JPH11173711A - Dual refrigerator - Google Patents
Dual refrigeratorInfo
- Publication number
- JPH11173711A JPH11173711A JP34292297A JP34292297A JPH11173711A JP H11173711 A JPH11173711 A JP H11173711A JP 34292297 A JP34292297 A JP 34292297A JP 34292297 A JP34292297 A JP 34292297A JP H11173711 A JPH11173711 A JP H11173711A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- primary
- evaporator
- primary refrigerant
- secondary refrigerant
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Defrosting Systems (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本願発明は、ショーケース用
冷凍装置等として利用される二元冷凍装置に関し、さら
に詳しくは二元冷凍装置における除霜機構に関するもの
である。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a binary refrigeration system used as a refrigeration system for a showcase, and more particularly, to a defrosting mechanism in a binary refrigeration system.
【０００２】[0002]
【従来の技術】例えば、ショーケース用冷凍装置とし
て、図５に示すように、一次冷媒ｘを圧縮する一次冷媒
用圧縮機５、一次冷媒ｘを凝縮液化する一次冷媒用凝縮
器６、一次冷媒ｘを減圧する一次冷媒用減圧機構７およ
び一次冷媒ｘを蒸発気化させる一次冷媒用蒸発器８を順
次冷媒配管を介して順次接続してなる高温側冷凍ユニッ
トと、二次冷媒ｙを圧縮する二次冷媒用圧縮機９、前記
一次冷媒用蒸発器８との熱交換により二次冷媒ｙを凝縮
液化する二次冷媒用凝縮器１０、二次冷媒ｙを減圧する
二次冷媒用減圧機構１１および二次冷媒ｙを蒸発気化さ
せる二次冷媒用蒸発器１２を冷媒配管を介して順次接続
してなる低温側冷凍ユニットとを備えた二元冷凍装置が
用いられる場合がある。符号１３は一次冷媒用凝縮器６
を冷却するための冷却ファンである。なお、前記一次冷
媒用圧縮機５および一次冷媒用凝縮器６は室外ユニット
１を構成し、前記一次冷媒用減圧機構７、一次冷媒用蒸
発器８、二次冷媒用圧縮機９および二次冷媒用凝縮器１
０はカスケードユニット２を構成し、二次冷媒用減圧機
構１１および二次冷媒用蒸発器１２はショーケース用冷
凍ユニット３を構成することとなっており、前記カスケ
ードユニット２およびショーケース用冷凍ユニット３は
ショーケース配置室４に設置される。2. Description of the Prior Art For example, as a showcase refrigerating apparatus, as shown in FIG. 5, a primary refrigerant compressor 5 for compressing a primary refrigerant x, a primary refrigerant condenser 6 for condensing and liquefying the primary refrigerant x, a primary refrigerant a high-temperature side refrigeration unit in which a primary refrigerant decompression mechanism 7 for decompressing x and a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x are sequentially connected via refrigerant pipes; A secondary refrigerant compressor 9, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, a secondary refrigerant decompression mechanism 11 for decompressing the secondary refrigerant y, and In some cases, a binary refrigeration apparatus including a low-temperature refrigeration unit in which a secondary refrigerant evaporator 12 for evaporating and evaporating the secondary refrigerant y is sequentially connected via a refrigerant pipe is used. Reference numeral 13 denotes a condenser 6 for a primary refrigerant.
Is a cooling fan for cooling. The primary refrigerant compressor 5 and the primary refrigerant condenser 6 constitute the outdoor unit 1, and the primary refrigerant decompression mechanism 7, the primary refrigerant evaporator 8, the secondary refrigerant compressor 9, and the secondary refrigerant Condenser 1
Numeral 0 constitutes the cascade unit 2, and the secondary refrigerant decompression mechanism 11 and the secondary refrigerant evaporator 12 constitute the showcase refrigeration unit 3, and the cascade unit 2 and the showcase refrigeration unit 3 is installed in the showcase arrangement room 4.
【０００３】上記構成の二元冷凍装置において、冷凍運
転を継続していると、ショーケース用冷凍ユニット３に
おける二次冷媒用蒸発器１２に着霜が進行し、冷凍能力
が低下してくるので、所定の時間間隔で、あるいは着霜
の進行度合いを検知して二次冷媒用蒸発器１２の着霜を
融霜除去する除霜運転を行う必要がある。In the binary refrigeration system having the above structure, if the refrigeration operation is continued, frost formation proceeds on the evaporator 12 for the secondary refrigerant in the refrigeration unit 3 for the showcase, and the refrigeration capacity decreases. It is necessary to perform a defrosting operation at a predetermined time interval or by detecting the degree of progress of frost formation to melt and remove frost formation on the secondary refrigerant evaporator 12.
【０００４】従来の除霜運転は、図５に示すように、二
次冷媒用圧縮機９から吐出される高温の吐出ガス冷媒
（即ち、ホットガス）ｙを三方弁１５を介して二次冷媒
用蒸発器１２の入口側へバイパスさせるバイパス回路１
４を設け、前記三方弁１５を二次冷媒用圧縮機９とバイ
パス回路１４とを連通させるように切り換えることによ
り、該バイパス回路１４を介してホットガスｙを二次冷
媒用蒸発器１２に供給し、該ホットガスｙの保有する熱
により着霜を融霜除去するホットガスバイパス方式とさ
れていた。In a conventional defrosting operation, as shown in FIG. 5, a high-temperature discharge gas refrigerant (ie, hot gas) y discharged from a secondary refrigerant compressor 9 is supplied to a secondary refrigerant through a three-way valve 15. Circuit 1 for bypassing to the inlet side of evaporator 12
The hot gas y is supplied to the secondary refrigerant evaporator 12 through the bypass circuit 14 by switching the three-way valve 15 so that the compressor 9 for the secondary refrigerant communicates with the bypass circuit 14. However, the hot gas bypass method is used to melt and remove frost by the heat of the hot gas y.
【０００５】[0005]
【発明が解決しようとする課題】ところが、上記したホ
ットガスバイパス方式の除霜運転では、除霜能力に限界
があるため、除霜時間が長くなるという不具合があっ
た。なお、通常の空気調和機用蒸発器のようにフィンピ
ッチが小さい熱交換器が使用されていると、高い除霜能
力で除霜すると、伝熱管周りだけが先に融霜してしま
い、着霜全体の融霜が進まない場合が生じるおそれがあ
るので、ホットガスバイパス方式のようにあまり高くな
い除霜能力でゆっくりと除霜するのが望ましいが、ショ
ーケース用蒸発器の場合、フィンピッチが比較的大きい
熱交換器が使用されているため、高い除霜能力で短時間
で除霜を行っても、伝熱管周りの融霜だけで着霜が落下
する。しかも、ショーケースの場合、食品等が陳列され
ているため、除霜時間は短い方が望ましいという要求も
ある。However, in the above-described hot gas bypass type defrosting operation, there is a problem that the defrosting time becomes long because the defrosting ability is limited. If a heat exchanger with a small fin pitch is used, such as a normal air conditioner evaporator, if defrosting is performed with a high defrosting capacity, only the area around the heat transfer tubes will melt first, and the Since there is a possibility that the entire frost will not melt, it is desirable to defrost slowly with a not so high defrosting capacity as in the hot gas bypass method. Since a heat exchanger having a relatively large heat transfer rate is used, even if defrosting is performed in a short time with a high defrosting ability, frost formation is caused only by the frost around the heat transfer tube. In addition, in the case of a showcase, since foods and the like are displayed, there is a demand that a shorter defrosting time is desirable.
【０００６】また、二次冷媒用蒸発器への着霜を電気ヒ
ータによる加熱で融霜除去する方法もあるが、電気ヒー
タは、電力消費が大きいためランニングコストが高くな
るとともに、定期的なメンテナンスが必要となるという
不具合がある。There is also a method of removing frost on the secondary refrigerant evaporator by heating with an electric heater to remove the frost. However, the electric heater consumes a large amount of electric power, so that running costs are increased and periodic maintenance is performed. Is required.
【０００７】本願発明は、上記の点に鑑みてなされたも
ので、電気ヒータを用いることなく、冷媒の保有する高
い除霜能力で短時間で除霜を完了し得るようにすること
を目的とするものである。[0007] The present invention has been made in view of the above points, and an object of the present invention is to make it possible to complete defrosting in a short time with a high defrosting capacity of a refrigerant without using an electric heater. Is what you do.
【０００８】[0008]
【課題を解決するための手段】本願発明の第１の基本構
成（請求項１の発明）では、上記課題を解決するための
手段として、一次冷媒ｘを圧縮する一次冷媒用圧縮機
５、一次冷媒ｘを凝縮液化する一次冷媒用凝縮器６、一
次冷媒ｘを減圧する一次冷媒用減圧機構７および一次冷
媒ｘを蒸発気化させる一次冷媒用蒸発器８を冷媒配管１
６を介して順次接続してなる高温側冷凍サイクルＡと、
二次冷媒ｙを圧縮する二次冷媒用圧縮機９、前記一次冷
媒用蒸発器８との熱交換により二次冷媒ｙを凝縮液化す
る二次冷媒用凝縮器１０、二次冷媒ｙを減圧する二次冷
媒用減圧機構１１および二次冷媒ｙを蒸発気化させる二
次冷媒用蒸発器１２を冷媒配管１７を介して順次接続し
てなる低温側冷凍サイクルＢとを備えた二元冷凍装置に
おいて、前記高温側冷凍ユニットＡを逆サイクル運転が
可能に構成するとともに、前記高温側冷凍サイクルＡの
逆サイクル運転時において前記一次冷媒用圧縮機５から
吐出されるガス冷媒ｘを前記二次冷媒用蒸発器１２を経
て前記一次冷媒用減圧機構７の下流側へバイパスさせる
除霜用バイパス回路１８を設けている。According to a first basic configuration of the present invention (invention of claim 1), as means for solving the above-mentioned problems, a primary refrigerant compressor 5 for compressing a primary refrigerant x, a primary refrigerant The refrigerant pipe 1 includes a primary refrigerant condenser 6 for condensing and liquefying the refrigerant x, a primary refrigerant decompression mechanism 7 for decompressing the primary refrigerant x, and a primary refrigerant evaporator 8 for evaporating the primary refrigerant x.
6, a high-temperature refrigeration cycle A sequentially connected through
A secondary refrigerant compressor 9 for compressing the secondary refrigerant y, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, and depressurizing the secondary refrigerant y. In a binary refrigeration apparatus including a low-temperature side refrigeration cycle B in which a secondary refrigerant decompression mechanism 11 and a secondary refrigerant evaporator 12 for evaporating and evaporating the secondary refrigerant y are sequentially connected via a refrigerant pipe 17, The high-temperature side refrigeration unit A is configured to be capable of reverse cycle operation, and the gas refrigerant x discharged from the primary refrigerant compressor 5 during the reverse cycle operation of the high-temperature side refrigeration cycle A is vaporized for the secondary refrigerant. A defrost bypass circuit 18 is provided for bypassing to the downstream side of the primary refrigerant pressure reducing mechanism 7 through the device 12.
【０００９】上記のように構成したことにより、除霜運
転時においては、一次冷媒用圧縮機５から吐出される高
温のガス冷媒（即ち、ホットガス）ｘが、除霜用バイパ
ス回路１８を介して二次冷媒用蒸発器１２へ供給され、
二次冷媒用蒸発器１２の着霜を融霜した後、蒸発器とし
て作用する一次冷媒用凝縮器６で蒸発気化された後に一
次冷媒用圧縮機５へ還流されることとなる。従って、除
霜用熱源としては、一次冷媒用圧縮機５の仕事量と、一
次冷媒用凝縮器６と熱交換する媒体（例えば、外気）の
保有する熱とが利用されることとなるため、除霜能力が
大きく向上することとなる。With the above configuration, during the defrosting operation, the high-temperature gas refrigerant (ie, hot gas) x discharged from the primary refrigerant compressor 5 passes through the defrost bypass circuit 18. To the secondary refrigerant evaporator 12,
After the frost of the secondary refrigerant evaporator 12 is melted and frosted, it is vaporized and vaporized by the primary refrigerant condenser 6 acting as an evaporator, and then returned to the primary refrigerant compressor 5. Therefore, as the defrosting heat source, the work of the primary refrigerant compressor 5 and the heat held by the medium (for example, outside air) that exchanges heat with the primary refrigerant condenser 6 are used. The defrosting ability will be greatly improved.
【００１０】本願発明の第２の基本構成（請求項２の発
明）では、上記課題を解決するための手段として、一次
冷媒ｘを圧縮する一次冷媒用圧縮機５、一次冷媒ｘを凝
縮液化する一次冷媒用凝縮器６、一次冷媒ｘを減圧する
一次冷媒用減圧機構７および一次冷媒ｘを蒸発気化させ
る一次冷媒用蒸発器８を冷媒配管１６を介して順次接続
してなる高温側冷凍サイクルＡと、二次冷媒ｙを圧縮す
る二次冷媒用圧縮機９、前記一次冷媒用蒸発器８との熱
交換により二次冷媒ｙを凝縮液化する二次冷媒用凝縮器
１０、二次冷媒ｙを減圧する二次冷媒用減圧機構１１お
よび二次冷媒ｙを蒸発気化させる二次冷媒用蒸発器１２
を冷媒配管１７を介して順次接続してなる低温側冷凍サ
イクルＢとを備えた二元冷凍装置において、前記低温側
冷凍サイクルＢを逆サイクル運転が可能に構成するとと
もに、前記低温側冷凍サイクルＢの逆サイクル運転時に
前記二次冷媒用圧縮機９に還流する液冷媒ｙを蒸発気化
させる空冷熱交換器１９を付設している。In the second basic configuration of the present invention (the invention of claim 2), as means for solving the above problems, a primary refrigerant compressor 5 for compressing the primary refrigerant x, and condensing and liquefying the primary refrigerant x. A high-temperature side refrigeration cycle A in which a primary refrigerant condenser 6, a primary refrigerant decompression mechanism 7 for decompressing the primary refrigerant x, and a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x are sequentially connected via a refrigerant pipe 16. And a secondary refrigerant compressor 9 for compressing the secondary refrigerant y, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, and a secondary refrigerant y. A decompression mechanism 11 for the secondary refrigerant for reducing the pressure and an evaporator 12 for the secondary refrigerant for evaporating the secondary refrigerant y
And a low-temperature side refrigeration cycle B sequentially connected through a refrigerant pipe 17, the low-temperature side refrigeration cycle B is configured to be capable of reverse cycle operation, An air-cooled heat exchanger 19 for evaporating and evaporating the liquid refrigerant y flowing back to the secondary refrigerant compressor 9 during the reverse cycle operation is provided.
【００１１】上記のように構成したことにより、除霜運
転時においては、二次冷媒用圧縮機９から吐出された高
温のガス冷媒（即ち、ホットガス）ｙが、二次冷媒用蒸
発器１２に供給され、二次冷媒用蒸発器１２の着霜を融
霜した後、空冷熱交換器１９で蒸発気化された後に二次
冷媒用圧縮機９へ還流されることとなる。従って、除霜
用熱源としては、二次冷媒用圧縮機９の仕事量と、空冷
熱交換器１９と熱交換する媒体（例えば、室内空気）の
保有する熱とが利用されることとなるため、除霜能力が
大きく向上することとなる。With the above configuration, during the defrosting operation, the high-temperature gas refrigerant (ie, hot gas) y discharged from the secondary refrigerant compressor 9 is supplied to the secondary refrigerant evaporator 12. After the frost of the secondary refrigerant evaporator 12 is melted and frosted, the air is evaporated and vaporized by the air-cooling heat exchanger 19 and then returned to the secondary refrigerant compressor 9. Therefore, as the heat source for defrosting, the work of the compressor 9 for the secondary refrigerant and the heat held by the medium (for example, indoor air) that exchanges heat with the air-cooling heat exchanger 19 are used. As a result, the defrosting ability is greatly improved.
【００１２】請求項３の発明におけるように、前記空冷
熱交換器１９を、前記高温側冷凍サイクルＡにおける一
次冷媒用凝縮器６で兼用した場合、除霜運転時において
二次冷媒用凝縮器１２で凝縮液化された二次冷媒ｙを一
次冷媒用凝縮器６で蒸発気化できることとなり、部品点
数の低減およびコスト低減に寄与できる。なお、この場
合、外気の保有するする熱が除霜用熱源として利用され
ることとなる。When the air-cooling heat exchanger 19 is also used as the primary refrigerant condenser 6 in the high-temperature side refrigeration cycle A as in the third aspect of the present invention, the secondary refrigerant condenser 12 is used during the defrosting operation. Thus, the secondary refrigerant y condensed and liquefied can be evaporated and vaporized in the primary refrigerant condenser 6, which can contribute to a reduction in the number of parts and cost. In this case, the heat held by the outside air is used as a heat source for defrosting.
【００１３】本願発明の第３の基本構成（請求項４の発
明）では、上記課題を解決するための手段として、一次
冷媒ｘを圧縮する一次冷媒用圧縮機５、一次冷媒ｘを凝
縮液化する一次冷媒用凝縮器６、一次冷媒ｘを減圧する
一次冷媒用減圧機構７および一次冷媒ｘを蒸発気化させ
る一次冷媒用蒸発器８を冷媒配管１６を介して順次接続
してなる高温側冷凍サイクルＡと、二次冷媒ｙを圧縮す
る二次冷媒用圧縮機９、前記一次冷媒用蒸発器８との熱
交換により二次冷媒ｙを凝縮液化する二次冷媒用凝縮器
１０、二次冷媒ｙを減圧する二次冷媒用減圧機構１１お
よび二次冷媒ｙを蒸発気化させる二次冷媒用蒸発器１２
を冷媒配管１７を介して順次接続してなる低温側冷凍サ
イクルＢとを備えた二元冷凍装置において、前記高温側
冷凍サイクルＡおよび低温側冷凍サイクルＢを逆サイク
ル運転が可能に構成している。In a third basic configuration of the present invention (invention of claim 4), as means for solving the above problems, a primary refrigerant compressor 5 for compressing the primary refrigerant x, and condensing and liquefying the primary refrigerant x. A high-temperature side refrigeration cycle A in which a primary refrigerant condenser 6, a primary refrigerant decompression mechanism 7 for decompressing the primary refrigerant x, and a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x are sequentially connected via a refrigerant pipe 16. And a secondary refrigerant compressor 9 for compressing the secondary refrigerant y, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, and a secondary refrigerant y. A decompression mechanism 11 for the secondary refrigerant for reducing the pressure and an evaporator 12 for the secondary refrigerant for evaporating the secondary refrigerant y
And a low-temperature refrigeration cycle B, which is sequentially connected via a refrigerant pipe 17, wherein the high-temperature refrigeration cycle A and the low-temperature refrigeration cycle B can be operated in reverse cycle. .
【００１４】上記のように構成したことにより、除霜運
転時においては、二次冷媒用圧縮機９から吐出される高
温のガス冷媒（即ち、ホットガス）ｙが、二次冷媒用蒸
発器１２に供給され、二次冷媒用蒸発器１２の着霜を融
霜した後、蒸発器として作用している二次冷媒用凝縮器
１０で蒸発気化された後に二次冷媒用圧縮機９へ還流さ
れるとともに、一次冷媒用圧縮機５から吐出された高温
のガス冷媒（即ち、ホットガス）ｘが、一次冷媒用蒸発
器８に供給され、二次冷媒用凝縮器１０での液冷媒ｙの
蒸発気化を助けて自身凝縮液化された後、蒸発器として
作用している一次冷媒用凝縮器６で蒸発気化されて一次
冷媒用圧縮機５へ還流される。従って、除霜用熱源とし
ては、一次冷媒用圧縮機５および二次冷媒用圧縮機９の
仕事量と、一次冷媒用凝縮器６と熱交換する媒体（例え
ば、外気）の保有する熱とが利用されることとなるた
め、除霜能力が大きく向上することとなる。With the above configuration, during the defrosting operation, the high-temperature gas refrigerant (ie, hot gas) y discharged from the secondary refrigerant compressor 9 is supplied to the secondary refrigerant evaporator 12. Is supplied to the secondary refrigerant evaporator 12 to melt the frost, and after being evaporated and vaporized by the secondary refrigerant condenser 10 acting as an evaporator, is returned to the secondary refrigerant compressor 9. At the same time, the high-temperature gas refrigerant (that is, hot gas) x discharged from the primary refrigerant compressor 5 is supplied to the primary refrigerant evaporator 8, and the secondary refrigerant condenser 10 evaporates the liquid refrigerant y. After being condensed and liquefied by the aid of vaporization, it is evaporated and vaporized by the primary refrigerant condenser 6 acting as an evaporator and returned to the primary refrigerant compressor 5. Accordingly, as the defrosting heat source, the work of the primary refrigerant compressor 5 and the secondary refrigerant compressor 9 and the heat of the medium (for example, outside air) that exchanges heat with the primary refrigerant condenser 6 are provided. Since it is used, the defrosting ability is greatly improved.
【００１５】[0015]
【発明の実施の形態】以下、添付の図面を参照して、本
願発明の幾つかの好適な実施の形態について詳述する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Some preferred embodiments of the present invention will be described below in detail with reference to the accompanying drawings.
【００１６】第１の実施の形態（請求項１に対応） 図１には、本願発明の第１の実施の形態にかかる二元冷
凍装置が示されている。First Embodiment (corresponding to claim 1) FIG. 1 shows a binary refrigeration apparatus according to a first embodiment of the present invention.
【００１７】この二元冷凍装置は、図１に示すように、
既に従来技術の項において説明したと同様な構成とされ
ている。As shown in FIG. 1, this binary refrigeration system
The configuration is the same as that already described in the section of the prior art.
【００１８】即ち、この二元冷凍装置は、ショーケース
用冷凍装置として用いられるものであり、一次冷媒ｘを
圧縮する一次冷媒用圧縮機５、一次冷媒ｘを凝縮液化す
る一次冷媒用凝縮器６、一次冷媒ｘを減圧する一次冷媒
用減圧機構７および一次冷媒ｘを蒸発気化させる一次冷
媒用蒸発器８を冷媒配管１６を介して順次接続してなる
高温側冷凍サイクルＡと、二次冷媒ｙを圧縮する二次冷
媒用圧縮機９、前記一次冷媒用蒸発器８との熱交換によ
り二次冷媒ｙを凝縮液化する二次冷媒用凝縮器１０、二
次冷媒ｙを減圧する二次冷媒用減圧機構１１および二次
冷媒ｙを蒸発気化させる二次冷媒用蒸発器１２を冷媒配
管１７を介して順次接続してなる低温側冷凍サイクルＢ
とを備えて構成されている。符号１３は一次冷媒用凝縮
器６を冷却するための冷却ファンである。That is, this binary refrigerating apparatus is used as a showcase refrigerating apparatus, and comprises a primary refrigerant compressor 5 for compressing a primary refrigerant x, and a primary refrigerant condenser 6 for condensing and liquefying the primary refrigerant x. A high-temperature side refrigeration cycle A in which a primary refrigerant decompression mechanism 7 for decompressing the primary refrigerant x and a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x are sequentially connected through a refrigerant pipe 16; , A secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, and a secondary refrigerant for decompressing the secondary refrigerant y. A low-temperature refrigeration cycle B in which a pressure reducing mechanism 11 and a secondary refrigerant evaporator 12 for evaporating and evaporating the secondary refrigerant y are sequentially connected via a refrigerant pipe 17.
It is comprised including. Reference numeral 13 denotes a cooling fan for cooling the condenser 6 for the primary refrigerant.
【００１９】なお、前記一次冷媒用圧縮機５および一次
冷媒用凝縮器６は室外ユニット１を構成し、前記一次冷
媒用減圧機構７、一次冷媒用蒸発器８、二次冷媒用圧縮
機９および二次冷媒用凝縮器１０はカスケードユニット
２を構成し、二次冷媒用減圧機構１１および二次冷媒用
蒸発器１２はショーケース用冷凍ユニット３を構成する
こととなっており、前記カスケードユニット２およびシ
ョーケース用冷凍ユニット３はショーケース配置室４に
設置される。The compressor 5 for the primary refrigerant and the condenser 6 for the primary refrigerant constitute the outdoor unit 1. The decompression mechanism 7 for the primary refrigerant, the evaporator 8 for the primary refrigerant, the compressor 9 for the secondary refrigerant and The condenser 10 for the secondary refrigerant constitutes the cascade unit 2, and the decompression mechanism 11 for the secondary refrigerant and the evaporator 12 for the secondary refrigerant constitute the refrigeration unit 3 for the showcase. The showcase refrigeration unit 3 is installed in the showcase arrangement room 4.
【００２０】そして、この二元冷凍装置においては、前
記高温側冷凍サイクルＡにおける一次冷媒用圧縮機５の
吐出側に四路切換弁２０を設けて、該高温側冷凍サイク
ルＡの逆サイクル運転が可能なように構成されており、
前記高温側冷凍サイクルＡの逆サイクル運転時において
前記一次冷媒用圧縮機５から吐出されるガス冷媒ｘを前
記二次冷媒用蒸発器１２を経て前記一次冷媒用減圧機構
７の下流側へバイパスさせる除霜用バイパス回路１８が
設けられている。該除霜用バイパス回路１８の途中に
は、前記二次冷媒用蒸発器１２と熱交換可能に構成され
た加熱用熱交換器２１が設けられている。符号２２は一
次冷媒用凝縮器６から一次冷媒用減圧機構７への冷媒流
通のみを許容する逆止弁、２３は該逆止弁２２と並列に
接続された減圧機構であり、冷却運転時には一次冷媒ｘ
は逆止弁２２を介して流通し、除霜運転時には一次冷媒
ｘは減圧機構２３を介して流通することとなっている。
符号２４は前記除霜用バイパス回路１８の入口側に介設
された除霜運転時にのみ開弁する開閉弁、２５は前記除
霜用バイパス回路１８の出口側に介設された除霜運転時
にのみ冷媒流通を許容する逆止弁である。なお、前記開
閉弁２４および逆止弁２５に代えて、高温用冷凍サイク
ルＡと除霜用バイパス回路１８との分岐点に三方弁を介
設してもよい。In this two-way refrigeration system, a four-way switching valve 20 is provided on the discharge side of the primary refrigerant compressor 5 in the high-temperature side refrigeration cycle A, so that the reverse cycle operation of the high-temperature side refrigeration cycle A is performed. Is configured as possible,
During the reverse cycle operation of the high-temperature side refrigeration cycle A, the gas refrigerant x discharged from the primary refrigerant compressor 5 is bypassed to the downstream side of the primary refrigerant pressure reducing mechanism 7 via the secondary refrigerant evaporator 12. A defrost bypass circuit 18 is provided. A heating heat exchanger 21 configured to be able to exchange heat with the secondary refrigerant evaporator 12 is provided in the middle of the defrost bypass circuit 18. Reference numeral 22 denotes a check valve that permits only the flow of the refrigerant from the primary refrigerant condenser 6 to the primary refrigerant pressure reducing mechanism 7, and 23 denotes a pressure reducing mechanism connected in parallel with the check valve 22, and the primary pressure during cooling operation. Refrigerant x
Flows through the check valve 22, and the primary refrigerant x flows through the pressure reducing mechanism 23 during the defrosting operation.
Reference numeral 24 denotes an open / close valve provided only at the time of defrosting operation provided on the inlet side of the bypass circuit 18 for defrosting, and reference numeral 25 designates an open / close valve provided at the outlet side of the bypass circuit 18 for defrosting. This is a check valve that allows only refrigerant flow. Instead of the on-off valve 24 and the check valve 25, a three-way valve may be provided at a branch point between the high-temperature refrigeration cycle A and the defrost bypass circuit 18.
【００２１】上記のように構成された二元冷凍装置は、
次のように作用する。The binary refrigeration system configured as described above has
It works as follows.
【００２２】（Ｉ） 冷却運転時 この時、四路切換弁２０は正サイクル側に切り換えら
れ、開閉弁２４は閉弁され、一次冷媒用圧縮機５、二次
冷媒用圧縮機９および冷却ファン１３は運転されてい
る。(I) At the time of cooling operation At this time, the four-way switching valve 20 is switched to the forward cycle side, the on-off valve 24 is closed, the primary refrigerant compressor 5, the secondary refrigerant compressor 9, and the cooling fan 13 is operating.
【００２３】一次冷媒用圧縮機５から圧送された一次冷
媒ｘは、図１に実線矢印で示すように、四路切換弁２０
を経て一次冷媒用凝縮器６に供給され、そこで凝縮液化
された後、逆止弁２２を経た後一次冷媒用減圧機構７で
減圧され、その後一次冷媒用蒸発器８で蒸発気化され、
四路切換弁２０を経て一次冷媒用圧縮機５へ還流され
る。The primary refrigerant x sent from the primary refrigerant compressor 5 under pressure is supplied to the four-way switching valve 20 as shown by the solid arrows in FIG.
Is supplied to the condenser 6 for the primary refrigerant, and is condensed and liquefied there. After passing through the check valve 22, the pressure is reduced by the pressure reducing mechanism 7 for the primary refrigerant, and thereafter, it is evaporated and vaporized by the evaporator 8 for the primary refrigerant.
The refrigerant is returned to the primary refrigerant compressor 5 through the four-way switching valve 20.
【００２４】一方、二次冷媒用圧縮機９から圧送された
二次冷媒ｙは、図１に実線矢印で示すように、二次冷媒
用凝縮器１０において前記一次冷媒用蒸発器８との熱交
換により凝縮液化された後、二次冷媒用減圧機構１１で
減圧され、その後二次冷媒用蒸発器１２で蒸発気化さ
れ、二次冷媒用圧縮機９へ還流される。従って、一次冷
媒用蒸発器８との熱交換により低温化された二次冷媒ｙ
が二次冷媒用蒸発器１２において蒸発気化することによ
り、二次冷媒用蒸発器１２による冷却作用が大きく向上
することとなる。On the other hand, as shown by a solid line arrow in FIG. 1, the secondary refrigerant y pressure-fed from the secondary refrigerant compressor 9 is transferred to the primary refrigerant evaporator 8 in the secondary refrigerant condenser 10 by heat. After being condensed and liquefied by the exchange, the pressure is reduced by the secondary refrigerant decompression mechanism 11, then evaporated and vaporized by the secondary refrigerant evaporator 12, and returned to the secondary refrigerant compressor 9. Therefore, the secondary refrigerant y which has been cooled down by heat exchange with the primary refrigerant evaporator 8
Is evaporated and vaporized in the secondary refrigerant evaporator 12, so that the cooling effect of the secondary refrigerant evaporator 12 is greatly improved.
【００２５】（ＩＩ） 除霜運転時 この時、四路切換弁２０は逆サイクル側に切り換えら
れ、開閉弁２４は開弁され、一次冷媒用圧縮機５および
冷却ファン１３は運転され、二次冷媒用圧縮機９は運転
停止されている。(II) During defrosting operation At this time, the four-way switching valve 20 is switched to the reverse cycle side, the on-off valve 24 is opened, the primary refrigerant compressor 5 and the cooling fan 13 are operated, and the secondary The operation of the refrigerant compressor 9 is stopped.
【００２６】一次冷媒用圧縮機５から吐出される高温の
ガス冷媒（即ち、ホットガス）ｘは、図１に点線で示す
ように、四路切換弁２０を経た後除霜用バイパス回路１
８を介して二次冷媒用蒸発器１２へ供給され、二次冷媒
用蒸発器１２の着霜を融霜した後、減圧機構２３を経て
蒸発器として作用する一次冷媒用凝縮器６に供給され、
そこで蒸発気化された後に四路切換弁２０を経て一次冷
媒用圧縮機５へ還流されることとなる。従って、除霜用
熱源としては、一次冷媒用圧縮機５の仕事量と、一次冷
媒用凝縮器６と熱交換する媒体である外気の保有する熱
とが利用されることとなるため、除霜能力が大きく向上
することとなる。The high-temperature gas refrigerant (ie, hot gas) x discharged from the primary refrigerant compressor 5 passes through the four-way switching valve 20 and then passes through the defrost bypass circuit 1 as shown by the dotted line in FIG.
8, is supplied to the secondary refrigerant evaporator 12, melts frost on the secondary refrigerant evaporator 12, and is then supplied to the primary refrigerant condenser 6 acting as an evaporator via the pressure reducing mechanism 23. ,
Then, after being vaporized and vaporized, the refrigerant is returned to the primary refrigerant compressor 5 via the four-way switching valve 20. Therefore, as the heat source for defrosting, the work of the compressor 5 for the primary refrigerant and the heat held by the outside air, which is a medium for exchanging heat with the condenser 6 for the primary refrigerant, are used. The ability will be greatly improved.
【００２７】なお、ショーケース用冷凍装置における蒸
発器の場合、フィンピッチが比較的大きい熱交換器が使
用されているため、本実施の形態におけるように、高い
除霜能力で短時間で除霜を行っても、伝熱管周りの融霜
だけで着霜が落下するので、着霜が残るということはな
い。しかも、ショーケースの場合、食品等が陳列されて
いるため、除霜時間は短い方が望ましいという要求も満
たすことができる。In the case of the evaporator in the showcase refrigeration system, since a heat exchanger having a relatively large fin pitch is used, the defrosting is performed in a short time with a high defrosting ability as in the present embodiment. However, since frost drops only due to the frost around the heat transfer tubes, frost does not remain. In addition, in the case of a showcase, since food and the like are displayed, it is possible to satisfy the requirement that a shorter defrosting time is desirable.
【００２８】また、電気ヒータを用いる除霜方法ではな
く、冷媒により搬送される熱により除霜を行うこととな
っているため、ランニングコストが高くなることもな
く、定期的なメンテナンスも不必要となる。In addition, since the defrosting is performed not by the defrosting method using the electric heater but by the heat carried by the refrigerant, the running cost is not increased and the periodic maintenance is unnecessary. Become.
【００２９】第２の実施の形態（請求項２に対応） 図２には、本願発明の第２の実施の形態にかかる二元冷
凍装置が示されている。Second Embodiment (Corresponding to Claim 2) FIG. 2 shows a binary refrigeration apparatus according to a second embodiment of the present invention.
【００３０】この場合、高温側冷凍サイクルＡは、一次
冷媒ｘを圧縮する一次冷媒用圧縮機５、一次冷媒ｘを凝
縮液化する一次冷媒用凝縮器６、一次冷媒ｘを減圧する
一次冷媒用減圧機構７および一次冷媒ｘを蒸発気化させ
る一次冷媒用蒸発器８を冷媒配管１６を介して順次接続
して構成されている。In this case, the high-temperature side refrigeration cycle A includes a primary refrigerant compressor 5 for compressing the primary refrigerant x, a primary refrigerant condenser 6 for condensing and liquefying the primary refrigerant x, and a primary refrigerant decompression for reducing the primary refrigerant x. A mechanism 7 and a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x are sequentially connected via a refrigerant pipe 16.
【００３１】一方低温側冷凍サイクルＢにおける二次冷
媒用圧縮機９の吐出側に四路切換弁２６を設けて、逆サ
イクル運転が可能に構成されており、該低温側冷凍サイ
クルＢの逆サイクル運転時に前記二次冷媒用圧縮機９に
還流する液冷媒ｙを蒸発気化させる空冷熱交換器１９が
付設されている。なお、第１の実施の形態における除霜
用バイパス回路１８は省略される。符号２７は空冷熱交
換器１９の冷却ファン、２８は二次冷媒用減圧機構１１
と並列に接続された除霜運転時にのみ冷媒流通を許容す
る逆止弁、２９は二次冷媒用凝縮器１０から二次冷媒用
減圧機構１１への冷媒流通のみを許容する逆止弁、３０
は該逆止弁２９と並列に接続された減圧機構であり、冷
却運転時には二次冷媒ｙは逆止弁２９を介して流通し、
除霜運転時には二次冷媒ｙは減圧機構３０を介して流通
することとなっている。その他の構成は、第１の実施の
形態におけると同様なので説明を省略する。On the other hand, a four-way switching valve 26 is provided on the discharge side of the secondary refrigerant compressor 9 in the low-temperature side refrigeration cycle B to enable reverse cycle operation. An air-cooled heat exchanger 19 for evaporating and evaporating the liquid refrigerant y flowing back to the secondary refrigerant compressor 9 during operation is provided. Note that the defrost bypass circuit 18 in the first embodiment is omitted. Reference numeral 27 denotes a cooling fan of the air-cooled heat exchanger 19, and reference numeral 28 denotes a secondary refrigerant pressure reducing mechanism 11.
A check valve 29 connected in parallel to allow the refrigerant to flow only during the defrosting operation; 29 is a check valve that allows only the refrigerant to flow from the secondary refrigerant condenser 10 to the secondary refrigerant pressure reducing mechanism 11;
Is a pressure reducing mechanism connected in parallel with the check valve 29. During the cooling operation, the secondary refrigerant y flows through the check valve 29,
During the defrosting operation, the secondary refrigerant y flows through the pressure reducing mechanism 30. Other configurations are the same as those in the first embodiment, and a description thereof will be omitted.
【００３２】上記のように構成された二元冷凍装置は、
次のように作用する。The binary refrigeration system configured as described above has
It works as follows.
【００３３】（Ｉ） 冷却運転時 この時、四路切換弁２６は正サイクル側に切り換えら
れ、一次冷媒用圧縮機５、二次冷媒用圧縮機９および冷
却ファン１３，２７は運転されている。(I) Cooling operation At this time, the four-way switching valve 26 is switched to the forward cycle side, and the primary refrigerant compressor 5, the secondary refrigerant compressor 9, and the cooling fans 13, 27 are operated. .
【００３４】一次冷媒用圧縮機５から圧送された一次冷
媒ｘは、図２に実線矢印で示すように、一次冷媒用凝縮
器６に供給され、そこで凝縮液化された後、一次冷媒用
減圧機構７で減圧され、その後一次冷媒用蒸発器８で蒸
発気化され、一次冷媒用圧縮機５へ還流される。The primary refrigerant x fed from the primary refrigerant compressor 5 is supplied to the primary refrigerant condenser 6 where it is condensed and liquefied, as shown by the solid arrow in FIG. The pressure is reduced at 7, then evaporated and vaporized at the primary refrigerant evaporator 8 and returned to the primary refrigerant compressor 5.
【００３５】一方、二次冷媒用圧縮機９から圧送された
二次冷媒ｙは、図２に実線矢印で示すように、四路切換
弁２６を経た後空冷熱交換器１９で冷却ファン２７から
の冷却風により冷却され、さらに二次冷媒用凝縮器１０
において前記一次冷媒用蒸発器８との熱交換により凝縮
液化され、逆止弁２９を経た後二次冷媒用減圧機構１１
で減圧され、その後二次冷媒用蒸発器１２で蒸発気化さ
れ、四路切換弁２６を経て二次冷媒用圧縮機９へ還流さ
れる。従って、一次冷媒用蒸発器８との熱交換により低
温化された二次冷媒ｙが二次冷媒用蒸発器１２において
蒸発気化することにより、二次冷媒用蒸発器１２による
冷却作用が大きく向上することとなる。なお、この場
合、空冷熱交換器１９は二次冷媒用凝縮器１０へ供給さ
れる冷媒を予冷することとなる。On the other hand, the secondary refrigerant y pressure-fed from the secondary refrigerant compressor 9 passes through the four-way switching valve 26 and then from the cooling fan 27 in the air-cooled heat exchanger 19 as shown by the solid arrow in FIG. Is cooled by the cooling air of the
Is condensed and liquefied by heat exchange with the primary refrigerant evaporator 8, passes through the check valve 29, and then the secondary refrigerant pressure reducing mechanism 11
After that, the refrigerant is evaporated and vaporized by the secondary refrigerant evaporator 12 and returned to the secondary refrigerant compressor 9 via the four-way switching valve 26. Therefore, the secondary refrigerant y whose temperature has been lowered by heat exchange with the primary refrigerant evaporator 8 is evaporated and vaporized in the secondary refrigerant evaporator 12, so that the cooling effect of the secondary refrigerant evaporator 12 is greatly improved. It will be. In this case, the air-cooled heat exchanger 19 pre-cools the refrigerant supplied to the secondary refrigerant condenser 10.
【００３６】（ＩＩ） 除霜運転時 この時、四路切換弁２０は逆サイクル側に切り換えら
れ、一次冷媒用圧縮機５および冷却ファン１３は運転停
止され、二次冷媒用圧縮機９および冷却ファン２７は運
転されている。(II) Defrosting Operation At this time, the four-way switching valve 20 is switched to the reverse cycle side, the operation of the primary refrigerant compressor 5 and the cooling fan 13 is stopped, and the operation of the secondary refrigerant compressor 9 and the cooling The fan 27 is operating.
【００３７】二次冷媒用圧縮機９から吐出される高温の
ガス冷媒（即ち、ホットガス）ｘは、図２に点線で示す
ように、四路切換弁２６を経て二次冷媒用蒸発器１２へ
供給され、二次冷媒用蒸発器１２の着霜を融霜した後、
逆止弁２８および減圧機構３０を経て蒸発器として作用
している空冷熱交換器１９に供給され、そこで蒸発気化
された後に四路切換弁２６を経て二次冷媒用圧縮機９へ
還流されることとなる。従って、除霜用熱源としては、
二次冷媒用圧縮機９の仕事量と、空冷熱交換器１９と熱
交換する媒体である室内空気の保有する熱とが利用され
ることとなるため、除霜能力が大きく向上することとな
る。The high-temperature gas refrigerant (ie, hot gas) x discharged from the secondary refrigerant compressor 9 passes through a four-way switching valve 26 as shown by a dotted line in FIG. Is supplied to the secondary refrigerant evaporator 12 to melt the frost,
It is supplied to the air-cooled heat exchanger 19 acting as an evaporator via the check valve 28 and the pressure reducing mechanism 30, where it is evaporated and vaporized and then returned to the secondary refrigerant compressor 9 via the four-way switching valve 26. It will be. Therefore, as a defrost heat source,
Since the work of the compressor 9 for the secondary refrigerant and the heat held by the indoor air, which is a medium that exchanges heat with the air-cooled heat exchanger 19, are used, the defrosting ability is greatly improved. .
【００３８】なお、ショーケース用冷凍装置における蒸
発器の場合、フィンピッチが比較的大きい熱交換器が使
用されているため、本実施の形態におけるように、高い
除霜能力で短時間で除霜を行っても、伝熱管周りの融霜
だけで着霜が落下するので、着霜が残るということはな
い。しかも、ショーケースの場合、食品等が陳列されて
いるため、除霜時間は短い方が望ましいという要求も満
たすことができる。In the case of an evaporator in a refrigeration system for a showcase, a heat exchanger having a relatively large fin pitch is used. However, since frost drops only due to the frost around the heat transfer tubes, frost does not remain. In addition, in the case of a showcase, since food and the like are displayed, it is possible to satisfy the requirement that a shorter defrosting time is desirable.
【００３９】また、電気ヒータを用いる除霜方法ではな
く、冷媒により搬送される熱により除霜を行うこととな
っているため、ランニングコストが高くなることもな
く、定期的なメンテナンスも不必要となる。Further, since the defrosting is performed not by the defrosting method using the electric heater but by the heat carried by the refrigerant, the running cost is not increased and the periodic maintenance is unnecessary. Become.
【００４０】第３の実施の形態（請求項３に対応） 図３には、本願発明の第３の実施の形態にかかる二元冷
凍装置が示されている。Third Embodiment (corresponding to claim 3) FIG. 3 shows a binary refrigeration apparatus according to a third embodiment of the present invention.
【００４１】この場合、カスケードユニット２が室外ユ
ニット１内に配置されており、低温側冷凍サイクルＢに
おいて除霜運転時に減圧機構３０の出口側となる位置か
ら三方弁３１を介して分岐し、高温側冷凍サイクルＡに
おいて除霜運転時に一次冷媒用凝縮器６の入口側となる
位置に至る第１除霜運転用回路３２と、高温側冷凍サイ
クルＡにおいて除霜運転用に一次冷媒用凝縮器６の出口
側となる位置から三方弁３３を介して分岐し、低温側冷
凍サイクルＢにおいて除霜運転時に二次冷媒用凝縮器１
０の出口側となる位置に至る第２除霜運転用回路３４と
が付設されている。そして、除霜運転時に二次冷媒ｙが
減圧機構３０、第１除霜運転用回路３２、一次冷媒用凝
縮器６および第２除霜運転用回路３４を介して二次冷媒
用凝縮器１０の出口側へ流通することとなっている。第
２の実施の形態における空冷熱交換器１９および冷却フ
ァン２７は省略される。つまり、第２の実施の形態にお
ける空冷熱交換器１９を一次冷媒用凝縮器６で兼用する
ように構成されているのである。その他の構成は、第１
および第２の実施の形態におけると同様なので説明を省
略する。In this case, the cascade unit 2 is disposed in the outdoor unit 1 and branches off from the position on the outlet side of the pressure reducing mechanism 30 during the defrosting operation in the low-temperature side refrigeration cycle B via the three-way valve 31, and the high-temperature The first defrosting operation circuit 32 reaches a position on the inlet side of the primary refrigerant condenser 6 during the defrosting operation in the side refrigeration cycle A, and the primary refrigerant condenser 6 for the defrosting operation in the high temperature side refrigeration cycle A. Of the secondary refrigerant condenser 1 during the defrosting operation in the low-temperature side refrigeration cycle B from the position on the outlet side of the
A second defrosting operation circuit 34 that reaches a position on the exit side of 0 is additionally provided. During the defrosting operation, the secondary refrigerant y is supplied to the secondary refrigerant condenser 10 via the pressure reducing mechanism 30, the first defrosting operation circuit 32, the primary refrigerant condenser 6, and the second defrosting operation circuit. It will be distributed to the exit side. The air-cooled heat exchanger 19 and the cooling fan 27 in the second embodiment are omitted. That is, the air-cooled heat exchanger 19 in the second embodiment is configured to be also used as the primary refrigerant condenser 6. Other configurations are the first
The description is omitted because it is the same as in the second embodiment.
【００４２】上記のように構成された二元冷凍装置は、
次のように作用する。The binary refrigeration system configured as described above has:
It works as follows.
【００４３】（Ｉ） 冷却運転時 この時、四路切換弁２６は正サイクル側に切り換えら
れ、三方弁３１，３３は低温側冷凍サイクルＢ側および
高温側冷凍サイクルＡ側に切り換えられ、一次冷媒用圧
縮機５、二次冷媒用圧縮機９および冷却ファン１３は運
転されている。(I) At the time of cooling operation At this time, the four-way switching valve 26 is switched to the normal cycle side, and the three-way valves 31 and 33 are switched to the low-temperature side refrigeration cycle B side and the high-temperature side refrigeration cycle A side. Compressor 5, secondary refrigerant compressor 9, and cooling fan 13 are operating.
【００４４】一次冷媒用圧縮機５から圧送された一次冷
媒ｘは、図３に実線矢印で示すように、一次冷媒用凝縮
器６に供給され、そこで凝縮液化された後、一次冷媒用
減圧機構７で減圧され、その後一次冷媒用蒸発器８で蒸
発気化され、一次冷媒用圧縮機５へ還流される。The primary refrigerant x fed from the primary refrigerant compressor 5 is supplied to a primary refrigerant condenser 6 where it is condensed and liquefied as shown by a solid line arrow in FIG. The pressure is reduced at 7, then evaporated and vaporized at the primary refrigerant evaporator 8 and returned to the primary refrigerant compressor 5.
【００４５】一方、二次冷媒用圧縮機９から圧送された
二次冷媒ｙは、図３に実線矢印で示すように、四路切換
弁２６を経て二次冷媒用凝縮器１０に供給され、そこで
前記一次冷媒用蒸発器８との熱交換により凝縮液化さ
れ、逆止弁２９を経た後二次冷媒用減圧機構１１で減圧
され、その後二次冷媒用蒸発器１２で蒸発気化され、四
路切換弁２６を経て二次冷媒用圧縮機９へ還流される。
従って、一次冷媒用蒸発器８との熱交換により低温化さ
れた二次冷媒ｙが二次冷媒用蒸発器１２において蒸発気
化することにより、二次冷媒用蒸発器１２による冷却作
用が大きく向上することとなる。On the other hand, the secondary refrigerant y pressure-fed from the secondary refrigerant compressor 9 is supplied to the secondary refrigerant condenser 10 through the four-way switching valve 26 as shown by the solid arrow in FIG. Then, it is condensed and liquefied by heat exchange with the primary refrigerant evaporator 8, passes through a check valve 29, is decompressed by the secondary refrigerant depressurizing mechanism 11, and is then evaporated and vaporized by the secondary refrigerant evaporator 12, and is subjected to four-way The refrigerant is returned to the secondary refrigerant compressor 9 via the switching valve 26.
Therefore, the secondary refrigerant y whose temperature has been lowered by heat exchange with the primary refrigerant evaporator 8 is evaporated and vaporized in the secondary refrigerant evaporator 12, so that the cooling effect of the secondary refrigerant evaporator 12 is greatly improved. It will be.
【００４６】（ＩＩ） 除霜運転時 この時、四路切換弁２０は逆サイクル側に切り換えら
れ、三方弁３１，３３は第１および第２除霜運転用回路
３２，３４側に切り換えられ、一次冷媒用圧縮機５は運
転停止され、二次冷媒用圧縮機９および冷却ファン１３
は運転されている。(II) During defrosting operation At this time, the four-way switching valve 20 is switched to the reverse cycle side, and the three-way valves 31, 33 are switched to the first and second defrosting operation circuits 32, 34. The operation of the primary refrigerant compressor 5 is stopped, and the operation of the secondary refrigerant compressor 9 and the cooling fan 13
Is driving.
【００４７】二次冷媒用圧縮機９から吐出される高温の
ガス冷媒（即ち、ホットガス）ｘは、図３に点線で示す
ように、四路切換弁２６を経て二次冷媒用蒸発器１２へ
供給され、二次冷媒用蒸発器１２の着霜を融霜した後、
逆止弁２８、減圧機構３０および第１除霜運転用回路３
２を経て蒸発器として作用している一次冷媒用凝縮器６
に供給され、そこで蒸発気化された後に第２除霜運転用
回路３４および四路切換弁２６を経て二次冷媒用圧縮機
９へ還流されることとなる。従って、除霜用熱源として
は、二次冷媒用圧縮機９の仕事量と、一次冷媒用凝縮器
６と熱交換する媒体である外気の保有する熱とが利用さ
れることとなるため、除霜能力が大きく向上することと
なる。The high-temperature gas refrigerant (that is, hot gas) x discharged from the secondary refrigerant compressor 9 passes through a four-way switching valve 26 as shown by a dotted line in FIG. Is supplied to the secondary refrigerant evaporator 12 to melt the frost,
Check valve 28, pressure reducing mechanism 30, and first defrosting operation circuit 3
And a condenser 6 for the primary refrigerant acting as an evaporator
After being evaporated and vaporized there, it is returned to the secondary refrigerant compressor 9 via the second defrosting operation circuit 34 and the four-way switching valve 26. Therefore, as the heat source for defrosting, the work of the compressor 9 for the secondary refrigerant and the heat held by the outside air, which is a medium that exchanges heat with the condenser 6 for the primary refrigerant, are used. The frost capacity will be greatly improved.
【００４８】なお、ショーケース用冷凍装置における蒸
発器の場合、フィンピッチが比較的大きい熱交換器が使
用されているため、本実施の形態におけるように、高い
除霜能力で短時間で除霜を行っても、伝熱管周りの融霜
だけで着霜が落下するので、着霜が残るということはな
い。しかも、ショーケースの場合、食品等が陳列されて
いるため、除霜時間は短い方が望ましいという要求も満
たすことができる。In the case of the evaporator in the showcase refrigeration system, since a heat exchanger having a relatively large fin pitch is used, as in the present embodiment, defrosting is performed in a short time with a high defrosting ability. However, since frost drops only due to the frost around the heat transfer tubes, frost does not remain. In addition, in the case of a showcase, since food and the like are displayed, it is possible to satisfy the requirement that a shorter defrosting time is desirable.
【００４９】また、電気ヒータを用いる除霜方法ではな
く、冷媒により搬送される熱により除霜を行うこととな
っているため、ランニングコストが高くなることもな
く、定期的なメンテナンスも不必要となる。Further, since the defrosting is performed not by the defrosting method using the electric heater but by the heat carried by the refrigerant, the running cost is not increased and the periodic maintenance is unnecessary. Become.
【００５０】第４の実施の形態（請求項４に対応） 図４には、本願発明の第４の実施の形態にかかる二元冷
凍装置が示されている。Fourth Embodiment (corresponding to claim 4) FIG. 4 shows a binary refrigeration apparatus according to a fourth embodiment of the present invention.
【００５１】この場合、高温側冷凍サイクルＡおよび低
温側冷凍サイクルＢにおける一次冷媒用圧縮機５および
二次冷媒用圧縮機９の吐出側に四路切換弁２０，２６を
それぞれ設けて、両サイクルＡ，Ｂともに逆サイクル運
転が可能に構成されている。符号２８は二次冷媒用減圧
機構１１と並列に接続された除霜運転時にのみ冷媒流通
を許容する逆止弁、２９は二次冷媒用凝縮器１０から二
次冷媒用減圧機構１１への冷媒流通のみを許容する逆止
弁、３０は該逆止弁２９と並列に接続された減圧機構、
３５は一次冷媒用減圧機構７と並列に接続された逆止弁
である。その他の構成は、第１の実施の形態におけると
同様なので説明を省略する。In this case, four-way switching valves 20 and 26 are provided on the discharge side of the primary refrigerant compressor 5 and the secondary refrigerant compressor 9 in the high-temperature refrigeration cycle A and the low-temperature refrigeration cycle B, respectively. Both A and B are configured to enable reverse cycle operation. Reference numeral 28 denotes a check valve connected in parallel with the secondary refrigerant pressure reducing mechanism 11 and allowing the refrigerant to flow only during the defrosting operation. Reference numeral 29 denotes a refrigerant from the secondary refrigerant condenser 10 to the secondary refrigerant pressure reducing mechanism 11. A check valve allowing only circulation, 30 is a pressure reducing mechanism connected in parallel with the check valve 29,
A check valve 35 is connected in parallel with the primary refrigerant pressure reducing mechanism 7. Other configurations are the same as those in the first embodiment, and a description thereof will be omitted.
【００５２】上記のように構成された二元冷凍装置は、
次のように作用する。The binary refrigeration system configured as described above has
It works as follows.
【００５３】（Ｉ） 冷却運転時 この時、四路切換弁２０，２６は正サイクル側に切り換
えられ、一次冷媒用圧縮機５、二次冷媒用圧縮機９およ
び冷却ファン１３は運転されている。(I) Cooling operation At this time, the four-way switching valves 20 and 26 are switched to the normal cycle side, and the primary refrigerant compressor 5, the secondary refrigerant compressor 9 and the cooling fan 13 are operated. .
【００５４】一次冷媒用圧縮機５から圧送された一次冷
媒ｘは、図４に実線矢印で示すように、四路切換弁２０
を経て一次冷媒用凝縮器６に供給され、そこで凝縮液化
された後、逆止弁２２を経て一次冷媒用減圧機構７で減
圧され、その後一次冷媒用蒸発器８で蒸発気化され、四
路切換弁２０を経て一次冷媒用圧縮機５へ還流される。The primary refrigerant x pressure-fed from the primary refrigerant compressor 5 is supplied to the four-way switching valve 20 as shown by a solid line arrow in FIG.
Is supplied to the primary refrigerant condenser 6, where it is condensed and liquefied. Then, it is depressurized by the primary refrigerant decompression mechanism 7 through the check valve 22, then is vaporized and vaporized by the primary refrigerant evaporator 8, and is switched in four ways. The refrigerant is returned to the primary refrigerant compressor 5 through the valve 20.
【００５５】一方、二次冷媒用圧縮機９から圧送された
二次冷媒ｙは、図４に実線矢印で示すように、四路切換
弁２６を経て二次冷媒用凝縮器１０に供給され、そこで
前記一次冷媒用蒸発器８との熱交換により凝縮液化さ
れ、逆止弁２９を経た後二次冷媒用減圧機構１１で減圧
され、その後二次冷媒用蒸発器１２で蒸発気化され、四
路切換弁２６を経て二次冷媒用圧縮機９へ還流される。
従って、一次冷媒用蒸発器８との熱交換により低温化さ
れた二次冷媒ｙが二次冷媒用蒸発器１２において蒸発気
化することにより、二次冷媒用蒸発器１２による冷却作
用が大きく向上することとなる。On the other hand, the secondary refrigerant y pressure-fed from the secondary refrigerant compressor 9 is supplied to the secondary refrigerant condenser 10 through the four-way switching valve 26 as shown by the solid arrow in FIG. Then, it is condensed and liquefied by heat exchange with the primary refrigerant evaporator 8, passes through a check valve 29, is decompressed by the secondary refrigerant depressurizing mechanism 11, and is then evaporated and vaporized by the secondary refrigerant evaporator 12, and is subjected to four-way The refrigerant is returned to the secondary refrigerant compressor 9 via the switching valve 26.
Therefore, the secondary refrigerant y whose temperature has been lowered by heat exchange with the primary refrigerant evaporator 8 is evaporated and vaporized in the secondary refrigerant evaporator 12, so that the cooling effect of the secondary refrigerant evaporator 12 is greatly improved. It will be.
【００５６】（ＩＩ） 除霜運転時 この時、四路切換弁２０，２６は逆サイクル側に切り換
えられ、一次冷媒用圧縮機５、二次冷媒用圧縮機９およ
び冷却ファン１３は運転されている。(II) At the time of defrosting operation At this time, the four-way switching valves 20 and 26 are switched to the reverse cycle side, and the primary refrigerant compressor 5, the secondary refrigerant compressor 9 and the cooling fan 13 are operated. I have.
【００５７】一次冷媒用圧縮機５から吐出される高温の
ガス冷媒（即ち、ホットガス）ｘは、図４に点線で示す
ように、四路切換弁２０を経て一次冷媒用蒸発器８に供
給され、逆止弁３５および減圧機構２３を経て蒸発器と
して作用している一次冷媒用凝縮器６へ供給され、そこ
で蒸発気化された後に四路切換弁２０を経て一次冷媒用
圧縮機５へ還流されることとなる。The high-temperature gas refrigerant (ie, hot gas) x discharged from the primary refrigerant compressor 5 is supplied to the primary refrigerant evaporator 8 through the four-way switching valve 20, as shown by the dotted line in FIG. The refrigerant is supplied to the primary refrigerant condenser 6 acting as an evaporator via the check valve 35 and the pressure reducing mechanism 23, and is evaporated and vaporized there, and then returned to the primary refrigerant compressor 5 via the four-way switching valve 20. Will be done.
【００５８】一方、二次冷媒用圧縮機９から吐出される
高温のガス冷媒（即ち、ホットガス）ｘは、図４に点線
で示すように、四路切換弁２６を経て二次冷媒用蒸発器
１２へ供給され、二次冷媒用蒸発器１２の着霜を融霜し
た後、逆止弁２８および減圧機構３０を経て蒸発器とし
て作用している二次冷媒用凝縮器１０に供給され、そこ
で一次冷媒用蒸発器８に供給されるホットガスｘと熱交
換して蒸発気化された後に四路切換弁２６を経て二次冷
媒用圧縮機９へ還流されることとなる。従って、除霜用
熱源としては、一次冷媒用圧縮機５および二次冷媒用圧
縮機９の仕事量と、一次冷媒用凝縮器６と熱交換する媒
体である外気の保有する熱とが利用されることとなるた
め、除霜能力が大きく向上することとなる。On the other hand, the high-temperature gas refrigerant (ie, hot gas) x discharged from the secondary refrigerant compressor 9 passes through the four-way switching valve 26 as shown by the dotted line in FIG. After being supplied to the evaporator 12 and thawing the frost on the secondary refrigerant evaporator 12, the secondary refrigerant is supplied to the secondary refrigerant condenser 10 acting as an evaporator via the check valve 28 and the pressure reducing mechanism 30, Then, the heat is exchanged with the hot gas x supplied to the primary refrigerant evaporator 8 to evaporate and then return to the secondary refrigerant compressor 9 via the four-way switching valve 26. Therefore, as the defrosting heat source, the work of the primary refrigerant compressor 5 and the secondary refrigerant compressor 9 and the heat held by the outside air, which is a medium that exchanges heat with the primary refrigerant condenser 6, are used. Therefore, the defrosting ability is greatly improved.
【００５９】なお、ショーケース用冷凍装置における蒸
発器の場合、フィンピッチが比較的大きい熱交換器が使
用されているため、本実施の形態におけるように、高い
除霜能力で短時間で除霜を行っても、伝熱管周りの融霜
だけで着霜が落下するので、着霜が残るということはな
い。しかも、ショーケースの場合、食品等が陳列されて
いるため、除霜時間は短い方が望ましいという要求も満
たすことができる。In the case of the evaporator in the showcase refrigeration system, a heat exchanger having a relatively large fin pitch is used. However, since frost drops only due to the frost around the heat transfer tubes, frost does not remain. In addition, in the case of a showcase, since food and the like are displayed, it is possible to satisfy the requirement that a shorter defrosting time is desirable.
【００６０】また、電気ヒータを用いる除霜方法ではな
く、冷媒により搬送される熱により除霜を行うこととな
っているため、ランニングコストが高くなることもな
く、定期的なメンテナンスも不必要となる。In addition, since the defrosting is performed not by the defrosting method using the electric heater but by the heat carried by the refrigerant, the running cost is not increased and the periodic maintenance is unnecessary. Become.
【００６１】上記実施の形態においては、二元冷凍装置
をショーケース用冷凍装置として使用した場合について
説明したが、本願発明の二元冷凍装置は、その他の用と
にも用いることができる。In the above embodiment, the case where the dual refrigerating apparatus is used as a showcase refrigerating apparatus has been described, but the dual refrigerating apparatus of the present invention can be used for other purposes.
【００６２】[0062]
【発明の効果】本願発明の第１の基本構成（請求項１の
発明）によれば、一次冷媒ｘを圧縮する一次冷媒用圧縮
機５、一次冷媒ｘを凝縮液化する一次冷媒用凝縮器６、
一次冷媒ｘを減圧する一次冷媒用減圧機構７および一次
冷媒ｘを蒸発気化させる一次冷媒用蒸発器８を冷媒配管
１６を介して順次接続してなる高温側冷凍サイクルＡ
と、二次冷媒ｙを圧縮する二次冷媒用圧縮機９、前記一
次冷媒用蒸発器８との熱交換により二次冷媒ｙを凝縮液
化する二次冷媒用凝縮器１０、二次冷媒ｙを減圧する二
次冷媒用減圧機構１１および二次冷媒ｙを蒸発気化させ
る二次冷媒用蒸発器１２を冷媒配管１７を介して順次接
続してなる低温側冷凍サイクルＢとを備えた二元冷凍装
置において、前記高温側冷凍ユニットＡを逆サイクル運
転が可能に構成するとともに、前記高温側冷凍サイクル
Ａの逆サイクル運転時において前記一次冷媒用圧縮機５
から吐出されるガス冷媒ｘを前記二次冷媒用蒸発器１２
を経て前記一次冷媒用減圧機構７の下流側へバイパスさ
せる除霜用バイパス回路１８を設けて、除霜運転時にお
いては、一次冷媒用圧縮機５から吐出される高温のガス
冷媒（即ち、ホットガス）ｘが、除霜用バイパス回路１
８を介して二次冷媒用蒸発器１２へ供給され、二次冷媒
用蒸発器１２の着霜を融霜した後、蒸発器として作用す
る一次冷媒用凝縮器６で蒸発気化された後に一次冷媒用
圧縮機５へ還流されるようにしたので、除霜用熱源とし
て、一次冷媒用圧縮機５の仕事量と、一次冷媒用凝縮器
６と熱交換する媒体（例えば、外気）の保有する熱とを
利用できることとなり、除霜能力が大きく向上し、除霜
時間を短縮することができるという優れた効果がある。
しかも、電気ヒータを用いる除霜方法ではなく、冷媒に
より搬送される熱により除霜を行うこととなっているた
め、ランニングコストが高くなることもなく、定期的な
メンテナンスも不必要となるという効果もある。According to the first basic configuration of the present invention (the invention of claim 1), the primary refrigerant compressor 5 for compressing the primary refrigerant x, and the primary refrigerant condenser 6 for condensing and liquefying the primary refrigerant x. ,
A high temperature side refrigeration cycle A in which a primary refrigerant decompression mechanism 7 for decompressing the primary refrigerant x and a primary refrigerant evaporator 8 for evaporating and evaporating the primary refrigerant x are sequentially connected via a refrigerant pipe 16.
And a secondary refrigerant compressor 9 for compressing the secondary refrigerant y, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, and a secondary refrigerant y. A binary refrigeration system including a low-temperature side refrigeration cycle B in which a secondary refrigerant decompression mechanism 11 for reducing pressure and a secondary refrigerant evaporator 12 for evaporating and evaporating the secondary refrigerant y are sequentially connected via a refrigerant pipe 17. , The high-temperature side refrigeration unit A is configured to be capable of reverse cycle operation, and the primary refrigerant compressor 5
The refrigerant gas x discharged from the secondary refrigerant evaporator 12
And a bypass circuit 18 for defrosting is provided for bypassing to the downstream side of the primary refrigerant decompression mechanism 7 through the above. In the defrosting operation, a high-temperature gas refrigerant discharged from the primary refrigerant compressor 5 (that is, hot gas refrigerant) Gas) x is the defrost bypass circuit 1
After being supplied to the secondary refrigerant evaporator 12 through the secondary evaporator 8 and thawing the frost of the secondary refrigerant evaporator 12, the primary refrigerant is evaporated and vaporized by the primary refrigerant condenser 6 acting as an evaporator. As a heat source for defrosting, the work amount of the primary refrigerant compressor 5 and the heat retained in a medium (for example, outside air) that exchanges heat with the primary refrigerant condenser 6 are used as heat sources for defrosting. Can be used, and there is an excellent effect that the defrosting ability is greatly improved and the defrosting time can be shortened.
Moreover, since the defrosting is performed by the heat carried by the refrigerant instead of the defrosting method using the electric heater, the running cost is not increased, and the periodic maintenance is unnecessary. There is also.
【００６３】本願発明の第２の基本構成（請求項２の発
明）によれば、一次冷媒ｘを圧縮する一次冷媒用圧縮機
５、一次冷媒ｘを凝縮液化する一次冷媒用凝縮器６、一
次冷媒ｘを減圧する一次冷媒用減圧機構７および一次冷
媒ｘを蒸発気化させる一次冷媒用蒸発器８を冷媒配管１
６を介して順次接続してなる高温側冷凍サイクルＡと、
二次冷媒ｙを圧縮する二次冷媒用圧縮機９、前記一次冷
媒用蒸発器８との熱交換により二次冷媒ｙを凝縮液化す
る二次冷媒用凝縮器１０、二次冷媒ｙを減圧する二次冷
媒用減圧機構１１および二次冷媒ｙを蒸発気化させる二
次冷媒用蒸発器１２を冷媒配管１７を介して順次接続し
てなる低温側冷凍サイクルＢとを備えた二元冷凍装置に
おいて、前記低温側冷凍サイクルＢを逆サイクル運転が
可能に構成するとともに、前記低温側冷凍サイクルＢの
逆サイクル運転時に前記二次冷媒用圧縮機９に還流する
液冷媒ｙを蒸発気化させる空冷熱交換器１９を付設し
て、除霜運転時においては、二次冷媒用圧縮機９から吐
出された高温のガス冷媒（即ち、ホットガス）ｙが、二
次冷媒用蒸発器１２に供給され、二次冷媒用蒸発器１２
の着霜を融霜した後、空冷熱交換器１９で蒸発気化され
た後に二次冷媒用圧縮機９へ還流されるようにしたの
で、除霜用熱源として、二次冷媒用圧縮機９の仕事量
と、空冷熱交換器１９と熱交換する媒体（例えば、室内
空気）の保有する熱とを利用できることとなり、除霜能
力が大きく向上し、除霜時間を短縮することができると
いう優れた効果がある。しかも、電気ヒータを用いる除
霜方法ではなく、冷媒により搬送される熱により除霜を
行うこととなっているため、ランニングコストが高くな
ることもなく、定期的なメンテナンスも不必要となると
いう効果もある。According to the second basic configuration of the present invention (the invention of claim 2), the primary refrigerant compressor 5 for compressing the primary refrigerant x, the primary refrigerant condenser 6 for condensing and liquefying the primary refrigerant x, the primary refrigerant The refrigerant pipe 1 includes a primary refrigerant decompression mechanism 7 for decompressing the refrigerant x and a primary refrigerant evaporator 8 for evaporating the primary refrigerant x.
6, a high-temperature refrigeration cycle A sequentially connected through
A secondary refrigerant compressor 9 for compressing the secondary refrigerant y, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, and depressurizing the secondary refrigerant y. In a binary refrigeration apparatus including a low-temperature side refrigeration cycle B in which a secondary refrigerant decompression mechanism 11 and a secondary refrigerant evaporator 12 for evaporating and evaporating the secondary refrigerant y are sequentially connected via a refrigerant pipe 17, An air-cooled heat exchanger configured to enable the low-temperature side refrigeration cycle B to perform a reverse cycle operation and evaporate and evaporate the liquid refrigerant y flowing back to the secondary refrigerant compressor 9 during the reverse cycle operation of the low-temperature side refrigeration cycle B. At the time of the defrosting operation, a high-temperature gas refrigerant (that is, hot gas) y discharged from the secondary refrigerant compressor 9 is supplied to the secondary refrigerant evaporator 12 and the secondary refrigerant evaporator 12 is attached thereto. Evaporator for refrigerant 12
After the frost is melted, the refrigerant is evaporated and vaporized in the air-cooled heat exchanger 19 and then returned to the secondary refrigerant compressor 9, so that the secondary refrigerant compressor 9 is used as a defrosting heat source. The work amount and the heat held by the medium (for example, indoor air) that exchanges heat with the air-cooling heat exchanger 19 can be used, and the defrosting ability is greatly improved and the defrosting time can be shortened. effective. Moreover, since the defrosting is performed by the heat carried by the refrigerant instead of the defrosting method using the electric heater, the running cost is not increased, and the periodic maintenance is unnecessary. There is also.
【００６４】請求項３の発明におけるように、前記空冷
熱交換器１９を、前記高温側冷凍サイクルＡにおける一
次冷媒用凝縮器６で兼用した場合、除霜運転時において
二次冷媒用凝縮器１２で凝縮液化された二次冷媒ｙを一
次冷媒用凝縮器６で蒸発気化できることとなり、部品点
数の低減およびコスト低減に寄与できる。なお、この場
合、外気の保有するする熱が除霜用熱源として利用され
ることとなる。When the air-cooling heat exchanger 19 is also used as the primary refrigerant condenser 6 in the high-temperature side refrigeration cycle A as in the third aspect of the present invention, the secondary refrigerant condenser 12 is used during the defrosting operation. Thus, the secondary refrigerant y condensed and liquefied can be evaporated and vaporized in the primary refrigerant condenser 6, which can contribute to a reduction in the number of parts and cost. In this case, the heat held by the outside air is used as a heat source for defrosting.
【００６５】本願発明の第３の基本構成（請求項４の発
明）によれば、一次冷媒ｘを圧縮する一次冷媒用圧縮機
５、一次冷媒ｘを凝縮液化する一次冷媒用凝縮器６、一
次冷媒ｘを減圧する一次冷媒用減圧機構７および一次冷
媒ｘを蒸発気化させる一次冷媒用蒸発器８を冷媒配管１
６を介して順次接続してなる高温側冷凍サイクルＡと、
二次冷媒ｙを圧縮する二次冷媒用圧縮機９、前記一次冷
媒用蒸発器８との熱交換により二次冷媒ｙを凝縮液化す
る二次冷媒用凝縮器１０、二次冷媒ｙを減圧する二次冷
媒用減圧機構１１および二次冷媒ｙを蒸発気化させる二
次冷媒用蒸発器１２を冷媒配管１７を介して順次接続し
てなる低温側冷凍サイクルＢとを備えた二元冷凍装置に
おいて、前記高温側冷凍サイクルＡおよび低温側冷凍サ
イクルＢを逆サイクル運転が可能に構成して、除霜運転
時においては、二次冷媒用圧縮機９から吐出される高温
のガス冷媒（即ち、ホットガス）ｙが、二次冷媒用蒸発
器１２に供給され、二次冷媒用蒸発器１２の着霜を融霜
した後、蒸発器として作用している二次冷媒用凝縮器１
０で蒸発気化された後に二次冷媒用圧縮機９へ還流され
るとともに、一次冷媒用圧縮機５から吐出された高温の
ガス冷媒（即ち、ホットガス）ｘが、一次冷媒用蒸発器
８に供給され、二次冷媒用凝縮器１０での液冷媒ｙの蒸
発気化を助けて自身凝縮液化された後、蒸発器として作
用している一次冷媒用凝縮器６で蒸発気化された後に一
次冷媒用圧縮機５へ還流されるようにしたので、除霜用
熱源として、一次冷媒用圧縮機５および二次冷媒用圧縮
機９の仕事量と、一次冷媒用凝縮器６と熱交換する媒体
（例えば、外気）の保有する熱とを利用できることとな
り、除霜能力が大きく向上し、除霜時間を短縮すること
ができるという優れた効果がある。しかも、電気ヒータ
を用いる除霜方法ではなく、冷媒により搬送される熱に
より除霜を行うこととなっているため、ランニングコス
トが高くなることもなく、定期的なメンテナンスも不必
要となるという効果もある。According to the third basic configuration of the present invention (the invention of claim 4), the primary refrigerant compressor 5 for compressing the primary refrigerant x, the primary refrigerant condenser 6 for condensing and liquefying the primary refrigerant x, the primary refrigerant The refrigerant pipe 1 includes a primary refrigerant decompression mechanism 7 for decompressing the refrigerant x and a primary refrigerant evaporator 8 for evaporating the primary refrigerant x.
6, a high-temperature refrigeration cycle A sequentially connected through
A secondary refrigerant compressor 9 for compressing the secondary refrigerant y, a secondary refrigerant condenser 10 for condensing and liquefying the secondary refrigerant y by heat exchange with the primary refrigerant evaporator 8, and depressurizing the secondary refrigerant y. In a binary refrigeration apparatus including a low-temperature side refrigeration cycle B in which a secondary refrigerant decompression mechanism 11 and a secondary refrigerant evaporator 12 for evaporating and evaporating the secondary refrigerant y are sequentially connected via a refrigerant pipe 17, The high-temperature side refrigeration cycle A and the low-temperature side refrigeration cycle B are configured to be capable of performing a reverse cycle operation. During the defrosting operation, a high-temperature gas refrigerant (that is, hot gas) discharged from the secondary refrigerant compressor 9 is used. ) Y is supplied to the secondary refrigerant evaporator 12, and after melting the frost of the secondary refrigerant evaporator 12, the secondary refrigerant condenser 1 acting as an evaporator
After being vaporized and vaporized at 0, the refrigerant is returned to the secondary refrigerant compressor 9 and the high-temperature gas refrigerant (that is, hot gas) x discharged from the primary refrigerant compressor 5 is supplied to the primary refrigerant evaporator 8. After being supplied and condensed and liquefied by assisting the evaporation and vaporization of the liquid refrigerant y in the secondary refrigerant condenser 10, the liquid refrigerant y is evaporated and vaporized in the primary refrigerant condenser 6 acting as an evaporator, and then used for the primary refrigerant. Since the refrigerant is returned to the compressor 5, as a defrosting heat source, the work amounts of the primary refrigerant compressor 5 and the secondary refrigerant compressor 9 and a medium that exchanges heat with the primary refrigerant condenser 6 (for example, , Outside air) can be used, and there is an excellent effect that the defrosting ability is greatly improved and the defrosting time can be shortened. Moreover, since the defrosting is performed by the heat carried by the refrigerant instead of the defrosting method using the electric heater, the running cost is not increased, and the periodic maintenance is unnecessary. There is also.
【図１】本願発明の第１の実施の形態にかかる二元冷凍
装置の冷媒回路図である。FIG. 1 is a refrigerant circuit diagram of a binary refrigeration apparatus according to a first embodiment of the present invention.
【図２】本願発明の第２の実施の形態にかかる二元冷凍
装置の冷媒回路図である。FIG. 2 is a refrigerant circuit diagram of a binary refrigeration apparatus according to a second embodiment of the present invention.
【図３】本願発明の第３の実施の形態にかかる二元冷凍
装置の冷媒回路図である。FIG. 3 is a refrigerant circuit diagram of a binary refrigeration apparatus according to a third embodiment of the present invention.
【図４】本願発明の第４の実施の形態にかかる二元冷凍
装置の冷媒回路図である。FIG. 4 is a refrigerant circuit diagram of a binary refrigeration apparatus according to a fourth embodiment of the present invention.
【図５】従来の二元冷凍装置の冷媒回路図である。FIG. 5 is a refrigerant circuit diagram of a conventional binary refrigeration apparatus.
５は一次冷媒用圧縮機、６は一次冷媒用凝縮器、７は一
次冷媒用減圧機構、８は一次冷媒用蒸発器、９は二次冷
媒用圧縮機、１０は二次冷媒用凝縮器、１１は二次冷媒
用減圧機構、１２は二次冷媒用蒸発器、１６，１７は冷
媒配管、１８は除霜用バイパス回路、１９は空冷熱交換
器、２０，２６は四路切換弁、Ａは高温側冷凍サイク
ル、Ｂは低温側冷凍サイクル、ｘは一次冷媒、ｙは二次
冷媒。5 is a primary refrigerant compressor, 6 is a primary refrigerant condenser, 7 is a primary refrigerant decompression mechanism, 8 is a primary refrigerant evaporator, 9 is a secondary refrigerant compressor, 10 is a secondary refrigerant condenser, 11 is a pressure reducing mechanism for a secondary refrigerant, 12 is an evaporator for a secondary refrigerant, 16 and 17 are refrigerant pipes, 18 is a defrost bypass circuit, 19 is an air-cooled heat exchanger, 20 and 26 are four-way switching valves, and A Is a high-temperature side refrigeration cycle, B is a low-temperature side refrigeration cycle, x is a primary refrigerant, and y is a secondary refrigerant.
Claims (4)
縮機（５）、一次冷媒（ｘ）を凝縮液化する一次冷媒用
凝縮器（６）、一次冷媒（ｘ）を減圧する一次冷媒用減
圧機構（７）および一次冷媒（ｘ）を蒸発気化させる一
次冷媒用蒸発器（８）を冷媒配管（１６）を介して順次
接続してなる高温側冷凍サイクル（Ａ）と、二次冷媒
（ｙ）を圧縮する二次冷媒用圧縮機（９）、前記一次冷
媒用蒸発器（８）との熱交換により二次冷媒（ｙ）を凝
縮液化する二次冷媒用凝縮器（１０）、二次冷媒（ｙ）
を減圧する二次冷媒用減圧機構（１１）および二次冷媒
（ｙ）を蒸発気化させる二次冷媒用蒸発器（１２）を冷
媒配管（１７）を介して順次接続してなる低温側冷凍サ
イクル（Ｂ）とを備えた二元冷凍装置であって、前記高
温側冷凍ユニット（Ａ）を逆サイクル運転が可能に構成
するとともに、前記高温側冷凍サイクル（Ａ）の逆サイ
クル運転時において前記一次冷媒用圧縮機（５）から吐
出されるガス冷媒（ｘ）を前記二次冷媒用蒸発器（１
０）を経て前記一次冷媒用減圧機構（７）の下流側へバ
イパスさせる除霜用バイパス回路（１８）を設けたこと
を特徴とする二元冷凍装置。1. A primary refrigerant compressor (5) for compressing a primary refrigerant (x), a primary refrigerant condenser (6) for condensing and liquefying the primary refrigerant (x), and a primary refrigerant for decompressing the primary refrigerant (x). High-temperature refrigeration cycle (A) in which a pressure reducing mechanism (7) for use and a primary refrigerant evaporator (8) for evaporating and evaporating the primary refrigerant (x) are sequentially connected via a refrigerant pipe (16); A secondary refrigerant compressor (9) for compressing (y), a secondary refrigerant condenser (10) for condensing and liquefying the secondary refrigerant (y) by heat exchange with the primary refrigerant evaporator (8), Secondary refrigerant (y)
Low-temperature refrigeration cycle comprising a secondary refrigerant evaporator (12) for evaporating and evaporating the secondary refrigerant (y) and a secondary refrigerant evaporator (12) sequentially connected via a refrigerant pipe (17). (B), wherein the high-temperature refrigeration unit (A) is configured to be capable of reverse cycle operation, and the primary refrigeration unit (A) is configured to perform the primary cycle during reverse cycle operation of the high-temperature refrigeration cycle (A). The gas refrigerant (x) discharged from the refrigerant compressor (5) is supplied to the secondary refrigerant evaporator (1).
A binary refrigeration system comprising a defrosting bypass circuit (18) that bypasses the downstream side of the primary refrigerant pressure reducing mechanism (7) via 0).
縮機（５）、一次冷媒（ｘ）を凝縮液化する一次冷媒用
凝縮器（６）、一次冷媒（ｘ）を減圧する一次冷媒用減
圧機構（７）および一次冷媒（ｘ）を蒸発気化させる一
次冷媒用蒸発器（８）を冷媒配管（１６）を介して順次
接続してなる高温側冷凍サイクル（Ａ）と、二次冷媒
（ｙ）を圧縮する二次冷媒用圧縮機（９）、前記一次冷
媒用蒸発器（８）との熱交換により二次冷媒（ｙ）を凝
縮液化する二次冷媒用凝縮器（１０）、二次冷媒（ｙ）
を減圧する二次冷媒用減圧機構（１１）および二次冷媒
（ｙ）を蒸発気化させる二次冷媒用蒸発器（１２）を冷
媒配管（１７）を介して順次接続してなる低温側冷凍サ
イクル（Ｂ）とを備えた二元冷凍装置であって、前記低
温側冷凍サイクル（Ｂ）を逆サイクル運転が可能に構成
するとともに、前記低温側冷凍サイクル（Ｂ）の逆サイ
クル運転時に前記二次冷媒用圧縮機（９）に還流する液
冷媒（ｙ）を蒸発気化させる空冷熱交換器（１９）を付
設したことを特徴とする二元冷凍装置。2. A primary refrigerant compressor (5) for compressing a primary refrigerant (x), a primary refrigerant condenser (6) for condensing and liquefying the primary refrigerant (x), and a primary refrigerant for decompressing the primary refrigerant (x). High-temperature refrigeration cycle (A) in which a pressure reducing mechanism (7) for use and a primary refrigerant evaporator (8) for evaporating and evaporating the primary refrigerant (x) are sequentially connected via a refrigerant pipe (16); A secondary refrigerant compressor (9) for compressing (y), a secondary refrigerant condenser (10) for condensing and liquefying the secondary refrigerant (y) by heat exchange with the primary refrigerant evaporator (8), Secondary refrigerant (y)
Low-temperature refrigeration cycle comprising a secondary refrigerant evaporator (12) for evaporating and evaporating the secondary refrigerant (y) and a secondary refrigerant evaporator (12) sequentially connected via a refrigerant pipe (17). (B), wherein the low-temperature refrigeration cycle (B) is configured to be capable of performing a reverse cycle operation, and the secondary refrigeration cycle (B) is configured to perform the reverse cycle operation during the reverse cycle operation of the low-temperature refrigeration cycle (B). A binary refrigeration system comprising an air-cooled heat exchanger (19) for evaporating and evaporating a liquid refrigerant (y) flowing back to a refrigerant compressor (9).
側冷凍サイクル（Ａ）における一次冷媒用凝縮器（６）
で兼用したことを特徴とする前記請求項２記載の二元冷
凍装置。3. A condenser (6) for a primary refrigerant in the high-temperature side refrigeration cycle (A), wherein the air-cooled heat exchanger (19) is provided.
3. The dual refrigeration apparatus according to claim 2, wherein the dual refrigeration apparatus is also used.
縮機（５）、一次冷媒（ｘ）を凝縮液化する一次冷媒用
凝縮器（６）、一次冷媒（ｘ）を減圧する一次冷媒用減
圧機構（７）および一次冷媒（ｘ）を蒸発気化させる一
次冷媒用蒸発器（８）を冷媒配管（１６）を介して順次
接続してなる高温側冷凍サイクル（Ａ）と、二次冷媒
（ｙ）を圧縮する二次冷媒用圧縮機（９）、前記一次冷
媒用蒸発器（８）との熱交換により二次冷媒（ｙ）を凝
縮液化する二次冷媒用凝縮器（１０）、二次冷媒（ｙ）
を減圧する二次冷媒用減圧機構（１１）および二次冷媒
（ｙ）を蒸発気化させる二次冷媒用蒸発器（１２）を冷
媒配管（１７）を介して順次接続してなる低温側冷凍サ
イクル（Ｂ）とを備えた二元冷凍装置であって、前記高
温側冷凍サイクル（Ａ）および低温側冷凍サイクル
（Ｂ）を逆サイクル運転が可能に構成したことを特徴と
する二元冷凍装置。4. A primary refrigerant compressor (5) for compressing a primary refrigerant (x), a primary refrigerant condenser (6) for condensing and liquefying the primary refrigerant (x), a primary refrigerant for decompressing the primary refrigerant (x). High-temperature refrigeration cycle (A) in which a pressure reducing mechanism (7) for use and a primary refrigerant evaporator (8) for evaporating and evaporating the primary refrigerant (x) are sequentially connected via a refrigerant pipe (16); A secondary refrigerant compressor (9) for compressing (y), a secondary refrigerant condenser (10) for condensing and liquefying the secondary refrigerant (y) by heat exchange with the primary refrigerant evaporator (8), Secondary refrigerant (y)
Low-temperature refrigeration cycle comprising a secondary refrigerant evaporator (12) for evaporating and evaporating the secondary refrigerant (y) and a secondary refrigerant evaporator (12) sequentially connected via a refrigerant pipe (17). (B), wherein the high-temperature side refrigeration cycle (A) and the low-temperature side refrigeration cycle (B) are configured to be capable of reverse cycle operation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP34292297A JPH11173711A (en) | 1997-12-12 | 1997-12-12 | Dual refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP34292297A JPH11173711A (en) | 1997-12-12 | 1997-12-12 | Dual refrigerator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH11173711A true JPH11173711A (en) | 1999-07-02 |
Family
ID=18357564
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP34292297A Pending JPH11173711A (en) | 1997-12-12 | 1997-12-12 | Dual refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH11173711A (en) |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100385432B1 (en) * | 2000-09-19 | 2003-05-27 | 주식회사 케이씨텍 | Surface cleaning aerosol production system |
| US7000414B2 (en) | 2002-08-06 | 2006-02-21 | Samsung Electronics Co., Ltd. | Defrost and refrigerator employing the same |
| WO2007054095A1 (en) * | 2005-11-11 | 2007-05-18 | Johnson Controls Denmark Aps | Defrost system |
| WO2007083559A1 (en) * | 2006-01-17 | 2007-07-26 | Daikin Industries, Ltd. | Refrigeration system |
| KR100796452B1 (en) | 2007-06-20 | 2008-01-22 | 김진수 | Heat pump and demist method |
| WO2010098073A1 (en) * | 2009-02-24 | 2010-09-02 | ダイキン工業株式会社 | Heat pump system |
| JP2011127878A (en) * | 2009-12-21 | 2011-06-30 | Mitsubishi Electric Corp | Hot water heat source machine |
| JP2012112622A (en) * | 2010-11-26 | 2012-06-14 | Mitsubishi Electric Corp | Binary refrigeration device |
| JP2014098551A (en) * | 2014-02-28 | 2014-05-29 | Daikin Ind Ltd | Heat pump system |
| JP2015102541A (en) * | 2013-11-28 | 2015-06-04 | エスペック株式会社 | Environmental test device and cooling system |
| CN106979638A (en) * | 2017-04-28 | 2017-07-25 | 上海理工大学 | Automobile air-conditioning evaporator defroster |
| CN107062688A (en) * | 2017-01-20 | 2017-08-18 | 合肥天鹅制冷科技有限公司 | The cold liquid machine of wide temperature air cooling island |
| CN110030677A (en) * | 2019-04-28 | 2019-07-19 | 广东美的暖通设备有限公司 | Air conditioning control method, device and computer readable storage medium |
| CN114234465A (en) * | 2021-12-27 | 2022-03-25 | 上海理工大学 | High-low temperature environment test box refrigerating system adopting multi-channel evaporator |
-
1997
- 1997-12-12 JP JP34292297A patent/JPH11173711A/en active Pending
Cited By (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100385432B1 (en) * | 2000-09-19 | 2003-05-27 | 주식회사 케이씨텍 | Surface cleaning aerosol production system |
| US7000414B2 (en) | 2002-08-06 | 2006-02-21 | Samsung Electronics Co., Ltd. | Defrost and refrigerator employing the same |
| WO2007054095A1 (en) * | 2005-11-11 | 2007-05-18 | Johnson Controls Denmark Aps | Defrost system |
| WO2007083559A1 (en) * | 2006-01-17 | 2007-07-26 | Daikin Industries, Ltd. | Refrigeration system |
| JP2007192430A (en) * | 2006-01-17 | 2007-08-02 | Daikin Ind Ltd | Refrigerating device |
| KR100796452B1 (en) | 2007-06-20 | 2008-01-22 | 김진수 | Heat pump and demist method |
| US8984901B2 (en) | 2009-02-24 | 2015-03-24 | Daikin Industries, Ltd. | Heat pump system |
| WO2010098073A1 (en) * | 2009-02-24 | 2010-09-02 | ダイキン工業株式会社 | Heat pump system |
| JP2010196951A (en) * | 2009-02-24 | 2010-09-09 | Daikin Ind Ltd | Heat pump system |
| CN102326037A (en) * | 2009-02-24 | 2012-01-18 | 大金工业株式会社 | Heat pump |
| AU2010219037B2 (en) * | 2009-02-24 | 2013-07-11 | Daikin Europe N.V. | Heat pump system |
| JP2011127878A (en) * | 2009-12-21 | 2011-06-30 | Mitsubishi Electric Corp | Hot water heat source machine |
| JP2012112622A (en) * | 2010-11-26 | 2012-06-14 | Mitsubishi Electric Corp | Binary refrigeration device |
| JP2015102541A (en) * | 2013-11-28 | 2015-06-04 | エスペック株式会社 | Environmental test device and cooling system |
| JP2014098551A (en) * | 2014-02-28 | 2014-05-29 | Daikin Ind Ltd | Heat pump system |
| CN107062688A (en) * | 2017-01-20 | 2017-08-18 | 合肥天鹅制冷科技有限公司 | The cold liquid machine of wide temperature air cooling island |
| CN107062688B (en) * | 2017-01-20 | 2023-08-11 | 合肥天鹅制冷科技有限公司 | Wide Wen Kongleng island type liquid cooler |
| CN106979638A (en) * | 2017-04-28 | 2017-07-25 | 上海理工大学 | Automobile air-conditioning evaporator defroster |
| CN110030677A (en) * | 2019-04-28 | 2019-07-19 | 广东美的暖通设备有限公司 | Air conditioning control method, device and computer readable storage medium |
| CN114234465A (en) * | 2021-12-27 | 2022-03-25 | 上海理工大学 | High-low temperature environment test box refrigerating system adopting multi-channel evaporator |
| CN114234465B (en) * | 2021-12-27 | 2023-08-29 | 上海理工大学 | High-low temperature environment test box refrigerating system adopting multichannel evaporator |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4565070A (en) | Apparatus and method for defrosting a heat exchanger in a refrigeration circuit | |
| US6094925A (en) | Crossover warm liquid defrost refrigeration system | |
| JPH11173711A (en) | Dual refrigerator | |
| KR19980017695A (en) | Dropping prevention device of heat pump | |
| WO1999039138A1 (en) | Refrigerating plant | |
| KR100381634B1 (en) | Refrigerator | |
| JPH09318206A (en) | Heat pump type air conditioner | |
| JP2013137123A (en) | Refrigerating apparatus | |
| JPH03117866A (en) | Heat pump type refrigerating cycle | |
| JP4622901B2 (en) | Air conditioner | |
| KR100333814B1 (en) | Dual unit type air conditioner for heating and cooling and defrosting method thereof | |
| JP2002188873A (en) | Refrigerating equipment of air conditioner | |
| JP3254178B2 (en) | Refrigeration circuit with auxiliary evaporator for defrost | |
| JP2962311B1 (en) | Binary refrigeration equipment | |
| JP3781340B2 (en) | Thermal storage refrigeration air conditioner | |
| JP2003004346A (en) | Cooling equipment | |
| JP2646709B2 (en) | Air conditioner | |
| JP3304866B2 (en) | Thermal storage type air conditioner | |
| JPH035680A (en) | Air conditioner | |
| JPH10325641A (en) | Refrigerating device | |
| JP2524382B2 (en) | Air conditioner | |
| JP3008925B2 (en) | Refrigeration equipment | |
| JPH09217972A (en) | Refrigerating device | |
| JP2924460B2 (en) | Air conditioner | |
| JPH0821664A (en) | Refrigerating cycle device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Effective date: 20040824 Free format text: JAPANESE INTERMEDIATE CODE: A621 |
|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20050421 |
|
| A131 | Notification of reasons for refusal |
Effective date: 20050524 Free format text: JAPANESE INTERMEDIATE CODE: A131 |
|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20051018 |