JP3408022B2 - Refrigeration equipment - Google Patents
Refrigeration equipmentInfo
- Publication number
- JP3408022B2 JP3408022B2 JP17027195A JP17027195A JP3408022B2 JP 3408022 B2 JP3408022 B2 JP 3408022B2 JP 17027195 A JP17027195 A JP 17027195A JP 17027195 A JP17027195 A JP 17027195A JP 3408022 B2 JP3408022 B2 JP 3408022B2
- Authority
- JP
- Japan
- Prior art keywords
- refrigeration cycle
- indoor
- cycle
- condenser
- 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.)
- Expired - Fee Related
Links
- 238000005057 refrigeration Methods 0.000 title claims description 86
- 239000012267 brine Substances 0.000 claims description 31
- HPALAKNZSZLMCH-UHFFFAOYSA-M sodium;chloride;hydrate Chemical compound O.[Na+].[Cl-] HPALAKNZSZLMCH-UHFFFAOYSA-M 0.000 claims description 31
- 238000009833 condensation Methods 0.000 claims description 20
- 230000005494 condensation Effects 0.000 claims description 20
- 230000006837 decompression Effects 0.000 claims description 14
- 230000008602 contraction Effects 0.000 claims 1
- 239000003507 refrigerant Substances 0.000 description 51
- 238000005338 heat storage Methods 0.000 description 15
- 238000010276 construction Methods 0.000 description 10
- 230000001105 regulatory effect Effects 0.000 description 10
- 238000001816 cooling Methods 0.000 description 8
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 7
- 238000010586 diagram Methods 0.000 description 5
- 239000010802 sludge Substances 0.000 description 5
- 239000000428 dust Substances 0.000 description 4
- 238000007710 freezing Methods 0.000 description 4
- 230000008014 freezing Effects 0.000 description 4
- 238000009413 insulation Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 238000003466 welding Methods 0.000 description 3
- FAPWRFPIFSIZLT-UHFFFAOYSA-M Sodium chloride Chemical compound [Na+].[Cl-] FAPWRFPIFSIZLT-UHFFFAOYSA-M 0.000 description 2
- 239000002253 acid Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 239000010696 ester oil Substances 0.000 description 2
- 229920005862 polyol Polymers 0.000 description 2
- 150000003077 polyols Chemical class 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
- UXVMQQNJUSDDNG-UHFFFAOYSA-L Calcium chloride Chemical compound [Cl-].[Cl-].[Ca+2] UXVMQQNJUSDDNG-UHFFFAOYSA-L 0.000 description 1
- 239000001110 calcium chloride Substances 0.000 description 1
- 229910001628 calcium chloride Inorganic materials 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000000344 soap Substances 0.000 description 1
- 239000011780 sodium chloride Substances 0.000 description 1
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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/22—Refrigeration systems for supermarkets
Landscapes
- Other Air-Conditioning Systems (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、ＨＦＣ系冷媒あるいは
その混合冷媒を用いる冷凍装置に係り、特に圧縮機、凝
縮器、減圧装置、蒸発器を備えてショーケースや冷凍冷
蔵庫等として用いられるのに好適な冷凍装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerating apparatus using an HFC type refrigerant or a mixed refrigerant thereof, and is particularly used as a showcase or a refrigerator / freezer provided with a compressor, a condenser, a pressure reducing device and an evaporator. The present invention relates to a suitable refrigeration system.
【０００２】[0002]
【従来の技術】図４は従来の一般的な小型の冷凍装置を
示しており、図５は従来の一般的な大型の冷凍装置を示
している。図４に示す小型の冷凍装置は一台の室外機１
０１に一台の室内機１００をつないだものであり、室内
機１００は蒸発器１０３と膨張弁１０４を有し、室外機
１０１は凝縮器１０５と圧縮機１０６を有する。一方、
図５に示す大型の冷凍装置は一台の室外機２０１に二台
の室内機２００，２００をつないだものであり、室内機
２００は、蒸発器２０３と膨張弁２０４を有し、室外機
２０１は凝縮器２０５と圧縮機２０６を有する。この種
の従来の冷凍装置では施工現場において長い配管を用い
て室外機と室内機とをつないだ後に回路内に冷媒を充填
する。2. Description of the Related Art FIG. 4 shows a conventional general small refrigerating apparatus, and FIG. 5 shows a conventional general large refrigerating apparatus. The small refrigerator shown in FIG. 4 is a single outdoor unit 1.
01 is connected to one indoor unit 100. The indoor unit 100 has an evaporator 103 and an expansion valve 104, and the outdoor unit 101 has a condenser 105 and a compressor 106. on the other hand,
The large-scale refrigerating apparatus shown in FIG. 5 is one outdoor unit 201 connected with two indoor units 200, 200, and the indoor unit 200 has an evaporator 203 and an expansion valve 204, and the outdoor unit 201. Has a condenser 205 and a compressor 206. In this type of conventional refrigeration system, a long pipe is used at the construction site to connect the outdoor unit and the indoor unit, and then the circuit is filled with the refrigerant.
【０００３】[0003]
【発明が解決しようとする課題】しかしながら、近年で
はこの種の冷凍装置の冷媒としてＨＦＣ系の単一冷媒や
その非共沸混合冷媒が用いられる。ＨＦＣ系冷媒を冷凍
装置の冷媒として用いる際には、圧縮機の潤滑油として
ポリオールエステル油が用いられる。施工現場において
は、上記のように室外機と室内機とをつないだ後に、Ｈ
ＦＣ系の単一冷媒やその非共沸混合冷媒を充填すると、
長い配管内に残った空気又は水分がポリオールエステル
油と反応し、加水分解し、冷媒の分解や酸の発生、金属
石鹸を生成してスラッジになり、このスラッジが熱交換
器に詰まる等の問題がある。また、ＨＦＣ系冷媒を用い
る際には配管内のゴミの管理が困難になるという問題が
ある。更に、図４及び図５に示すような従来の冷凍装置
では、ＨＦＣ系冷媒の圧縮比が高くなり過ぎるので、耐
久性や信頼性に劣るという問題がある。However, in recent years, an HFC type single refrigerant or a non-azeotropic mixed refrigerant thereof has been used as a refrigerant for this type of refrigerating apparatus. When the HFC-based refrigerant is used as the refrigerant of the refrigeration system, polyol ester oil is used as the lubricating oil of the compressor. At the construction site, after connecting the outdoor unit and the indoor unit as described above,
When FC single refrigerant or its non-azeotropic mixed refrigerant is filled,
The air or water remaining in the long pipe reacts with the polyol ester oil, hydrolyzes, decomposes the refrigerant, generates acid, produces metallic soap, and becomes sludge, which causes clogging of the heat exchanger. There is. Further, when using the HFC refrigerant, there is a problem that it becomes difficult to manage dust in the pipe. Further, in the conventional refrigerating apparatus as shown in FIGS. 4 and 5, the compression ratio of the HFC refrigerant is too high, which causes a problem of poor durability and reliability.
【０００４】そこで、本発明の目的は、上述した従来の
技術が有する問題点を解消し、水分管理や、ゴミ管理等
をあまり厳格に行わなくても、室外機と室内機とを現場
で簡単に施工することができ、しかも、従来のものに比
べて耐久性や信頼性に優れる冷凍装置を提供することに
ある。Therefore, an object of the present invention is to solve the problems of the above-mentioned conventional techniques, and to simplify the outdoor unit and the indoor unit on site without strict management of water content and dust. Another object of the present invention is to provide a refrigerating apparatus which can be installed on a vehicle and which is superior in durability and reliability to conventional ones.
【０００５】[0005]
【課題を解決するための手段】請求項１に記載の発明
は、圧縮機、凝縮器、減圧装置、蒸発器をつないだ室内
側冷凍サイクルと、室外側冷凍サイクルの蒸発器と前記
室内側冷凍サイクルの凝縮器とをつないだ熱搬送サイク
ルと、この熱搬送サイクルに設けられ、ブラインを循環
させる循環ポンプと、前記熱搬送サイクルのブラインの
温度を室温に近づけるために、前記室外側冷凍サイクル
に付加されて、前記室外側冷凍サイクルの圧縮機の容量
あるいは前記循環ポンプの容量を制御する容量制御手段
と、を備えるものである。According to a first aspect of the present invention, there is provided an indoor refrigeration cycle in which a compressor , a condenser, a pressure reducing device, and an evaporator are connected, an outdoor refrigeration cycle evaporator, and the indoor refrigeration cycle. A heat transfer cycle that connects to the condenser of the cycle, and this heat transfer cycle is provided to circulate brine
Of the circulating pump and brine of the heat transfer cycle
In order to bring the temperature close to room temperature, the outdoor refrigeration cycle
In addition to the capacity of the compressor of the outdoor refrigeration cycle
Alternatively, capacity control means for controlling the capacity of the circulation pump
And are provided.
【０００６】請求項２に記載の発明は、圧縮機、凝縮
器、減圧装置、蒸発器をつないだ室内側冷凍サイクル
と、室外側冷凍サイクルの蒸発器と前記室内側冷凍サイ
クルの凝縮器とをつないだ熱搬送サイクルと、前記室内
側冷凍サイクルの凝縮器の凝縮温度あるいは凝縮圧力に
応じて熱搬送サイクルの流量を調整する調整手段と、を
備えるものである。The invention described in claim 2 is a compressor and a condenser.
Indoor refrigeration cycle with a refrigerator, decompressor and evaporator
And the evaporator of the outdoor refrigeration cycle and the indoor refrigeration cycle.
Heat transfer cycle that connects the condenser of the
The condensation temperature or pressure of the condenser of the side refrigeration cycle
Adjusting means for adjusting the flow rate of the heat transfer cycle accordingly .
【０００７】[0007]
【０００８】[0008]
【０００９】[0009]
【００１０】[0010]
【作用】請求項１記載の発明によれば、現場施工する場
合に、室外側冷凍サイクルの蒸発器と室内側冷凍サイク
ルの凝縮器とを熱搬送サイクルで連結し、この熱搬送サ
イクルにはブラインを充填するだけなので、現場での冷
媒の充填は不要になり、現場施工の際に、水分管理やゴ
ミの管理が不要となり、施工が簡単になるとともに、ス
ラッジが熱交換器の冷媒管に詰まるという問題を解消す
ることができる。しかも現場溶接等による品質低下が防
止できる。According to the first aspect of the present invention, in the case of site construction, the evaporator of the outdoor refrigeration cycle and the condenser of the indoor refrigeration cycle are connected by the heat transfer cycle, and the brine is connected to this heat transfer cycle. Since it is only filled with water, it is not necessary to fill the refrigerant on site, and water management and dust management are not required at the time of on-site construction, which simplifies the construction and clogging the sludge of the heat exchanger with refrigerant pipes. The problem can be solved. Moreover, it is possible to prevent quality deterioration due to field welding or the like.
【００１１】更に、熱搬送サイクルのブラインの温度を
室温に近づけるために、容量制御手段が室内側冷凍サイ
クルの圧縮機の容量あるいは熱搬送サイクルのポンプの
容量を制御するので、室外側冷凍サイクルの蒸発器で冷
却されたブラインが室温以上の温度に制御され、結露や
氷結等がなくなり、現場での断熱工事等が不要になる。 Furthermore , in order to bring the temperature of the brine in the heat transfer cycle closer to room temperature, the capacity control means controls the capacity of the compressor in the indoor side refrigeration cycle or the capacity of the pump in the heat transfer cycle. The brine cooled by the evaporator is controlled to a temperature above room temperature, eliminating condensation and icing, thus eliminating the need for on-site insulation work.
【００１２】請求項２に記載の発明によれば、現場施工
する場合に、室外側冷凍サイクルの蒸発器と室内側冷凍
サイクルの凝縮器とを熱搬送サイクルで連結し、この熱
搬送サイクルにはブラインを充填するだけなので、現場
での冷媒の充填は不要になり、現場施工の際に、水分管
理やゴミの管理が不要となり、施工が簡単になるととも
に、スラッジが熱交換器の冷媒管に詰まるという問題を
解消することができる。しかも現場溶接等による品質低
下が防止できる。更に、調整手段は、室内側冷凍サイク
ルの凝縮器のブラインの流量を、凝縮温度あるいは凝縮
圧力に応じて調整するので、一定の凝縮温度が得られ
る。According to the invention described in claim 2 , construction on site
When the outdoor refrigeration cycle evaporator and indoor refrigeration
This cycle is connected to the condenser of the cycle by a heat transfer cycle,
Since only the brine is filled in the transport cycle,
It is no longer necessary to fill the refrigerant in the
There is no need to manage waste and waste, which simplifies construction.
The problem of sludge clogging the refrigerant tubes of the heat exchanger.
It can be resolved. Moreover, poor quality due to on-site welding, etc.
The bottom can be prevented. Furthermore , since the adjusting means adjusts the flow rate of the brine in the condenser of the indoor refrigeration cycle according to the condensation temperature or the condensation pressure, a constant condensation temperature can be obtained.
【００１３】[0013]
【００１４】[0014]
【実施例】以下、本発明の実施例を図面を参照して説明
する。
第１の実施例
図１は、本発明の第１の実施例にかかる冷凍装置を示
し、この冷凍装置では一台の室外機１２に二台の室内機
１１がつながれる。室内機１１、室外機１２ともに、冷
媒には、ＨＦＣ系冷媒またはその混合冷媒が用いられ
る。このＨＦＣ系混合冷媒としては、例えばＲ１３４ａ
を５２Ｗｔ％、Ｒ１２５を２５Ｗｔ％、Ｒ３２を２３Ｗ
ｔ％で混合した非共沸混合冷媒等が用いられる。二台の
室内機１１は夫々室内側冷凍サイクル１０，１０Ａを備
え、これら室内側冷凍サイクル１０，１０Ａは、ショー
ケースや冷凍冷蔵用の冷却ユニットとして使用される。
また、室外機１２は、室外側冷凍サイクル３０を備え、
チラー等として使用される。Embodiments of the present invention will be described below with reference to the drawings. First Embodiment FIG. 1 shows a refrigerating apparatus according to a first embodiment of the present invention. In this refrigerating apparatus, one outdoor unit 12 and two indoor units 11 are connected. As the refrigerant for both the indoor unit 11 and the outdoor unit 12, an HFC-based refrigerant or a mixed refrigerant thereof is used. As this HFC-based mixed refrigerant, for example, R134a
52 Wt%, R125 25 Wt%, R32 23 W
A non-azeotropic mixed refrigerant or the like mixed at t% is used. The two indoor units 11 are respectively provided with indoor refrigeration cycles 10 and 10A, and these indoor refrigeration cycles 10 and 10A are used as a showcase and a cooling unit for freezing and refrigerating.
In addition, the outdoor unit 12 includes an outdoor refrigeration cycle 30,
Used as a chiller, etc.
【００１５】室内機１１の室内側冷凍サイクル１０は、
圧縮機１、凝縮器（凝縮用熱交換器）２、減圧装置３、
蒸発器４をつないで構成される。この減圧装置３として
は、膨張弁等を採用することができ、減圧装置３は、蒸
発器４と圧縮機１との間の温度センサ１７により検出さ
れる冷媒温度に応じて、適宜に減圧調整される。室内側
冷凍サイクル１０の凝縮器２は、二重管コイル式、シェ
ルアンドコイル式、あるいはシェルチューブ式の凝縮器
である。また、同様にして、室内機１１の室内側冷凍サ
イクル１０Ａは、圧縮機１Ａ、凝縮器（凝縮用熱交換
器）２Ａ、減圧装置３Ａ、蒸発器４Ａをつないで構成さ
れる。減圧装置３Ａとしては、膨張弁等を採用すること
ができ、減圧装置３Ａは、蒸発器４Ａと圧縮機１Ａとの
間の温度センサ１７Ａにより検出される冷媒温度に応じ
て、適宜に減圧調整される。室内側冷凍サイクル１０Ａ
の凝縮器２Ａは、二重管コイル式、シェルアンドコイル
式、あるいはシェルチューブ式の凝縮器である。The indoor refrigeration cycle 10 of the indoor unit 11 is
Compressor 1, condenser (condensation heat exchanger) 2, decompression device 3,
It is configured by connecting the evaporator 4. An expansion valve or the like can be used as the decompression device 3, and the decompression device 3 appropriately adjusts the decompression according to the refrigerant temperature detected by the temperature sensor 17 between the evaporator 4 and the compressor 1. To be done. The condenser 2 of the indoor refrigeration cycle 10 is a double tube coil type, shell and coil type, or shell tube type condenser. Similarly, the indoor refrigeration cycle 10A of the indoor unit 11 is configured by connecting a compressor 1A, a condenser (condensation heat exchanger) 2A, a pressure reducing device 3A, and an evaporator 4A. An expansion valve or the like can be used as the decompression device 3A, and the decompression device 3A is appropriately decompressed and adjusted according to the refrigerant temperature detected by the temperature sensor 17A between the evaporator 4A and the compressor 1A. It Indoor refrigeration cycle 10A
2A is a double-tube coil type, shell-and-coil type, or shell-tube type condenser.
【００１６】一方、室外機１２の室外側冷凍サイクル３
０は、高温用圧縮機６、凝縮器７、減圧装置８、蒸発器
（蒸発用熱交換器）９をつないで構成される。減圧装置
８としては、膨張弁等を採用することができ、この減圧
装置８は、蒸発器９と高温用圧縮機６との間の温度セン
サ２０により検出される冷媒温度に応じて、適宜に減圧
度合が調整される。On the other hand, the outdoor refrigeration cycle 3 of the outdoor unit 12
0 is configured by connecting a high temperature compressor 6, a condenser 7, a decompression device 8 and an evaporator (evaporation heat exchanger) 9. An expansion valve or the like can be used as the decompression device 8. The decompression device 8 is appropriately arranged according to the refrigerant temperature detected by the temperature sensor 20 between the evaporator 9 and the high temperature compressor 6. The degree of decompression is adjusted.
【００１７】室内側冷凍サイクル１０，１０Ａの凝縮器
２，２Ａと室外側冷凍サイクル３０の蒸発器９とは熱搬
送サイクル１５でつながれる。この熱搬送サイクル１５
は、室内側冷凍サイクル１０，１０Ａの凝縮器２，２Ａ
を冷却するための、言わば冷却用回路であり、この熱搬
送サイクル１５には、例えば、水や、塩化カルシウム、
塩化ナトリウム入りの溶液等（尚、本明細書ではこれら
溶液等を「ブライン」という。）が熱搬送媒体として充
填される。The heat transfer cycle 15 connects the condensers 2 and 2A of the indoor refrigeration cycle 10 and 10A with the evaporator 9 of the outdoor refrigeration cycle 30. This heat transfer cycle 15
Is the condenser 2, 2A of the indoor refrigeration cycle 10, 10A
The heat transfer cycle 15 is, for example, water, calcium chloride,
A solution or the like containing sodium chloride (herein, these solutions and the like are referred to as “brine”) is filled as a heat carrier medium.
【００１８】熱搬送サイクル１５は、室外側冷凍サイク
ル３０の蒸発器９、循環ポンプ１９、三方向調整弁５、
室内側冷凍サイクル１０の凝縮器２をつないで構成さ
れ、更には、分岐管１５ａ，１５ｂ、三方向調整弁５Ａ
を介して、もう１つの室内側冷凍サイクル１０Ａの凝縮
器２Ａを並列につないで構成される。熱搬送サイクル１
５の三方向調整弁５，５Ａは各室内機１１に収容され
る。これら三方向調整弁５，５Ａにはバイパス管１６，
１６Ａがつながれ、バイパス管１６，１６Ａは循環ポン
プ１９の圧力上昇を防止する。The heat transfer cycle 15 includes the evaporator 9, the circulation pump 19, the three-way regulating valve 5 of the outdoor refrigeration cycle 30,
It is configured by connecting the condenser 2 of the indoor refrigeration cycle 10, and further includes the branch pipes 15a and 15b and the three-way regulating valve 5A.
The condenser 2A of the other indoor refrigeration cycle 10A is connected in parallel via the. Heat transfer cycle 1
The three-way regulating valves 5 and 5A of 5 are housed in each indoor unit 11. By-pass pipe 16,
16A are connected, and the bypass pipes 16 and 16A prevent the pressure of the circulation pump 19 from rising.
【００１９】三方向調整弁５，５Ａは、凝縮器２，２Ａ
に流れるブラインの流量を、凝縮温度あるいは凝縮圧力
に応じて調整するために室内側冷凍サイクル１０，１０
Ａの冷媒温度に応じて開度調整される。この時の冷媒温
度は、温度センサ２１，２１Ａにより検出され、これら
温度センサ２１，２１Ａは凝縮器２，２Ａの出口に設け
られる。The three-way adjusting valves 5 and 5A are condensers 2 and 2A.
In order to adjust the flow rate of brine flowing in the room according to the condensation temperature or the condensation pressure, the indoor side refrigeration cycle 10, 10
The opening degree is adjusted according to the refrigerant temperature of A. The refrigerant temperature at this time is detected by temperature sensors 21 and 21A, and these temperature sensors 21 and 21A are provided at the outlets of the condensers 2 and 2A.
【００２０】以上、この実施例において特徴点は、室内
側冷凍サイクル１０，１０Ａと室外側冷凍サイクル３０
とが夫々ＨＦＣ系冷媒封入の完結型装置であることであ
る。つまり、特徴点は、個々の冷凍サイクル１０，１０
Ａ，３０が完全に独立した装置になっていて、施工現場
では、配管接続時に熱搬送サイクル１５にブラインを充
填するだけで冷媒充填が不要な点にある。As described above, the feature of this embodiment is that the indoor refrigeration cycle 10, 10A and the outdoor refrigeration cycle 30 are
And HFC-based refrigerant are enclosed in each unit. That is, the characteristic point is that the individual refrigeration cycles 10, 10
A and 30 are completely independent devices, and at the construction site, the refrigerant is not required to be filled only by filling the heat transfer cycle 15 with brine at the time of pipe connection.
【００２１】次に、第１の実施例の作用を説明する。室
内機１１の各室内側冷凍サイクル１０，１０Ａでは、そ
れぞれ圧縮機１、凝縮器２、減圧装置３、蒸発器４の順
序で冷媒が循環される。室外機１２の室外側冷凍サイク
ル３０では、高温用圧縮機６、凝縮器７、減圧装置８、
蒸発器９の順序で冷媒が循環される。室内側冷凍サイク
ル１０，１０Ａの各蒸発器４では冷媒が気化され外部か
ら熱をくみ上げる。Next, the operation of the first embodiment will be described. In each of the indoor refrigeration cycles 10 and 10A of the indoor unit 11, the refrigerant is circulated in the order of the compressor 1, the condenser 2, the pressure reducing device 3, and the evaporator 4, respectively. In the outdoor refrigeration cycle 30 of the outdoor unit 12, the high temperature compressor 6, the condenser 7, the pressure reducing device 8,
The refrigerant is circulated in the order of the evaporator 9. In each evaporator 4 of the indoor refrigeration cycle 10, 10A, the refrigerant is vaporized and heat is drawn from the outside.
【００２２】室内側冷凍サイクル１０，１０Ａと室外側
冷凍サイクル３０とは上述したようにＨＦＣ系冷媒の封
入完結型であるので、室内機１１と室外機１２とを現場
に搬入した場合、熱搬送サイクル１５だけを現場施工す
ればよい。この熱搬送サイクル１５にはブラインを充填
するだけなので、水分管理やゴミ管理は不要になり、当
然のことながら室内側冷凍サイクル１０，１０Ａや室外
側冷凍サイクル３０内には水分、空気等は入らないの
で、冷媒の分解や酸の発生、スラッジなどが発生するこ
とはなく、このスラッジが熱交換器の冷媒管に詰まるこ
とはない。従って、ショーケースや冷凍・冷蔵ユニット
等を現場施工する時間と、労力とを大幅に低減すること
ができる。Since the indoor side refrigeration cycle 10 and 10A and the outdoor side refrigeration cycle 30 are of the type in which the HFC refrigerant is completely enclosed as described above, when the indoor unit 11 and the outdoor unit 12 are carried into the site, heat transfer is performed. Only cycle 15 needs to be constructed on site. Since the heat transfer cycle 15 is only filled with brine, water management and dust management are not necessary, and naturally, the indoor refrigeration cycle 10, 10A and the outdoor refrigeration cycle 30 do not contain water, air, etc. Since it does not exist, the refrigerant is not decomposed, the acid is not generated, and the sludge is not generated, and the sludge is not clogged with the refrigerant pipe of the heat exchanger. Therefore, it is possible to significantly reduce the time and labor for constructing the showcase, the freezing / refrigerating unit and the like on site.
【００２３】現場施工した冷凍装置の熱搬送サイクル１
５内では、循環ポンプ４の作用によりブラインが矢印方
向に循環して室内機１１の室内側冷凍サイクル１０，１
０Ａの凝縮器２，２Ａを冷却する。三方向調整弁５，５
Ａは、凝縮器２，２Ａに流れるブラインの流量を、室内
側冷凍サイクル１０，１０Ａの凝縮温度あるいは凝縮圧
力に応じて調整する。例えば、室内側冷凍サイクル１０
の凝縮器２での凝縮温度が高くなったときには、三方向
調整弁５の開度を、凝縮器２への流量を増大させ、かつ
バイパス管１６への流量を減少させる開度とする。な
お、室内側冷凍サイクル１０Ａにおいても同様の操作を
行なう。Heat transfer cycle 1 for refrigeration equipment installed on site
In the inside 5, the brine is circulated in the arrow direction by the action of the circulation pump 4, and the indoor side refrigeration cycle 10, 1 of the indoor unit 11 is
Cool 0A condensers 2, 2A. Three-way control valve 5,5
A adjusts the flow rate of brine flowing through the condensers 2 and 2A according to the condensation temperature or condensation pressure of the indoor refrigeration cycle 10 or 10A. For example, the indoor refrigeration cycle 10
When the condensation temperature in the condenser 2 becomes high, the opening degree of the three-way regulating valve 5 is set to an opening degree that increases the flow rate to the condenser 2 and decreases the flow rate to the bypass pipe 16. The same operation is performed in the indoor refrigeration cycle 10A.
【００２４】このように、三方向調整弁５，５Ａが凝縮
器２，２Ａに流れるブラインの流量を調整するので、複
数の室内側冷凍サイクル１０，１０Ａを連設しても、各
室内側冷凍サイクル１０，１０Ａに流れるブラインは夫
々独立して調整され、所望の凝縮温度を得ることができ
る。
第２の実施例
図２は、第２の実施例にかかる冷凍装置の冷媒回路を示
している。図２の第２の実施例が図１の第１の実施例と
異なる点は、室外側冷凍サイクル３０が容量制御装置
（容量制御手段）１８を備えることである。この容量制
御装置１８は、熱搬送サイクル１５内のブライン温度を
室温（常温）に近づけるために、熱搬送サイクル１５の
循環ポンプ１９のブライン容量及び／又は室外側冷凍サ
イクル３０の高温用圧縮機６のＨＦＣ系冷媒の吐出容量
を制御する。このように制御するのは、一般に室外側冷
凍サイクル３０でブラインが室温以下に冷やされると、
配管が結露あるいは氷結するため、配管に断熱工事を施
こさなければならないためである。２７はブラインの温
度を検出するセンサである。従って、容量制御装置１８
を用いて循環ポンプ１９の容量及び／又は高温用圧縮機
６の容量を制御すれば、ブラインの温度を室温に近付け
ることができるので、配管が結露あるいは氷結すること
がなくなり、現場施工時に、配管に断熱工事を施こさな
くてもよいというメリットが得られる。つまり、室内側
の冷却装置が複数台接続された場合には、その冷却の負
荷変動がブラインの温度変化になるので、この温度を一
定にするため、容量制御装置１８は循環ポンプ１９の容
量及び／又は高温用圧縮機６の容量を制御している。
第３の実施例
図３は、第３の実施例にかかる冷凍装置の冷媒回路を示
している。図３の第３の実施例が、ほかの実施例と異な
る点は、次の通りである。すなわち、室内側冷凍サイク
ル１０のバイパス管１６にはエネルギを氷熱として蓄熱
する蓄熱槽２２と、三方弁２３とが設けられる。通常の
冷却運転では、図１の第１の実施例や図２の第２の実施
例と同様に、熱搬送サイクル１５において、循環ポンプ
１９の動作によりブラインが矢印Ａで示すように、凝縮
器２，２Ａと蒸発器４との間を循環する。As described above, since the three-way regulating valves 5, 5A regulate the flow rate of the brine flowing to the condensers 2, 2A, even if a plurality of indoor refrigeration cycles 10, 10A are connected in series, each indoor refrigeration cycle The brine flowing in cycles 10 and 10A can be independently adjusted to obtain the desired condensation temperature. Second Embodiment FIG. 2 shows a refrigerant circuit of a refrigeration system according to the second embodiment. The second embodiment of FIG. 2 is different from the first embodiment of FIG. 1 in that the outdoor refrigeration cycle 30 includes a capacity control device (capacity control means) 18. The capacity control device 18 adjusts the brine capacity of the circulation pump 19 of the heat transfer cycle 15 and / or the high temperature compressor 6 of the outdoor refrigeration cycle 30 in order to bring the temperature of the brine in the heat transfer cycle 15 close to room temperature (normal temperature). The discharge capacity of the HFC refrigerant is controlled. This control is generally performed when the brine is cooled to room temperature or below in the outdoor refrigeration cycle 30.
This is because the piping must be subjected to heat insulation work due to dew condensation or freezing. 27 is a sensor that detects the temperature of the brine. Therefore, the capacity control device 18
If the capacity of the circulation pump 19 and / or the capacity of the high temperature compressor 6 is controlled by using, the temperature of the brine can be brought close to room temperature, so that the piping does not condense or freeze, and the piping is The advantage is that there is no need to perform heat insulation work on the. That is, when a plurality of indoor side cooling devices are connected, the load fluctuation of the cooling becomes a temperature change of the brine. Therefore, in order to keep this temperature constant, the capacity control device 18 sets the capacity of the circulation pump 19 and The capacity of the high temperature compressor 6 is controlled. Third Embodiment FIG. 3 shows a refrigerant circuit of a refrigeration system according to the third embodiment. The third embodiment of FIG. 3 differs from the other embodiments in the following points. That is, the bypass pipe 16 of the indoor refrigeration cycle 10 is provided with a heat storage tank 22 that stores energy as ice heat and a three-way valve 23. In the normal cooling operation, as in the first embodiment of FIG. 1 and the second embodiment of FIG. 2, in the heat transfer cycle 15, the operation of the circulation pump 19 causes the brine to move toward the condenser as indicated by arrow A. It circulates between 2, 2A and the evaporator 4.
【００２５】これに対して、例えば昼間から夜間になっ
て周囲の温度が下がって室内側冷凍サイクル１０，１０
Ａの冷却負荷が減少した時には、通常の運転から蓄熱運
転に切り替わり、蓄熱槽２２に氷熱として蓄熱される。
この蓄熱運転では、三方向調整弁５，５Ａを切り替える
ことにより、室内側冷凍サイクル１０，１０Ａの夫々の
凝縮器２，２Ａにブラインを流さないようにする。つま
り、ブラインは、図３の破線矢印Ｂで示すように、室外
側冷凍サイクル３０の蒸発器９、室内側冷凍サイクル１
０の三方向調整弁５、蓄熱槽２２、そして蒸発器９の順
に流されるとともに、蒸発器９、室内側冷凍サイクル１
０Ａの三方向調整弁５Ａ、蓄熱槽２２、そして室外側冷
凍サイクル３０の蒸発器９の順に流される。このように
ブラインが流されると、室外側冷凍サイクル３０の蒸発
器９で与えられた氷熱は、すべてが蓄熱槽２２に氷熱と
して蓄熱され、この蓄熱が終了したら蓄熱運転は停止さ
れる。On the other hand, for example, the ambient temperature decreases from daytime to nighttime, and the indoor refrigeration cycle 10, 10
When the cooling load of A decreases, the normal operation is switched to the heat storage operation, and the heat is stored in the heat storage tank 22 as ice heat.
In this heat storage operation, the three-way control valves 5 and 5A are switched to prevent brine from flowing into the condensers 2 and 2A of the indoor refrigeration cycles 10 and 10A. That is, the brine is the evaporator 9 of the outdoor refrigeration cycle 30 and the indoor refrigeration cycle 1 as shown by the broken line arrow B in FIG.
The three-way regulating valve 5 of 0, the heat storage tank 22, and the evaporator 9 are flowed in this order, and the evaporator 9 and the indoor refrigeration cycle 1
The three-way regulating valve 5A of 0 A, the heat storage tank 22, and the evaporator 9 of the outdoor refrigeration cycle 30 are flowed in this order. When the brine is flown in this way, all of the ice heat given by the evaporator 9 of the outdoor refrigeration cycle 30 is stored in the heat storage tank 22 as ice heat, and the heat storage operation is stopped when this heat storage ends.
【００２６】しかして、この実施例によれば、上記の蓄
熱運転で蓄熱された氷熱を利用して冷却運転することが
できる。この際には、室外側冷凍サイクル３０の運転は
停止である。蓄熱槽２２に氷熱として蓄熱された熱は、
室内側冷凍サイクル１０の三方向調整弁２３を通じてポ
ンプ２４で汲み出される。すなわち、ブラインは図３の
破線矢印Ｃで示すように管路２８を通じて流出し、三方
向調整弁５、凝縮器２へと流れ、ここで室内側冷凍サイ
クル１０の凝縮器２を通る冷媒を冷却した後に、三方向
調整弁２５、分岐管２９を通って蓄熱槽２２に入り、再
び三方向調整弁２３を通じてポンプ２４で汲み出され
る。また、ブラインは管路２８を通じて流出し、分岐管
１５ａ、三方向調整弁５Ａ、凝縮器２Ａへと流れ、ここ
で室内側冷凍サイクル１０の凝縮器２Ａを通る冷媒を冷
却した後に、三方向調整弁２５、分岐管２９を通って蓄
熱槽２２に入り、再び三方向調整弁２３を通じてポンプ
２４で汲み出される。これによれば、蓄熱槽２２に氷熱
として蓄熱された熱を利用して冷却運転することができ
るので、省エネルギ化を図ることができる。Therefore, according to this embodiment, the cooling operation can be carried out by utilizing the ice heat accumulated in the above heat storage operation. At this time, the operation of the outdoor refrigeration cycle 30 is stopped. The heat stored as ice heat in the heat storage tank 22 is
It is pumped out by the pump 24 through the three-way regulating valve 23 of the indoor refrigeration cycle 10. That is, the brine flows out through the conduit 28 as shown by the broken line arrow C in FIG. 3, and flows to the three-way regulating valve 5 and the condenser 2, where the refrigerant passing through the condenser 2 of the indoor refrigeration cycle 10 is cooled. After that, it enters the heat storage tank 22 through the three-way adjusting valve 25 and the branch pipe 29, and is pumped out again by the pump 24 through the three-way adjusting valve 23. Further, the brine flows out through the pipe 28, flows to the branch pipe 15a, the three-way adjusting valve 5A, and the condenser 2A, where the refrigerant passing through the condenser 2A of the indoor refrigeration cycle 10 is cooled, and then the three-way adjusting is performed. It enters the heat storage tank 22 through the valve 25 and the branch pipe 29, and is pumped out again by the pump 24 through the three-way regulating valve 23. According to this, the cooling operation can be performed using the heat stored as the ice heat in the heat storage tank 22, so that energy saving can be achieved.
【００２７】要するに、本発明の冷凍装置によれば、室
内側冷凍サイクル、及び室外側冷凍サイクルが冷媒封入
完結型の装置であるので、長い冷媒配管の工事は不要に
なり、冷媒の充填は不要になり、施工のための労力と時
間が大幅に削減され、従来生じた現場における溶接の不
備等による品質の低下が抑制される。また、室内側冷凍
サイクル１０，１０Ａ、室外側冷凍サイクル３０が二元
冷凍サイクル型の装置となっているので、高圧冷媒の圧
縮比を小さくすることができ、効率アップを図ることが
できる等の効果を奏する。In short, according to the refrigerating apparatus of the present invention, since the indoor refrigerating cycle and the outdoor refrigerating cycle are refrigerant enclosing completion type apparatuses, the construction of long refrigerant pipes is unnecessary, and the refrigerant is not charged. Therefore, the labor and time required for the construction can be significantly reduced, and the deterioration of quality due to defective welding at the site, which has occurred in the past, can be suppressed. Further, since the indoor side refrigeration cycle 10, 10A and the outdoor side refrigeration cycle 30 are dual refrigeration cycle type devices, the compression ratio of the high pressure refrigerant can be reduced and efficiency can be improved. Produce an effect.
【００２８】[0028]
【発明の効果】以上説明したように、請求項１に記載の
発明によれば、熱搬送サイクルのブラインの温度を室温
に近づけるために、容量制御装置が室外側冷凍サイクル
の圧縮機の容量あるいは熱搬送サイクルのポンプの容量
を制御するので、室内側冷凍サイクルで冷却されたブラ
インの冷媒が室温以下に冷やされることで生じる結露や
氷結等の問題を防げるので、現場での断熱工事が不要に
なる。 As described above, according to the invention of claim 1 , the temperature of the brine in the heat transfer cycle is set to the room temperature.
In order to bring the capacity control device closer to
Compressor capacity or heat transfer cycle pump capacity
To control the bra cooled by the indoor refrigeration cycle.
Condensation caused by cooling the refrigerant in the room to below room temperature
Prevents problems such as freezing, eliminating the need for on-site insulation work
Become.
【００２９】[0029]
【００３０】請求項２に記載の発明によれば、調整手段
は、室内側冷凍サイクルの凝縮器のブラインの流量を、
凝縮温度あるいは凝縮圧力に応じて調整するので、冷媒
の一定の凝縮温度を得ることができる。According to the second aspect of the present invention, the adjusting means adjusts the flow rate of the brine in the condenser of the indoor refrigeration cycle,
Since it is adjusted according to the condensation temperature or the condensation pressure, a constant condensation temperature of the refrigerant can be obtained.
【００３１】[0031]
【図１】本発明の第１の実施例の冷凍装置の冷媒回路図
である。FIG. 1 is a refrigerant circuit diagram of a refrigerating apparatus according to a first embodiment of the present invention.
【図２】本発明の第２の実施例の冷凍装置の冷媒回路図
である。FIG. 2 is a refrigerant circuit diagram of the refrigerating apparatus according to the second embodiment of the present invention.
【図３】本発明の第２の実施例の冷凍装置の冷媒回路図
である。FIG. 3 is a refrigerant circuit diagram of the refrigerating apparatus according to the second embodiment of the present invention.
【図４】従来の冷凍装置の冷媒回路図である。FIG. 4 is a refrigerant circuit diagram of a conventional refrigeration system.
【図５】従来の別の冷凍装置の冷媒回路図である。FIG. 5 is a refrigerant circuit diagram of another conventional refrigeration system.
１ 圧縮機 ２，２Ａ 凝縮器 ３，３Ａ 減圧装置 ４，４Ａ 蒸発器 ６ 圧縮機 ７ 凝縮器 ８ 減圧装置 ９ 蒸発器 １０，１０Ａ 室内側冷凍サイクル １５ 熱搬送サイクル １８ 容量制御装置 ２２ 蓄熱槽 ３０ 室内側冷凍サイクル 1 compressor 2,2A condenser 3,3A decompression device 4,4A evaporator 6 compressor 7 condenser 8 decompression device 9 evaporator 10,10A Indoor refrigeration cycle 15 heat transfer cycle 18 Capacity control device 22 Heat storage tank 30 Indoor refrigeration cycle
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F25B 7/00 F25B 1/00 397 ─────────────────────────────────────────────────── ─── Continuation of front page (58) Fields surveyed (Int.Cl. 7 , DB name) F25B 7/00 F25B 1/00 397
Claims (2)
いだ室内側冷凍サイクルと、室外側冷凍サイクルの蒸発器と 前記室内側冷凍サイクル
の凝縮器とをつないだ熱搬送サイクルと、この熱搬送サイクルに設けられ、ブラインを循環させる
循環ポンプと、 前記熱搬送サイクルのブラインの温度を室温に近づける
ために、前記室外側冷凍サイクルに付加されて、前記室
外側冷凍サイクルの圧縮機の容量あるいは前記循環ポン
プの容量を制御する容量制御手段と、 を備えることを特徴とする冷凍装置。1. An indoor refrigeration cycle in which a compressor, a condenser, a decompression device, and an evaporator are connected, a heat transfer cycle in which an evaporator in the outdoor refrigeration cycle and a condenser in the indoor refrigeration cycle are connected, Provided in this heat transfer cycle to circulate brine
Bring the circulating pump and the brine in the heat transfer cycle closer to room temperature.
In order to add the outdoor refrigeration cycle to the
Capacity of the compressor of the outer refrigeration cycle or the circulating pump
And a capacity control means for controlling the capacity of the pump.
いだ室内側冷凍サイクルと、室外側冷凍サイクルの蒸発器と 前記室内側冷凍サイクル
の凝縮器とをつないだ熱搬送サイクルと、前記室内側冷凍サイクルの凝縮器の凝縮温度あるいは凝
縮圧力に応じて熱搬送サイクルの流量を調整する調整手
段と、 を備えたことを特徴とする冷凍装置。2. An indoor refrigeration cycle in which a compressor, a condenser, a decompression device, and an evaporator are connected, and a heat transfer cycle in which an evaporator in the outdoor refrigeration cycle and a condenser in the indoor refrigeration cycle are connected. The condensation temperature or condensation of the condenser of the indoor refrigeration cycle
Adjuster that adjusts the flow rate of the heat transfer cycle according to the contraction pressure
Refrigerating apparatus characterized by comprising: a stage, a.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17027195A JP3408022B2 (en) | 1995-06-13 | 1995-06-13 | Refrigeration equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17027195A JP3408022B2 (en) | 1995-06-13 | 1995-06-13 | Refrigeration equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08338667A JPH08338667A (en) | 1996-12-24 |
| JP3408022B2 true JP3408022B2 (en) | 2003-05-19 |
Family
ID=15901851
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17027195A Expired - Fee Related JP3408022B2 (en) | 1995-06-13 | 1995-06-13 | Refrigeration equipment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3408022B2 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007071519A (en) * | 2005-09-09 | 2007-03-22 | Sanden Corp | Cooling system |
| EP2245388A2 (en) * | 2008-02-15 | 2010-11-03 | Ice Energy, Inc. | Thermal energy storage and cooling system utilizing multiple refrigerant and cooling loops with a common evaporator coil |
| WO2014097438A1 (en) * | 2012-12-20 | 2014-06-26 | 三菱電機株式会社 | Air-conditioning device |
| WO2014097439A1 (en) * | 2012-12-20 | 2014-06-26 | 三菱電機株式会社 | Air-conditioning device |
| WO2014097440A1 (en) * | 2012-12-20 | 2014-06-26 | 三菱電機株式会社 | Air-conditioning device |
| WO2025203427A1 (en) * | 2024-03-28 | 2025-10-02 | 三菱電機株式会社 | Air conditioning device |
| WO2025203425A1 (en) * | 2024-03-28 | 2025-10-02 | 三菱電機株式会社 | Air conditioner |
-
1995
- 1995-06-13 JP JP17027195A patent/JP3408022B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH08338667A (en) | 1996-12-24 |
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