP 3228135B2 JP 19338696 A JP19338696 A JP 19338696A JP 19338696 A JP19338696 A JP 19338696A JP 3228135 B2 JP3228135 B2 JP 3228135B2
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- refrigerant
- compressor
- pressure
- branch pipe
- 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
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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/029—Control issues
- F25B2313/0294—Control issues related to the outdoor fan, e.g. controlling speed
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、例えば空気調和機
などに適用される冷凍装置に係り、特に、熱源側熱交換
器に隣接して補助熱交換器を設け、利用側熱交換器の放
熱運転時の過渡時に、圧縮機からの吐出冷媒の一部を補
助熱交換器に分流するようにしたものの改良に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigeration system applied to, for example, an air conditioner, and more particularly, to an auxiliary heat exchanger provided adjacent to a heat source side heat exchanger, and a heat radiation of a use side heat exchanger. The present invention relates to an improvement of a system in which a part of refrigerant discharged from a compressor is diverted to an auxiliary heat exchanger during a transient operation.
【０００２】[0002]
【従来の技術】従来より、空気調和機に適用される冷凍
装置として、例えば特開平６−３３７１７４号公報に開
示されているような冷媒回路を備えたものが知られてい
る。この冷媒回路は、圧縮機と、室内熱交換器と、電動
膨張弁と、室外熱交換器とが冷媒配管によって順に接続
された主冷媒回路を備えている。そして、この主冷媒回
路に対し、上記室外熱交換器と電動膨張弁とに対して並
列に補助ラインが接続されている。この補助ラインに
は、上記室外熱交換器と共通の空気通路に配置された補
助熱交換器と、キャピラリチューブと、開閉弁とが設け
られている。また、上記空気通路には室外ファンが設け
られている。2. Description of the Related Art Conventionally, as a refrigerating apparatus applied to an air conditioner, there is known a refrigerating apparatus having a refrigerant circuit as disclosed in, for example, JP-A-6-337174. This refrigerant circuit includes a main refrigerant circuit in which a compressor, an indoor heat exchanger, an electric expansion valve, and an outdoor heat exchanger are sequentially connected by refrigerant piping. An auxiliary line is connected to the main refrigerant circuit in parallel with the outdoor heat exchanger and the electric expansion valve. The auxiliary line is provided with an auxiliary heat exchanger arranged in an air passage common to the outdoor heat exchanger, a capillary tube, and an on-off valve. An outdoor fan is provided in the air passage.
【０００３】そして、暖房運転時等における過渡時に、
高圧冷媒圧力が過上昇した場合には、上記開閉弁を開い
て補助ラインに吐出ガス冷媒の一部を逃がす。そして、
この冷媒を補助熱交換器で凝縮した後、キャピラリチュ
ーブで減圧し、室外熱交換器に導入することで高圧冷媒
圧力の上昇を抑制する。At the time of a transition such as a heating operation,
When the high-pressure refrigerant pressure rises excessively, the on-off valve is opened to allow a part of the discharged gas refrigerant to escape to the auxiliary line. And
After the refrigerant is condensed by the auxiliary heat exchanger, the pressure is reduced by the capillary tube and introduced into the outdoor heat exchanger to suppress an increase in the high-pressure refrigerant pressure.
【０００４】[0004]
【発明が解決しようとする課題】しかしながら、上述の
ような回路構成にあっては、補助ラインの下流端が、暖
房運転時における電動膨張弁の上流側、つまり、中間圧
部分に接続しているために、圧縮機の吐出圧との差圧が
十分に得られない。つまり、補助ラインの上流端と下流
端との差圧を大きく得ることができない。このため、補
助熱交換器の冷媒流量を十分に得ることができず、高圧
冷媒圧力の上昇抑制を確実に行うことができない可能性
があった。However, in the above-described circuit configuration, the downstream end of the auxiliary line is connected to the upstream side of the electric expansion valve during the heating operation, that is, to the intermediate pressure portion. Therefore, a sufficient differential pressure from the discharge pressure of the compressor cannot be obtained. That is, a large differential pressure between the upstream end and the downstream end of the auxiliary line cannot be obtained. For this reason, the flow rate of the refrigerant in the auxiliary heat exchanger cannot be sufficiently obtained, and there is a possibility that the increase in the high-pressure refrigerant pressure cannot be reliably suppressed.
【０００５】そこで、この高圧冷媒圧力の上昇抑制を確
実に行うために補助熱交換器の能力を大きく得ようとす
る場合、室外ファンの回転数を上昇させ、該補助熱交換
器を通過する空気量を増大させることが考えられる。[0005] Therefore, in order to obtain a large capacity of the auxiliary heat exchanger in order to reliably suppress the increase in the pressure of the high-pressure refrigerant, the rotational speed of the outdoor fan is increased and the air passing through the auxiliary heat exchanger is increased. It is conceivable to increase the amount.
【０００６】ところが、この場合、上述したように、補
助熱交換器と室外熱交換器とは共通の空気通路に設置さ
れているため、室外熱交換器を通過する空気量も増大す
ることになり、該室外熱交換器の能力も増大してしま
う。これでは、高圧冷媒圧力の上昇を抑制できなくなる
可能性がある。However, in this case, as described above, since the auxiliary heat exchanger and the outdoor heat exchanger are installed in a common air passage, the amount of air passing through the outdoor heat exchanger also increases. In addition, the capacity of the outdoor heat exchanger also increases. This may make it impossible to suppress an increase in the high-pressure refrigerant pressure.
【０００７】この不具合を解消するためには、補助熱交
換器を大型化し、十分な凝縮能力が得られるようにする
ことが考えられるが、このように補助熱交換器を大型化
する場合、室外ユニット全体の大型化を招くことになり
実用性に欠ける。また、室外ユニット全体を大型化する
ことなしに補助熱交換器を大型化しようとすると、熱交
換器の設置スペースの制約から、室外熱交換器を小型化
せねばならなくなり、本来の空調能力の低下に繋ってし
まう。In order to solve this problem, it is conceivable to increase the size of the auxiliary heat exchanger so as to obtain a sufficient condensing capacity. This leads to an increase in the size of the entire unit, and lacks practicality. Also, if the size of the auxiliary heat exchanger is increased without increasing the size of the entire outdoor unit, the size of the outdoor heat exchanger must be reduced due to the limited installation space of the heat exchanger. It leads to decline.
【０００８】更に、サーモオフ時などにおいて、圧縮機
が停止している場合には、高圧液ラインの液冷媒が、補
助ラインを逆流し、圧縮機に対し、その吐出側から導入
する虞れがあるため、電動膨張弁だけでなく補助ライン
の電磁弁をも閉鎖しておく必要がある。しかし、この電
磁弁として、冷媒の一方向（補助熱交換器から室外熱交
換器へ向って流れる方向）の流通のみを許容或いは規制
するものを採用した場合には、この逆流に対して流通を
阻止することができないことがある。従って、この電磁
弁としては双方向の冷媒の流通に対してその規制が行え
るものを採用しておかねばならず、コストの増大を招く
ことになっていた。Further, when the compressor is stopped, for example, at the time of thermo-off, the liquid refrigerant in the high-pressure liquid line may flow back through the auxiliary line and be introduced into the compressor from the discharge side. Therefore, it is necessary to close not only the electric expansion valve but also the solenoid valve of the auxiliary line. However, when a solenoid valve that permits or regulates only the flow in one direction of the refrigerant (the direction in which the refrigerant flows from the auxiliary heat exchanger toward the outdoor heat exchanger) is adopted, the flow is prevented in response to the reverse flow. Sometimes it cannot be stopped. Therefore, the electromagnetic valve must be able to regulate the flow of the refrigerant in both directions, which leads to an increase in cost.
【０００９】また、この液冷媒の逆流を阻止するための
他の手段として、高圧液ラインに設けられるレシーバに
ガス抜きのための回路を接続したり、補助ラインに逆流
防止用の逆止弁を設けたりすることも考えられるが、前
者のものでは回路構成の複雑化を招き、また、後者のも
のでは部品点数の増加を招くため好ましくない。Further, as other means for preventing the backflow of the liquid refrigerant, a circuit for venting gas is connected to a receiver provided in the high-pressure liquid line, and a check valve for preventing backflow is provided in the auxiliary line. Although it is conceivable to provide them, the former is not preferable because the circuit configuration becomes complicated, and the latter one increases the number of components.
【００１０】本発明は、これらの点に鑑みてなされたも
のであって、その目的は、補助ラインの上流端と下流端
との差圧を大きく得ることで、補助熱交換器の大型化を
招いたり、回路構成の複雑化や、部品点数の増加を生じ
させることを回避しながら、高圧冷媒圧力の上昇抑制を
確実に行うことにある。The present invention has been made in view of these points, and an object of the present invention is to obtain a large differential pressure between an upstream end and a downstream end of an auxiliary line, thereby increasing the size of the auxiliary heat exchanger. An object of the present invention is to surely suppress an increase in the high-pressure refrigerant pressure while avoiding inviting or complicating the circuit configuration and increasing the number of parts.
【００１１】[0011]
【課題を解決するための手段】上記の目的を達成するた
めに、本発明は、補助ラインの下流端を、膨張弁よりも
下流側、つまり、低圧側に接続することで、補助ライン
の上流端と下流端との差圧を大きく確保し、補助ライン
の冷媒流量が十分に得られるようにした。In order to achieve the above-mentioned object, the present invention is to connect the downstream end of the auxiliary line to the downstream side of the expansion valve, that is, to the low pressure side, so that the upstream side of the auxiliary line is connected. A large differential pressure between the end and the downstream end was ensured to ensure a sufficient refrigerant flow rate in the auxiliary line.
【００１２】具体的に、請求項１記載の発明は、図１に
示すように、圧縮機(1)、利用側熱交換器(12)、膨張機
構(5,6)及び熱源側熱交換器(3,4)が冷媒配管(10)により
接続されてなる主冷媒回路(C)を備え、圧縮機(1)からの
吐出冷媒を、利用側熱交換器(12)で凝縮し、膨張機構
(5,6)で減圧した後、熱源側熱交換器(3,4)で蒸発する冷
媒循環動作を行う冷凍装置を前提とする。Specifically, as shown in FIG. 1, the invention according to claim 1 includes a compressor (1), a use side heat exchanger (12), an expansion mechanism (5, 6), and a heat source side heat exchanger. (3, 4) is provided with a main refrigerant circuit (C) connected by a refrigerant pipe (10), the refrigerant discharged from the compressor (1) is condensed in the use side heat exchanger (12), and an expansion mechanism is provided.
It is assumed that the refrigerating apparatus performs a refrigerant circulation operation of evaporating in the heat source side heat exchangers (3, 4) after the pressure is reduced in (5, 6).
【００１３】そして、上記冷媒配管(10)の一部が分岐さ
れて成る並列な第１及び第２の分岐配管(10a,10b)が設
けられている。上記熱源側熱交換器(3,4)は、第１分岐
管(10a)に設けられた第１熱交換器(3)と、第２分岐管(1
0b)に設けられた第２熱交換器(4)とを備え、該第１熱交
換器(3)と第２熱交換器(4)とは、各々個別の空気通路に
配設されていて、各空気通路には、第１熱交換器(3)に
対向して第１ファン(F1)が、第２熱交換器(4)に対向し
て第２ファン(F2)が夫々設けられている。上記膨張機構
(5,6)は、第１分岐管(10a)に設けられた第１膨張機構
(5)と、第２分岐管(10b)に設けられた第２膨張機構(6)
とを備えている。 A part of the refrigerant pipe (10) is branched.
Parallel first and second branch pipes (10a, 10b)
Have been killed. The heat source side heat exchangers (3, 4) are in the first branch
The first heat exchanger (3) provided in the pipe (10a) and the second branch pipe (1
0b) and a second heat exchanger (4) provided in the first heat exchanger.
Heat exchanger (3) and the second heat exchanger (4)
Each air passage is connected to the first heat exchanger (3).
The first fan (F1) faces the second heat exchanger (4)
And second fans (F2) are provided respectively. The above expansion mechanism
(5, 6) is a first expansion mechanism provided in the first branch pipe (10a).
(5) and a second expansion mechanism (6) provided in the second branch pipe (10b).
And
【００１４】加えて、上記圧縮機(1)の吐出圧力の過上
昇時に吐出冷媒の一部を導いて該冷媒を凝縮する熱源側
補助熱交換器(21)が、上流側を圧縮機(1)の吐出側に、
下流側を第１膨張機構(5)と第１熱交換器(3)との間に夫
々接続して設けられると共に、熱源側補助熱交換器(21)
は、第２熱交換器(4)と共通の空気通路に設けられ、圧
縮機(1)の吐出圧力の過上昇時、第２ファン(F2)の送風
量を第１ファン(F1)の送風量よりも大きく設定する。In addition, when the discharge pressure of the compressor (1) rises excessively, a heat source side auxiliary heat exchanger (21) for guiding a part of the discharged refrigerant and condensing the refrigerant is provided on the upstream side of the compressor (1). ) On the discharge side,
The downstream side is provided to be connected between the first expansion mechanism (5) and the first heat exchanger (3), respectively, and the heat source side auxiliary heat exchanger (21)
Is provided in a common air passage with the second heat exchanger (4),
When the discharge pressure of the compressor (1) rises excessively, the second fan (F2) blows air.
The amount is set to be larger than the amount of air blown by the first fan (F1) .
【００１５】この発明の特定事項により、圧縮機(1)の
吐出圧力が過上昇した場合には、圧縮機(1)からの吐出
冷媒の一部が熱源側補助熱交換器(21)に導入して凝縮す
ることで、吐出圧力の上昇を抑制する。この際、熱源側
補助熱交換器(21)の下流側は、膨張機構(5)よりも下流
側、つまり、低圧側に接続しているので、この補助熱交
換器(21)の上流側と下流側との差圧は大きく確保されて
おり、該補助熱交換器(21)における冷媒流量は十分に確
保される。つまり、この補助熱交換器(21)の凝縮能力が
十分に得られて吐出圧力の上昇が確実に抑制できる。According to the particulars of the present invention, when the discharge pressure of the compressor (1) rises excessively, a part of the refrigerant discharged from the compressor (1) is introduced into the heat source side auxiliary heat exchanger (21). And condenses, thereby suppressing an increase in the discharge pressure. At this time, since the downstream side of the heat source side auxiliary heat exchanger (21) is connected to the downstream side of the expansion mechanism (5), that is, the low pressure side, the upstream side of the auxiliary heat exchanger (21) A large differential pressure with the downstream side is ensured, and the flow rate of the refrigerant in the auxiliary heat exchanger (21) is sufficiently ensured. That is, the condensing capacity of the auxiliary heat exchanger (21) is sufficiently obtained, and the rise of the discharge pressure can be reliably suppressed.
【００１６】更に、第１熱交換器(3)では通過空気量が
少ないことにより蒸発能力が低減する。つまり、回路全
体としての蒸発能力は低く抑えられる。一方、補助熱交
換器(21)では、第２ファン(F2)により通過空気量が大き
く確保されて凝縮能力が増大している。つまり、回路全
体としての凝縮能力は高くなっている。このため、吐出
圧力の上昇が確実に抑制される。 Further, in the first heat exchanger (3), the amount of passing air is
The smaller the amount, the lower the evaporation ability. In other words, the entire circuit
Evaporation ability as a body is kept low. Meanwhile, auxiliary heat exchange
In the heat exchanger (21), the amount of passing air is large due to the second fan (F2).
And the condensing capacity is increasing. In other words, the entire circuit
The ability to condense as a body is increasing. Therefore, the discharge
An increase in pressure is reliably suppressed.
【００１７】請求項２記載の発明は、図２に示すよう
に、圧縮機(1)、利用側熱交換器(12)、膨張機構(5,6)及
び熱源側熱交換器(3,4)が冷媒配管(10)により接続され
てなる主冷媒回路(C)を備え、該主冷媒回路(C)は、圧縮
機(1)の吸入側にアキュムレータ(8)が設けられ、圧縮機
(1)からの吐出冷媒を、利用側熱交換器(12)で凝縮し、
膨張機構(5,6)で減圧した後、熱源側熱交換器(3,4)で蒸
発する冷媒循環動作を行う冷凍装置を前提とする。 The invention according to claim 2 is as shown in FIG.
In addition, the compressor (1), the use side heat exchanger (12), the expansion mechanism (5, 6) and
And the heat source side heat exchangers (3, 4) are connected by refrigerant piping (10).
A main refrigerant circuit (C) comprising:
An accumulator (8) is provided on the suction side of the
The refrigerant discharged from (1) is condensed in the use-side heat exchanger (12),
After the pressure is reduced by the expansion mechanism (5, 6), the steam is
It is assumed that the refrigerating device performs a generated refrigerant circulation operation.
【００１８】そして、上記冷媒配管(10)の一部が分岐さ
れて成る並列な第１及び第２の分岐配管(10a,10b)が設
けられている。上記熱源側熱交換器(3,4)は、第１分岐
管(10a)に設けられた第１熱交換器(3)と、第２分岐管(1
0b)に設けられた第２熱交換器(4)とを備え、該第１熱交
換器(3)と第２熱交換器(4)とは、各々個別の空気通路に
配設されていて、各空気通路には、第１熱交換器(3)に
対向して第１ファン(F1)が、第２熱交換器(4)に対向し
て第２ファン(F2)が夫々設けられている。上記膨張機構
(5,6)は、第１分岐管(10a)に設けられた第１膨張機構
(5)と、第２分岐管(10b)に設けられた第２膨張機構(6)
とを備えている。 A part of the refrigerant pipe (10) is branched.
Parallel first and second branch pipes (10a, 10b)
Have been killed. The heat source side heat exchangers (3, 4) are in the first branch
The first heat exchanger (3) provided in the pipe (10a) and the second branch pipe (1
0b) and a second heat exchanger (4) provided in the first heat exchanger.
Heat exchanger (3) and the second heat exchanger (4)
Each air passage is connected to the first heat exchanger (3).
The first fan (F1) faces the second heat exchanger (4)
And second fans (F2) are provided respectively. The above expansion mechanism
(5, 6) is a first expansion mechanism provided in the first branch pipe (10a).
(5) and a second expansion mechanism (6) provided in the second branch pipe (10b).
And
【００１９】加えて、上記圧縮機(1)の吐出圧力の過上
昇時に吐出冷媒の一部を導いて該冷媒を凝縮する熱源側
補助熱交換器(21)が、上流側を圧縮機(1)の吐出側に、
下流側をアキュムレータ(8)の上流側に夫々接続して設
けられると共に、熱源側補助熱交換器(21)は、第２熱交
換器(4)と共通の空気通路に設けられ、圧縮機(1)の吐 出
圧力の過上昇時、第２ファン(F2)の送風量を第１ファン
(F1)の送風量よりも大きく設定する。 In addition, the discharge pressure of the compressor (1) becomes excessive.
Heat source side that guides a part of the discharged refrigerant during ascent and condenses the refrigerant
Auxiliary heat exchanger (21), the upstream side to the discharge side of the compressor (1),
Connect the downstream side to the upstream side of the accumulator (8)
And the heat source side auxiliary heat exchanger (21)
Exchanger (4) is provided in the common air passage, out-discharge of the compressor (1)
When the pressure rises excessively, the air flow of the second fan (F2) is
Set it to be larger than the airflow of (F1).
【００２０】この発明の特定事項により、補助熱交換器
(21)の上流側と下流側との差圧をいっそう大きく確保で
き、補助熱交換器(21)を小型化しても十分な凝縮能力が
得られ吐出圧力の上昇が抑制できる。 According to the specific features of the present invention, an auxiliary heat exchanger
(21) More secure differential pressure between upstream and downstream
Sufficient condensing capacity even if the auxiliary heat exchanger (21) is downsized.
The resulting increase in discharge pressure can be suppressed.
【００２１】更に、第１熱交換器(3)では通過空気量が
少ないことにより蒸発能力が低減する。つまり、回路全
体としての蒸発能力は低く抑えられる。一方、補助熱交
換器(21)では、第２ファン(F2)により通過空気量が大き
く確保されて凝縮能力が増大している。つまり、回路全
体としての凝縮能力は高くなっている。このため、吐出
圧力の上昇が確実に抑制される。 Further, the amount of passing air in the first heat exchanger (3) is
The smaller the amount, the lower the evaporation ability. In other words, the entire circuit
Evaporation ability as a body is kept low. Meanwhile, auxiliary heat exchange
In the heat exchanger (21), the amount of passing air is large due to the second fan (F2).
And the condensing capacity is increasing. In other words, the entire circuit
The ability to condense as a body is increasing. Therefore, the discharge
An increase in pressure is reliably suppressed.
【００２２】請求項３記載の発明は、補助熱交換器(21)
の凝縮能力を増大させるだけでなく、熱源側熱交換器
(3,4)の能力調整によっても吐出圧力の上昇を抑制する
ようにした。According to a third aspect of the present invention, there is provided an auxiliary heat exchanger (21).
Not only increase the condensation capacity of the heat source, but also the heat source side heat exchanger
The increase in the discharge pressure was also suppressed by adjusting the capacity of (3, 4).
【００２３】つまり、請求項３記載の発明は、請求項１
記載の発明において、第１膨張機構(5)及び第２膨張機
構(6)を第１膨張弁(5)及び第２膨張弁(6)より成し、圧
縮機(1)の吐出圧力の過上昇時、第１膨張弁(5)を所定開
度に調整し、且つ第２膨張弁(6)を閉鎖する。 That is, the third aspect of the present invention is the first aspect of the present invention.
In the described invention, the first expansion mechanism (5) and the second expansion machine
The structure (6) is composed of a first expansion valve (5) and a second expansion valve (6), and when the discharge pressure of the compressor (1) rises excessively, the first expansion valve (5) is adjusted to a predetermined opening. And the second expansion valve (6) is closed .
【００２４】この発明の特定事項により、第１熱交換器
(3)では通過空気量が少ないことにより蒸発能力が低減
し、第２熱交換器(4)では第２膨張弁(6)の閉鎖による冷
媒流通の阻止により、たとえ第２ファン(F2)が駆動され
ていても蒸発能力が発揮されなくなる。つまり、回路全
体としての蒸発能力は低く抑えられる。一方、補助熱交
換器(21)では、第２ファン(F2)により通過空気量が大き
く確保されて凝縮能力が増大している。つまり、回路全
体としての凝縮能力は高くなっている。このため、吐出
圧力の上昇が確実に抑制される。 According to the specific features of the present invention, the first heat exchanger
In (3), the evaporation capacity is reduced due to the small amount of passing air, and in the second heat exchanger (4), the refrigerant is blocked by closing the second expansion valve (6). Evaporation ability is not exhibited even when driven. That is, the evaporation ability of the entire circuit can be kept low. On the other hand, in the auxiliary heat exchanger (21), a large amount of air passes through the second fan (F2), and condensing capacity is increased. That is, the condensation capability of the entire circuit is high. For this reason, an increase in the discharge pressure is reliably suppressed .
【００２５】[0025]
【発明の実施の形態】（第１実施形態） 次に、本発明の第１実施形態を図面を用いて説明する。(First Embodiment) Next, a first embodiment of the present invention will be described with reference to the drawings.
【００２６】図１は本実施形態に係る空気調和機の室外
ユニット(A)及び室内ユニット(B)の冷媒配管系統を示し
ている。以下、各ユニット(A),(B)について説明する。FIG. 1 shows a refrigerant piping system of the outdoor unit (A) and the indoor unit (B) of the air conditioner according to the present embodiment. Hereinafter, each unit (A) and (B) will be described.
【００２７】室外ユニット(A)の内部には、インバータ
により運転容量が可変とされた圧縮機(1)と、暖房運転
時には図中実線の如く切換わり冷房運転時には図中破線
の如く切換わる四路切換弁(2)と、冷房運転時に凝縮
器、暖房運転時に蒸発器となる熱源側熱交換器としての
室外熱交換器(3,4)及び該室外熱交換器(3,4)に付設され
た室外ファン(F1,F2)と、暖房運転時に冷媒の絞り作用
を行う室外電動膨張弁(5,6)と、液化した冷媒を貯蔵す
るレシーバ(7)と、アキュムレータ(8)とが主要機器とし
て内蔵されている。そして、これら各機器(1)〜(8)が冷
媒配管(10)により冷媒の流通が可能に接続されている。Inside the outdoor unit (A), a compressor (1) whose operating capacity is made variable by an inverter and four compressors which are switched as shown by the solid line in the heating operation and which are switched as shown by the broken line in the cooling operation during the heating operation. A path switching valve (2), an outdoor heat exchanger (3, 4) as a heat source side heat exchanger that serves as a condenser during cooling operation and an evaporator during heating operation, and is attached to the outdoor heat exchanger (3, 4). The outdoor fans (F1, F2), the outdoor electric expansion valves (5, 6) that throttle the refrigerant during the heating operation, the receiver (7) that stores the liquefied refrigerant, and the accumulator (8). Built-in as a device. These devices (1) to (8) are connected by a refrigerant pipe (10) so that a refrigerant can flow.
【００２８】上記室外熱交換器(3,4)は、第１室外熱交
換器(3)及び第２室外熱交換器(4)から成り、室外電動膨
張弁(5,6)も第１膨張弁と(5)及び第２膨張弁(6)から成
る。この室外熱交換器(3,4)及び室外電動膨張弁(5,6)の
配置状態について説明すると、冷媒配管(10)は、その一
部が第１分岐配管(10a)と第２分岐配管(10b)との２系統
に分岐されている。そして、第１分岐配管(10a)には第
１熱交換器(3)及び第１膨張弁(5)が、第２分岐配管(10
b)には第２熱交換器(4)及び第２膨張弁(6)が夫々設けら
れている。つまり、第１熱交換器(3)及び第１膨張弁(5)
と、第２熱交換器(4)及び第２膨張弁(6)とが互いに並列
に接続されている。The outdoor heat exchanger (3, 4) comprises a first outdoor heat exchanger (3) and a second outdoor heat exchanger (4), and the outdoor electric expansion valves (5, 6) also perform the first expansion. It comprises a valve (5) and a second expansion valve (6). Explaining the arrangement of the outdoor heat exchangers (3, 4) and the outdoor electric expansion valves (5, 6), a part of the refrigerant pipe (10) is a first branch pipe (10a) and a second branch pipe. (10b). The first heat exchanger (3) and the first expansion valve (5) are connected to the first branch pipe (10a).
b) is provided with a second heat exchanger (4) and a second expansion valve (6), respectively. That is, the first heat exchanger (3) and the first expansion valve (5)
And the second heat exchanger (4) and the second expansion valve (6) are connected in parallel with each other.
【００２９】また、第１室外熱交換器(3)と第２室外熱
交換器(4)とは各々個別の空気通路に設置されている。
そして、室外ファン(F1,F2)は、第１室外熱交換器(3)の
空気通路に設置された第１室外ファン(F1)と、第２室外
熱交換器(4)の空気通路に設置された第２室外ファン(F
2)とから成る。つまり、第１室外ファン(F1)が駆動した
場合には第１室外熱交換器(3)の空気通路に外気が流
れ、第２室外ファン(F2)が駆動した場合には第２室外熱
交換器(4)の空気通路に外気が流れる構成である。Further, the first outdoor heat exchanger (3) and the second outdoor heat exchanger (4) are respectively installed in individual air passages.
The outdoor fans (F1, F2) are installed in the air passage of the first outdoor heat exchanger (3) and the air passage of the second outdoor heat exchanger (4). 2nd outdoor fan (F
2). That is, when the first outdoor fan (F1) is driven, outside air flows into the air passage of the first outdoor heat exchanger (3), and when the second outdoor fan (F2) is driven, the second outdoor heat exchanger is driven. The outside air flows through the air passage of the vessel (4).
【００３０】一方、室内ユニット(B)は、冷房運転時に
は蒸発器、暖房運転時には凝縮器となる利用側熱交換器
としての室内熱交換器(12)および室内ファン(F3)を備え
ている。また、室内熱交換器(12)の液管側には、暖房運
転時に冷媒流量を調節し、冷房運転時に冷媒の絞り作用
を行う室内電動膨張弁(13)が介設されている。On the other hand, the indoor unit (B) includes an indoor heat exchanger (12) as a use side heat exchanger serving as an evaporator during a cooling operation and a condenser during a heating operation, and an indoor fan (F3). On the liquid pipe side of the indoor heat exchanger (12), an indoor electric expansion valve (13) that adjusts the flow rate of the refrigerant during the heating operation and performs the throttling action of the refrigerant during the cooling operation is provided.
【００３１】このようにして、以上の各機器が冷媒配管
(10)により、冷媒の流通可能に接続されていて、各熱交
換器(3,4,12)での熱交換動作により、外気と室内空気と
の間で熱搬送を行う主冷媒回路(C)が構成されている。As described above, each of the above devices is connected to the refrigerant pipe.
According to (10), the main refrigerant circuit (C) is connected so that the refrigerant can flow, and performs heat transfer between the outside air and the indoor air by the heat exchange operation in each heat exchanger (3, 4, 12). ) Is configured.
【００３２】そして、本形態の特徴として、主冷媒回路
(C)には補助ライン(20)が接続されている。この補助ラ
イン(20)には、第２室外熱交換器(4)と共通の空気通路
に設置された補助熱交換器(21)、電磁開閉弁(SV)及びキ
ャピラリチューブ(CP)が順次直列に接続されている。そ
して、この補助ライン(20)は、一端が圧縮機(1)の吐出
側と四路切換弁(2)との間に、また他端が第１室外熱交
換器(3)と第１膨張弁(5)との間に夫々接続されている。
そして、冷房運転時には常時、暖房運転時には高圧の過
上昇時に、上記電磁開閉弁(SV)がオンつまり開状態にな
って、吐出ガスの一部を主冷媒回路(C)から補助ライン
(20)にバイパスするようになっている。そして、このと
き、補助ライン(20)にバイパスした吐出ガスが補助熱交
換器(21)で凝縮されるようになっている。As a feature of this embodiment, the main refrigerant circuit
An auxiliary line (20) is connected to (C). In this auxiliary line (20), an auxiliary heat exchanger (21), a solenoid on-off valve (SV) and a capillary tube (CP) are installed in series in the air passage common to the second outdoor heat exchanger (4). It is connected to the. The auxiliary line (20) has one end between the discharge side of the compressor (1) and the four-way switching valve (2), and the other end with the first outdoor heat exchanger (3) and the first expansion valve. Each is connected to the valve (5).
The solenoid on-off valve (SV) is turned on or opened at all times during the cooling operation and at the time of high pressure overheating during the heating operation, and a part of the discharged gas is transferred from the main refrigerant circuit (C) to the auxiliary line.
Bypass to (20). At this time, the discharge gas bypassed to the auxiliary line (20) is condensed in the auxiliary heat exchanger (21).
【００３３】また、本装置の各所にはセンサ類が配置さ
れている。圧縮機(1)の吐出側には主冷媒回路(C)の高圧
側圧力を検出するための高圧センサ(P1)が設けられてい
る。その他、室内温度、外気温度、室内熱交換器(12)の
液側およびガス側の冷媒温度、圧縮機(1)の吐出管温
度、圧縮機(1)吸入側圧力等を検出する種々のセンサ
（図示省略）が設けられている。Sensors are arranged at various points in the apparatus. On the discharge side of the compressor (1), a high-pressure sensor (P1) for detecting the high-pressure side pressure of the main refrigerant circuit (C) is provided. In addition, various sensors for detecting the indoor temperature, the outside air temperature, the refrigerant temperature on the liquid side and the gas side of the indoor heat exchanger (12), the discharge pipe temperature of the compressor (1), the pressure on the suction side of the compressor (1), and the like. (Not shown) is provided.
【００３４】そして、上記各センサの信号はコントロー
ルユニット(15)に送信され、該コントロールユニット(1
5)が各膨張弁(5,6)及び電磁開閉弁(SV)の開閉制御、圧
縮機(1)の容量制御、各ファン(F1,F2,F3)の回転数制御
等を行うようになっている。Then, the signal of each sensor is transmitted to the control unit (15), and the control unit (1)
5) controls the opening and closing of each expansion valve (5, 6) and solenoid on-off valve (SV), controls the capacity of the compressor (1), and controls the rotation speed of each fan (F1, F2, F3). ing.
【００３５】次に、上述の如く構成された空気調和装置
の運転動作について説明する。Next, the operation of the air conditioner constructed as described above will be described.
【００３６】先ず、空気調和装置の冷房運転時について
説明する。この運転時には、四路切換弁(2)が図１中破
線側に切換わり、補助ライン(20)の電磁開閉弁(SV)が常
時開いて、圧縮機(1)で圧縮された冷媒が、各室外熱交
換器(3,4)及び補助熱交換器(20)に導入され、外気との
間で熱交換を行って凝縮する。その後、この凝縮冷媒
は、レシーバ(7)を経て室内ユニット(B)に導入する。こ
の室内ユニット(B)では、液冷媒が、室内電動膨張弁(1
3)で減圧され、室内熱交換器(12)で室内空気との間で熱
交換を行って蒸発する。その後、この冷媒は、室外ユニ
ット(A)にガス状態で戻り、圧縮機(1)に吸入される。こ
のような冷媒循環動作を繰り返すことで、室内空気を冷
却する。First, the cooling operation of the air conditioner will be described. During this operation, the four-way switching valve (2) is switched to the broken line side in FIG. 1, the solenoid on-off valve (SV) of the auxiliary line (20) is always open, and the refrigerant compressed by the compressor (1) The heat is introduced into each of the outdoor heat exchangers (3, 4) and the auxiliary heat exchanger (20), and exchanges heat with the outside air to condense. Thereafter, the condensed refrigerant is introduced into the indoor unit (B) via the receiver (7). In this indoor unit (B), the liquid refrigerant is supplied to the indoor electric expansion valve (1).
The pressure is reduced in 3), and heat is exchanged with indoor air in the indoor heat exchanger (12) to evaporate. Thereafter, the refrigerant returns to the outdoor unit (A) in a gaseous state, and is sucked into the compressor (1). By repeating such a refrigerant circulation operation, the room air is cooled.
【００３７】一方、暖房運転時には、四路切換弁(2)が
図１中実線側に切換わり、冷媒の流れは上記冷房運転時
と逆となる。つまり、圧縮機(1)で圧縮された冷媒が、
室内熱交換器(12)で室内空気との間で熱交換を行って凝
縮した後、液状態で室外ユニット(A)に導入する。そし
て、この冷媒は、各室外電動膨張弁(5,6)により減圧さ
れ、各室外熱交換器(3,4)で蒸発した後、圧縮機(1)に戻
るように循環する。これにより、室内空気を加熱するこ
とになる。そして、高圧センサ(P1)により検出する主冷
媒回路(C)の高圧側圧力が所定値以下である場合には、
補助ライン(20)の電磁開閉弁(SV)が閉鎖されており、ま
た、各膨張弁(5,6)が各室外熱交換器(3,4)の出口側の過
熱度を一定にするように開度調整される。また、各室外
ファン(F1,F2)は共に高い回転数（Ｈタップ）で駆動し
ている。On the other hand, during the heating operation, the four-way switching valve (2) is switched to the solid line side in FIG. 1, and the flow of the refrigerant is opposite to that during the cooling operation. That is, the refrigerant compressed by the compressor (1)
After condensing by performing heat exchange with indoor air in the indoor heat exchanger (12), the liquid is introduced into the outdoor unit (A) in a liquid state. The refrigerant is decompressed by the outdoor electric expansion valves (5, 6), evaporated in the outdoor heat exchangers (3, 4), and circulated back to the compressor (1). As a result, the room air is heated. When the high-pressure side pressure of the main refrigerant circuit (C) detected by the high-pressure sensor (P1) is equal to or less than a predetermined value,
The solenoid on-off valve (SV) of the auxiliary line (20) is closed, and each expansion valve (5, 6) keeps the degree of superheat at the outlet side of each outdoor heat exchanger (3, 4) constant. The opening is adjusted. Further, each of the outdoor fans (F1, F2) is driven at a high rotation speed (H tap).
【００３８】そして、本例の特徴としては、上記高圧側
圧力が上昇して所定値に達した際に、この高圧側圧力の
上昇を阻止するための動作にある。以下、この動作につ
いて説明する。本形態では、この高圧上昇の阻止動作と
して３段階の動作がある。そして、高圧側圧力の上昇が
回避されるまで、第１段階動作から第３段階動作へ順に
動作が移行していく。以下、各段階の動作について説明
する。The feature of the present embodiment lies in an operation for preventing the rise of the high pressure side pressure when the high pressure side pressure rises and reaches a predetermined value. Hereinafter, this operation will be described. In the present embodiment, there are three stages of the operation for preventing the high pressure from rising. Then, the operation sequentially shifts from the first stage operation to the third stage operation until the increase in the high pressure side pressure is avoided. Hereinafter, the operation of each stage will be described.
【００３９】−第１段階動作− 上述したような通常の暖房運転状態において、高圧側圧
力が所定値を越えた場合には、先ず、第１段階動作に移
る。この動作では、第２分岐管(10b)の第２膨張弁(6)を
閉鎖する。これにより、第２分岐管(10b)には冷媒が流
れなくなる。つまり、室内熱交換器(12)で凝縮した冷媒
は、第１膨張弁(5)のみによって減圧され、第１室外熱
交換器(3)のみによって蒸発する。従って、室外熱交換
器(3,4)全体としての蒸発能力が低減することになり、
これによって高圧側圧力の上昇を抑制する。-First Stage Operation- When the high pressure side pressure exceeds a predetermined value in the normal heating operation state as described above, first, the operation proceeds to the first stage operation. In this operation, the second expansion valve (6) of the second branch pipe (10b) is closed. As a result, the refrigerant stops flowing through the second branch pipe (10b). That is, the refrigerant condensed in the indoor heat exchanger (12) is decompressed only by the first expansion valve (5) and evaporates only by the first outdoor heat exchanger (3). Therefore, the evaporation capacity of the outdoor heat exchanger (3, 4) as a whole is reduced,
This suppresses an increase in the high pressure side pressure.
【００４０】−第２段階動作− 上述した第１段階動作を行っても未だ高圧側圧力が低下
しない場合には、第２段階動作に移る。この動作では、
上記第１段階動作に加えて、第１室外ファン(F1)の回転
数を低下（Ｌタップ）させる。これにより、第１室外熱
交換器(3)を通過する外気の流量が低減され、これによ
って該第１室外熱交換器(3)の蒸発能力が低下する。従
って、室外熱交換器(3,4)全体としての蒸発能力を更に
低減することで高圧側圧力の上昇を抑制する。-Second Stage Operation- If the high pressure side pressure still does not decrease even after performing the first stage operation described above, the operation shifts to the second stage operation. In this behavior,
In addition to the first stage operation, the rotation speed of the first outdoor fan (F1) is reduced (L tap). As a result, the flow rate of the outside air passing through the first outdoor heat exchanger (3) is reduced, thereby reducing the evaporation ability of the first outdoor heat exchanger (3). Therefore, an increase in the high-pressure side pressure is suppressed by further reducing the evaporation capacity of the outdoor heat exchangers (3, 4) as a whole.
【００４１】−第３段階動作− 更に、上述した第２段階動作を行っても未だ高圧側圧力
が低下しない場合には、本形態の特徴とする動作である
第３段階動作に移る。この動作では、上記第１及び第２
段階の動作に加えて、補助ライン(20)の電磁開閉弁(SV)
を開放する。つまり、圧縮機(1)からの吐出冷媒の一部
を補助ライン(20)に逃がす。そして、この補助ライン(2
0)に導入したガス冷媒は、補助熱交換器(21)において外
気との間で熱交換を行って凝縮する。この凝縮冷媒は、
キャピラリチューブ(CP)で減圧された後、第１分岐管(1
0a)に導入し、主冷媒回路(C)を循環する冷媒と合流す
る。そして、この合流した冷媒は、第１室外熱交換器
(3)で蒸発した後、圧縮機(1)に戻る。このような冷媒循
環動作により、回路全体としての凝縮能力が増大し、こ
れによって高圧側圧力の上昇が抑制されることになる。-Third-Stage Operation- Further, if the high-pressure side pressure still does not decrease even after performing the above-described second-stage operation, the operation proceeds to the third-stage operation, which is an operation characteristic of the present embodiment. In this operation, the first and second
In addition to the step operation, the solenoid valve (SV) of the auxiliary line (20)
To release. That is, a part of the refrigerant discharged from the compressor (1) is released to the auxiliary line (20). And this auxiliary line (2
The gas refrigerant introduced in 0) exchanges heat with the outside air in the auxiliary heat exchanger (21) and condenses. This condensed refrigerant
After the pressure is reduced by the capillary tube (CP), the first branch pipe (1
0a) and merges with the refrigerant circulating in the main refrigerant circuit (C). The combined refrigerant is supplied to the first outdoor heat exchanger.
After evaporating in (3), return to the compressor (1). By such a refrigerant circulation operation, the condensing capacity of the entire circuit increases, thereby suppressing an increase in the high-pressure side pressure.
【００４２】そして、上述したように、本回路では、補
助熱交換器(21)で凝縮した冷媒の第１分岐管(10a)への
導入部分は、第１膨張弁(5)と第１室外熱交換器(3)との
間、つまり、第１膨張弁(5)の下流側の低圧部分となっ
ている。従って、補助ライン(20)の上流端と下流端との
差圧が十分に確保され、冷媒流量が十分に確保される。As described above, in this circuit, the part of the refrigerant condensed in the auxiliary heat exchanger (21) to the first branch pipe (10a) is connected to the first expansion valve (5) and the first outdoor unit. The low pressure portion is between the heat exchanger (3), that is, the downstream side of the first expansion valve (5). Therefore, the differential pressure between the upstream end and the downstream end of the auxiliary line (20) is sufficiently ensured, and the flow rate of the refrigerant is sufficiently ensured.
【００４３】つまり、この第３段階動作では、第２膨張
弁(6)を閉鎖することで、第２室外熱交換器(4)が能力を
発揮しないようにし、また、第１室外ファン(F1)の回転
数を低下させることで、第１室外熱交換器(3)の能力を
低減させ、これらによって室外熱交換器(3,4)の全体と
しての蒸発能力を大幅に低下させている。そして、それ
ばかりでなく、下流端が第１膨張弁(5)の下流側である
低圧部分に接続された補助ライン(20)を開放すること
で、その上流端と下流端との差圧を十分に確保して冷媒
流量を増大させ、且つ第２ファン(F2)の回転数を高く維
持することにより、補助熱交換器(21)の凝縮能力が大き
く得られるようにしている。これにより、高圧側圧力を
確実に低下させることができる。That is, in the third stage operation, the second outdoor heat exchanger (4) is prevented from exerting its capacity by closing the second expansion valve (6), and the first outdoor fan (F1 ), The capacity of the first outdoor heat exchanger (3) is reduced, thereby greatly reducing the evaporation capacity of the outdoor heat exchangers (3, 4) as a whole. In addition, by opening the auxiliary line (20), the downstream end of which is connected to the low pressure portion downstream of the first expansion valve (5), the differential pressure between the upstream end and the downstream end is reduced. By sufficiently securing the refrigerant flow rate and keeping the rotation speed of the second fan (F2) high, the condensing capacity of the auxiliary heat exchanger (21) can be largely obtained. Thereby, the high pressure side pressure can be reliably reduced.
【００４４】このように、本形態によれば、補助ライン
(20)の下流端の接続位置を改良し、また、各熱交換器
(3,4,21)の設置位置や夫々のファン(F1,F2)の駆動状態
を調整して、凝縮能力の拡大と蒸発能力の縮小とを両立
させて高圧側圧力を確実に低下させるようにしている。
このため、従来のように、補助熱交換器の大型化を招く
ことなしに、高圧側圧力の上昇抑制を確実に行うことが
でき、装置の実用性の向上を図ることができる。As described above, according to the present embodiment, the auxiliary line
The connection position at the downstream end of (20) has been improved, and each heat exchanger
Adjust the installation position of (3,4,21) and the driving condition of each fan (F1, F2) to ensure that the high pressure side pressure is reduced by increasing the condensation capacity and reducing the evaporation capacity at the same time. I have to.
For this reason, the increase in the high-pressure side pressure can be surely suppressed without increasing the size of the auxiliary heat exchanger as in the related art, and the practicality of the device can be improved.
【００４５】また、サーモオフ時などにおいて、圧縮機
(1)が停止している場合には、第１膨張弁(5)のみを閉鎖
すれば、高圧液ラインの液冷媒が、補助ライン(20)を逆
流して圧縮機(1)に導入するといったことが回避され
る。このため、従来のように、電磁開閉弁(SV)を閉鎖す
ることで液冷媒の逆流を防止する必要がなくなる。従っ
て、この電磁開閉弁(SV)としては、冷媒の一方向（補助
熱交換器(21)から第１室外熱交換器(3)へ向って流れる
方向）の流通のみを許容或いは規制するものを採用すれ
ばよく、双方向の冷媒の流通に対してその規制が行える
ものを採用しておく必要はなくなり、コストの低減を図
ることができる。また、補助ライン(20)での冷媒の逆流
を防止するために、レシーバにガス抜きのための回路を
接続したり、補助ラインに逆止弁を設けたりする必要も
なくなる。このため、回路構成の複雑化や、部品点数の
増加を招くことなしに、冷媒の逆流防止による圧縮機
(1)の信頼性が確保される。Also, when the thermostat is turned off, for example,
When (1) is stopped, if only the first expansion valve (5) is closed, the liquid refrigerant in the high pressure liquid line flows back through the auxiliary line (20) and is introduced into the compressor (1). This is avoided. Therefore, unlike the related art, there is no need to prevent the liquid refrigerant from flowing backward by closing the solenoid on-off valve (SV). Therefore, as the solenoid on-off valve (SV), one that permits or regulates only the flow in one direction of the refrigerant (the direction flowing from the auxiliary heat exchanger (21) to the first outdoor heat exchanger (3)). It suffices to employ a coolant that can regulate the flow of the two-way refrigerant, so that the cost can be reduced. Further, in order to prevent the backflow of the refrigerant in the auxiliary line (20), there is no need to connect a circuit for degassing to the receiver or to provide a check valve in the auxiliary line. For this reason, the compressor is prevented by preventing the refrigerant from flowing backward without complicating the circuit configuration and increasing the number of parts.
The reliability of (1) is secured.
【００４６】（第２実施形態） 次に、本発明の第２実施形態を図面を用いて説明する。Second Embodiment Next, a second embodiment of the present invention will be described with reference to the drawings.
【００４７】本形態は、補助ライン(20)の接続状態を改
良したものであって、その他の構成及び制御動作は上述
した第１実施形態のものと同様である。従って、ここで
は、第１実施形態との相違点についてのみ説明する。In the present embodiment, the connection state of the auxiliary line (20) is improved, and other configurations and control operations are the same as those of the first embodiment. Therefore, here, only the differences from the first embodiment will be described.
【００４８】図２（この図２は室外ユニット(A)のみの
回路構成である）に示すように、本形態に係る補助ライ
ン(20)は、一端が圧縮機(1)の吐出側に、他端がアキュ
ムレータ(8)の上流側に接続されている。つまり、本形
態にあっても補助ライン(20)の下流端は、主冷媒回路
(C)の低圧部分に接続されている。As shown in FIG. 2 (FIG. 2 shows a circuit configuration of only the outdoor unit (A)), the auxiliary line (20) according to this embodiment has one end on the discharge side of the compressor (1). The other end is connected to the upstream side of the accumulator (8). That is, even in this embodiment, the downstream end of the auxiliary line (20) is connected to the main refrigerant circuit.
It is connected to the low pressure part of (C).
【００４９】このため、上述した第１実施形態の第３段
階動作と同様に、この補助ライン(20)の電磁開閉弁(SV)
を開放した場合には、補助ライン(20)の上流端と下流端
との差圧を十分に確保できて冷媒流量が増大し、高圧側
圧力を確実に低下させることができる。Therefore, similarly to the third stage operation of the first embodiment, the solenoid on-off valve (SV) of the auxiliary line (20) is used.
Is opened, the differential pressure between the upstream end and the downstream end of the auxiliary line (20) can be sufficiently ensured, the flow rate of the refrigerant increases, and the high-pressure side pressure can be reliably reduced.
【００５０】そして、本第２実施形態と上述した第１実
施形態とを比較した場合、第１実施形態は液冷媒を高圧
液ラインに溜めるのに対し、第１実施形態はアキュムレ
ータ(8)に溜めるようになっている。また、第２実施形
態では、アキュムレータ(8)の上流側に液冷媒が戻るの
で、圧縮機(1)の吸入冷媒が湿る可能性がある。この点
では第１実施形態の回路構成の方が好ましい。また、本
第２実施形態のものでは、補助ライン(20)の上流端と下
流端との差圧を、第１実施形態のものよりも大きく確保
できるので、補助熱交換器(21)を小型化することができ
る。更に、この第２実施形態では、圧縮機(1)の吸入側
でガス欠が発生し易い低外気冷房運転時にあっても、こ
の吸入側のガス量を確保でき低圧保護を図ることができ
るという利点がある。When the second embodiment is compared with the first embodiment described above, the first embodiment stores the liquid refrigerant in the high-pressure liquid line, whereas the first embodiment stores the liquid refrigerant in the accumulator (8). It is designed to store. Further, in the second embodiment, since the liquid refrigerant returns to the upstream side of the accumulator (8), there is a possibility that the refrigerant sucked into the compressor (1) becomes wet. In this regard, the circuit configuration of the first embodiment is more preferable. Further, in the second embodiment, the differential pressure between the upstream end and the downstream end of the auxiliary line (20) can be secured larger than that in the first embodiment, so that the auxiliary heat exchanger (21) can be reduced in size. Can be Furthermore, in the second embodiment, even during a low outside air cooling operation in which gas shortage is likely to occur on the suction side of the compressor (1), the gas amount on the suction side can be secured and low pressure protection can be achieved. There are advantages.
【００５１】尚、本発明は、空調機として、複数の室内
ユニットを備えたマルチ型の空調機に採用したり、冷媒
回路として、室外ユニットに２個の圧縮機を配設した差
圧強制方式の圧縮機を備えた冷媒回路に採用することも
できる。The present invention is applied to a multi-type air conditioner having a plurality of indoor units as an air conditioner, or a differential pressure forced system in which two compressors are provided in an outdoor unit as a refrigerant circuit. Can be employed in a refrigerant circuit provided with the compressor of (1).
【００５２】[0052]
【発明の効果】以上説明してきたように、本発明によれ
ば以下に述べるような効果が発揮される。請求項１記載
の発明では、圧縮機の吐出圧力の過上昇時に吐出冷媒の
一部が導入されて該冷媒を凝縮する補助熱交換器を備え
た冷凍装置に対し、補助熱交換器の上流側を圧縮機の吐
出側に、下流側を膨張機構よりも下流側に夫々接続し
た。このため、補助熱交換器の上流側と下流側との差圧
を大きく確保することができ、補助熱交換器における冷
媒流量を十分に確保することができる。つまり、補助熱
交換器を大型化することなしに該補助熱交換器の凝縮能
力を十分に得ることができ、吐出圧力の上昇が確実に抑
制できて、装置の信頼性の向上が図れる。また、圧縮機
の停止時には、膨張機構の冷媒流通を規制するのみで高
圧液ラインの液冷媒が補助熱交換器を逆流して圧縮機に
導入するといったことが回避される。このため、従来の
ように、この逆流を防止するための特別な手段が不要に
なり、冷媒の逆流防止による圧縮機の信頼性の確保を容
易に実現できる。As described above, according to the present invention, the following effects are exhibited. According to the first aspect of the present invention, when the discharge pressure of the compressor is excessively increased, a part of the discharged refrigerant is introduced and the refrigeration apparatus including the auxiliary heat exchanger for condensing the refrigerant is provided on the upstream side of the auxiliary heat exchanger. Was connected to the discharge side of the compressor, and the downstream side was connected to the downstream side of the expansion mechanism. For this reason, a large differential pressure between the upstream side and the downstream side of the auxiliary heat exchanger can be ensured, and the refrigerant flow rate in the auxiliary heat exchanger can be sufficiently ensured. That is, it is possible to sufficiently obtain the condensing capacity of the auxiliary heat exchanger without increasing the size of the auxiliary heat exchanger, and it is possible to reliably suppress the rise in the discharge pressure and improve the reliability of the apparatus. Further, when the compressor is stopped, it is possible to prevent the liquid refrigerant in the high-pressure liquid line from flowing back through the auxiliary heat exchanger and being introduced into the compressor only by restricting the refrigerant flow in the expansion mechanism. This eliminates the need for a special means for preventing the backflow as in the related art, and can easily realize the reliability of the compressor by preventing the backflow of the refrigerant.
【００５３】更に、第１熱交換器の通過空気量を少なく
してその蒸発能力を低減させ、補助熱交換器では、通過
空気量が大きく確保して凝縮能力を増大させている。こ
れにより、回路全体としての蒸発能力の低減と凝縮能力
の向上とを両立でき、吐出圧力の上昇を確実に抑制でき
る。 Further, the amount of air passing through the first heat exchanger is reduced.
To reduce its evaporation capacity and pass through the auxiliary heat exchanger
A large air volume is secured to increase the condensation capacity. This
This reduces the evaporation capacity and condensing capacity of the entire circuit.
And increase of discharge pressure can be suppressed reliably.
You.
【００５４】請求項２記載の発明では、補助熱交換器の
下流端をアキュムレータの上流側に接続している。これ
により、補助熱交換器の上流側と下流側との差圧をいっ
そう大きく確保でき、吐出圧力の上昇を抑制と、補助熱
交換器の小型化とを両立できる。 According to the second aspect of the present invention, the auxiliary heat exchanger
The downstream end is connected to the upstream side of the accumulator. this
Pressure difference between the upstream and downstream sides of the auxiliary heat exchanger
It is possible to secure so large that the rise of the discharge pressure is suppressed and the auxiliary heat
It is possible to achieve both downsizing of the exchanger.
【００５５】更に、第１熱交換器の通過空気量を少なく
してその蒸発能力を低減させ、補助熱交換器では、通過
空気量が大きく確保して凝縮能力を増大させている。こ
れにより、回路全体としての蒸発能力の低減と凝縮能力
の向上とを両立でき、吐出圧力の上昇を確実に抑制でき
る。 Further, the amount of air passing through the first heat exchanger is reduced.
To reduce its evaporation capacity and pass through the auxiliary heat exchanger
A large air volume is secured to increase the condensation capacity. This
This reduces the evaporation capacity and condensing capacity of the entire circuit.
And increase of discharge pressure can be suppressed reliably.
You.
【００５６】請求項３記載の発明では、第１熱交換器の
通過空気量を少なくしてその蒸発能力を低減させ、第２
熱交換器の冷媒流通を阻止して蒸発能力が発揮されない
ようにし、補助熱交換器では、通過空気量が大きく確保
して凝縮能力を増大させている。これにより、回路全体
としての蒸発能力の低減と凝縮能力の向上とを両立で
き、吐出圧力の上昇を確実に抑制できる。 According to the third aspect of the present invention, the amount of air passing through the first heat exchanger is reduced to reduce its evaporation ability,
The refrigerant flow in the heat exchanger is prevented so that the evaporation ability is not exhibited, and the auxiliary heat exchanger secures a large amount of passing air to increase the condensation ability. This allows both an improvement in reducing the condensation capacity of the evaporating ability of the entire circuit, cut with reliably suppress the increase of the discharge pressure.
【図１】第１実施形態における冷媒配管系統を示す図で
ある。FIG. 1 is a diagram showing a refrigerant piping system according to a first embodiment.
【図２】第２実施形態における冷媒配管系統を示す図で
ある。FIG. 2 is a diagram illustrating a refrigerant piping system according to a second embodiment.
(1) 圧縮機 (3) 第１室外熱交換器（熱源側熱交換器） (4) 第２室外熱交換器（熱源側熱交換器） (5) 第１膨張弁（膨張機構） (6) 第２膨張弁（膨張機構） (8) アキュムレータ (10) 冷媒配管 (10a) 第１分岐管 (10b) 第２分岐管 (12) 室内熱交換器（利用側熱交換器） (C) 主冷媒回路 (F1) 第１室外ファン (F2) 第２室外ファン (21) 補助熱交換器 (1) Compressor (3) First outdoor heat exchanger (heat source side heat exchanger) (4) Second outdoor heat exchanger (heat source side heat exchanger) (5) First expansion valve (expansion mechanism) (6) ) Second expansion valve (expansion mechanism) (8) Accumulator (10) Refrigerant piping (10a) First branch pipe (10b) Second branch pipe (12) Indoor heat exchanger (use side heat exchanger) (C) Main Refrigerant circuit (F1) First outdoor fan (F2) Second outdoor fan (21) Auxiliary heat exchanger
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F25B 1/00 F25B 5/02 F25B 6/02 ──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int. Cl. 7 , DB name) F25B 1/00 F25B 5/02 F25B 6/02
Claims (3)
機構(5,6)及び熱源側熱交換器(3,4)が冷媒配管(10)によ
り接続されてなる主冷媒回路(C)を備え、圧縮機(1)から
の吐出冷媒を、利用側熱交換器(12)で凝縮し、膨張機構
(5,6)で減圧した後、熱源側熱交換器(3,4)で蒸発する冷
媒循環動作を行う冷凍装置において、上記冷媒配管(10)の一部が分岐されて成る並列な第１及
び第２の分岐配管(10a,10b)が設けられ、 上記熱源側熱交換器(3,4)は、第１分岐管(10a)に設けら
れた第１熱交換器(3)と、第２分岐管(10b)に設けられた
第２熱交換器(4)とを備え、該第１熱交換器(3)と第２熱
交換器(4)とは、各々個別の空気通路に配設されてい
て、各空気通路には、第１熱交換器(3)に対向して第１
ファン(F1)が、第２熱交換器(4)に対向して第２ファン
(F2)が夫々設けられ、 上記膨張機構(5,6)は、第１分岐管(10a)に設けられた第
１膨張機構(5)と、第２分岐管(10b)に設けられた第２膨
張機構(6)とを備える一方、 上記圧縮機(1)の吐出圧力の過上昇時に吐出冷媒の一部
を導いて該冷媒を凝縮する熱源側補助熱交換器(21)が、
上流側を圧縮機(1)の吐出側に、下流側を第１膨張機構
(5)と第１熱交換器(3)との間に夫々接続して設けられる
と共に、熱源側補助熱交換器(21)は、第２熱交換器(4)
と共通の空気通路に設けられ、 圧縮機(1)の吐出圧力の過上昇時、第２ファン(F2)の送
風量を第１ファン(F1)の送風量よりも大きく設定する こ
とを特徴とする冷凍装置。A main unit comprising a compressor (1), a use side heat exchanger (12), an expansion mechanism (5, 6), and a heat source side heat exchanger (3, 4) connected by a refrigerant pipe (10). Equipped with a refrigerant circuit (C), the refrigerant discharged from the compressor (1) is condensed in the use side heat exchanger (12), and the expansion mechanism
In the refrigerating apparatus which performs the refrigerant circulation operation of evaporating in the heat source side heat exchangers (3, 4) after the pressure is reduced in (5, 6), the first parallel refrigerant pipe in which a part of the refrigerant pipe (10) is branched is provided. Passing
And a second branch pipe (10a, 10b). The heat source side heat exchanger (3, 4) is provided in the first branch pipe (10a).
Installed in the first heat exchanger (3) and the second branch pipe (10b).
A second heat exchanger (4), wherein the first heat exchanger (3) and the second heat exchanger
The exchangers (4) are arranged in separate air passages, respectively.
Each air passage has a first heat exchanger (3) facing the first heat exchanger (3).
The fan (F1) faces the second heat exchanger (4) and the second fan
(F2) are provided respectively, and the expansion mechanism (5, 6) is provided with a first branch pipe (10a) provided in the first branch pipe (10a).
(1) an inflation mechanism (5) and a second inflation mechanism provided in the second branch pipe (10b).
While and a Zhang mechanism (6), the compressor (1) the heat source side auxiliary heat exchanger for condensing the refrigerant guides a part of the refrigerant discharged when excessive increase of the discharge pressure of (21),
The upstream side is the discharge side of the compressor (1), and the downstream side is the first expansion mechanism.
Provided in respectively connected between (5) and the first heat exchanger (3)
At the same time, the heat source side auxiliary heat exchanger (21) is connected to the second heat exchanger (4).
When the discharge pressure of the compressor (1) rises excessively, the second fan (F2)
A refrigeration apparatus characterized in that the air volume is set to be larger than the air volume of the first fan (F1) .
機構(5,6)及び熱源側熱交換器(3,4)が冷媒配管(10)によ
り接続されてなる主冷媒回路(C)を備え、該主冷媒回路
(C)は、圧縮機(1)の吸入側にアキュムレータ(8)が設け
られ、圧縮機(1)からの吐出冷媒を、利用側熱交換器(1
2)で凝縮し、膨張機構(5,6)で減圧した後、熱源側熱交
換器(3,4)で蒸発する冷媒循環動作を行う冷凍装置にお
いて、 上記冷媒配管(10)の一部が分岐されて成る並列な第１及
び第２の分岐配管(10a,10b)が設けられ、上記 熱源側熱交換器(3,4)は、第１分岐管(10a)に設けら
れた第１熱交換器(3)と、第２分岐管(10b)に設けられた
第２熱交換器(4)とを備え、該第１熱交換器(3)と第２熱
交換器(4)とは、各々個別の空気通路に配設されてい
て、各空気通路には、第１熱交換器(3)に対向して第１
ファン(F1)が、第２熱交換器(4)に対向して第２ファン
(F2)が夫々設けられ、 上記膨張機構(5,6)は、第１分岐管(10a)に設けられた第
１膨張機構(5)と、第２分岐管(10b)に設けられた第２膨
張機構(6)とを備える一方、上記圧縮機(1)の吐出圧力の過上昇時に吐出冷媒の一部
を導いて該冷媒を凝縮する熱源側補助熱交換器(21)が、
上流側を圧縮機(1)の吐出側に、下流側をアキュムレー
タ(8)の上流側に夫々接続して設けられると共に、 熱源
側補助熱交換器(21)は、第２熱交換器(4)と共通の空気
通路に設けられ、 圧縮機(1)の吐出圧力の過上昇時、第２ファン(F2)の送
風量を第１ファン(F1)の送風量よりも大きく設定するこ
とを特徴とする冷凍装置。2. A compressor (1), a use side heat exchanger (12), an expansion
The mechanism (5, 6) and the heat source side heat exchanger (3, 4) are connected by the refrigerant pipe (10).
A main refrigerant circuit (C) connected to the main refrigerant circuit.
(C) has an accumulator (8) on the suction side of the compressor (1).
The refrigerant discharged from the compressor (1) is transferred to the use-side heat exchanger (1).
After condensing in 2) and reducing the pressure by the expansion mechanism (5, 6), heat exchange
Refrigeration system that circulates refrigerant that evaporates in the heat exchangers (3, 4).
There are, the refrigerant pipe (10) of the part is formed by branched parallel first and second branch pipes (10a, 10b) are provided, the heat source-side heat exchanger (3, 4), first A first heat exchanger (3) provided in the branch pipe (10a); and a second heat exchanger (4) provided in the second branch pipe (10b) . ) And the second heat
The exchangers (4) are arranged in individual air passages, and each air passage has a first heat exchanger (3) opposed to the first heat exchanger (3).
The fan (F1) faces the second heat exchanger (4) and the second fan
(F2) are provided respectively, and the expansion mechanism (5, 6) is provided with a first branch pipe (10a) provided in the first branch pipe (10a) .
A first expansion mechanism (5), second bulging provided in the second branch pipe (10b)
While Ru and a Zhang mechanism (6), a part of the discharged refrigerant when excessive increase of the discharge pressure of the compressor (1)
A heat source side auxiliary heat exchanger (21) that guides and condenses the refrigerant,
The upstream side is the discharge side of the compressor (1), and the downstream side is an accumulator.
The heat source side auxiliary heat exchanger (21) is provided in the common air passage with the second heat exchanger (4), and is connected to the upstream side of the compressor (1). A refrigeration apparatus characterized in that when the discharge pressure rises excessively , the amount of air blown by the second fan (F2) is set to be larger than the amount of air blown by the first fan (F1).
て、 第１膨張機構(5)及び第２膨張機構(6)は、第１膨張弁
(5)及び第２膨張弁(6)よりなり、 圧縮機(1)の吐出圧力の過上昇時、第１膨張弁(5)を所定
開度に調整し、且つ第２膨張弁(6)を閉鎖する ことを特
徴とする冷凍装置。3. The refrigeration apparatus according to claim 1, wherein
Te, the first expansion mechanism (5) and the second expansion mechanism (6), the first expansion valve
(5) and the second expansion valve (6 ). When the discharge pressure of the compressor (1) rises excessively, the first expansion valve (5) is set to a predetermined value.
A refrigerating device, wherein the refrigerating device is adjusted to an opening degree and the second expansion valve (6) is closed .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19338696A JP3228135B2 (en) | 1996-07-23 | 1996-07-23 | Refrigeration equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19338696A JP3228135B2 (en) | 1996-07-23 | 1996-07-23 | Refrigeration equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH1038391A JPH1038391A (en) | 1998-02-13 |
| JP3228135B2 true JP3228135B2 (en) | 2001-11-12 |
Family
ID=16307078
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19338696A Expired - Fee Related JP3228135B2 (en) | 1996-07-23 | 1996-07-23 | Refrigeration equipment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3228135B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3468169B2 (en) * | 1999-08-31 | 2003-11-17 | ダイキン工業株式会社 | Refrigeration equipment |
| JP6647406B2 (en) * | 2016-07-29 | 2020-02-14 | 三菱電機株式会社 | Refrigeration cycle device |
-
1996
- 1996-07-23 JP JP19338696A patent/JP3228135B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH1038391A (en) | 1998-02-13 |
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