JPH03144236A - Cooling and heating device for multi rooms - Google Patents
Cooling and heating device for multi roomsInfo
- Publication number
- JPH03144236A JPH03144236A JP18650789A JP18650789A JPH03144236A JP H03144236 A JPH03144236 A JP H03144236A JP 18650789 A JP18650789 A JP 18650789A JP 18650789 A JP18650789 A JP 18650789A JP H03144236 A JPH03144236 A JP H03144236A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- refrigerant
- heat
- auxiliary
- refrigerant cycle
- 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.)
- Granted
Links
- 238000010438 heat treatment Methods 0.000 title claims abstract description 27
- 238000001816 cooling Methods 0.000 title claims abstract description 24
- 239000003507 refrigerant Substances 0.000 claims abstract description 91
- 238000005338 heat storage Methods 0.000 claims description 36
- 230000005855 radiation Effects 0.000 claims description 13
- 238000004378 air conditioning Methods 0.000 claims description 12
- 239000000463 material Substances 0.000 abstract 2
- 238000000034 method Methods 0.000 abstract 1
- 239000011232 storage material Substances 0.000 description 7
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は多室冷暖房装置の冷媒サイクルに関するもので
ある。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a refrigerant cycle for a multi-room heating and cooling system.
従来の技術
従来の熱源側冷媒サイクルと利用側冷媒サイクμに分離
された多室冷暖房装置は特開昭６２−２７２０４０号公
報に示されている。2. Description of the Related Art A conventional multi-room air conditioning system separated into a heat source side refrigerant cycle and a user side refrigerant cycle μ is disclosed in Japanese Patent Laid-Open No. 62-272040.
以下図面を参照しながら説明する。第２図において、１
１は圧縮機、１２は四方弁、１３は熱源側熱交換器、１
４は冷房用減圧装置、１６は暖房用減圧装置、１６は暖
房時冷房用減圧装置１４を閉成する逆止弁、１７は冷房
時暖房用減圧装置１Ｂを閉成する逆止弁、１８は第１補
助熱交換器でこれらを環状に連接し、熱源側冷媒サイク
ルを形成している。１９は第２補助熱交換器で第１補助
熱交換器１８と熱交換するように一体に形成されている
。２ｏは冷媒量調整タンクで冷房時と暖房時の冷凍量を
調整している。２１は冷媒搬送装置で冷房時と暖房時で
冷媒の流出方向が反対となる可逆特性をもっており、こ
れらは室外ユニッ）ｆに収納されている。２２ａ 、２
２ｂは利用側熱交換器で室内ユニッ） ’ｘ ｅ ｈに
収納され接続配管１゜ｉ／、 Ｊ、 ｓ／で室外ユニッ
）ｆと接続されている。This will be explained below with reference to the drawings. In Figure 2, 1
1 is a compressor, 12 is a four-way valve, 13 is a heat source side heat exchanger, 1
4 is a pressure reducing device for cooling, 16 is a heating pressure reducing device, 16 is a check valve that closes the cooling pressure reducing device 14 during heating, 17 is a check valve that closes the heating pressure reducing device 1B during cooling, and 18 is a check valve that closes the heating pressure reducing device 1B. These are connected in an annular manner by the first auxiliary heat exchanger to form a heat source side refrigerant cycle. A second auxiliary heat exchanger 19 is integrally formed to exchange heat with the first auxiliary heat exchanger 18. 2o is a refrigerant amount adjustment tank that adjusts the amount of refrigeration during cooling and heating. Reference numeral 21 denotes a refrigerant conveying device which has a reversible characteristic in which the outflow direction of the refrigerant is opposite during cooling and heating, and is housed in an outdoor unit) f. 22a, 2
2b is the heat exchanger on the user side, which is housed in the indoor unit (x e h) and connected to the outdoor unit (f) through the connecting pipes 1゜i/, J, s/.
前記第２補助熱交換器１９と冷媒量調整タンク２０゜冷
媒搬送装置２１．利用側熱交換器２２ａ、２２ｂおよび
接続配管ｉ、ｔ／、ｔ、Ｉを環状連接し利用側冷媒サイ
クルを形成している。The second auxiliary heat exchanger 19, the refrigerant amount adjustment tank 20°, and the refrigerant conveyance device 21. The utilization side heat exchangers 22a, 22b and the connecting pipes i, t/, t, and I are connected in a ring to form a utilization side refrigerant cycle.
以上のように構成された多室冷暖房装置について、その
動作を説明する。The operation of the multi-room heating and cooling system configured as described above will be explained.
冷房運転時は図中実線の冷媒サイクルとなシ、熱源側冷
媒サイクルでは、圧縮機１１からの高温高圧ガスは四方
弁１２を通り熱源側熱交換器１３で放熱して凝縮液化し
、逆止弁１６を通って冷房用膨張弁１４で減圧され第１
補助熱交換器１８で蒸発して四方弁１２を通シ圧縮機１
２へ循環する。During cooling operation, the refrigerant cycle shown by the solid line in the figure is used.In the refrigerant cycle on the heat source side, high temperature and high pressure gas from the compressor 11 passes through the four-way valve 12, radiates heat in the heat exchanger 13 on the heat source side, condenses and liquefies, and then It passes through the valve 16 and is depressurized by the cooling expansion valve 14.
It is evaporated in the auxiliary heat exchanger 18 and passed through the four-way valve 12 to the compressor 1.
Cycle to 2.
この時利用側冷媒サイクルの第２補助熱交換器１９と前
記第１補助熱交換器１８が熱交換し、利用側冷媒サイク
ル内のガヌ冷謀が冷却されて液化し、冷媒量調整タンク
２ｏを通って冷媒搬送装置２１に送られ、この冷媒搬送
装置２１によって接続配管ｌ、１を通って利用側熱交換
器２２ａ、２２ｂへ送られて吸熱蒸発し、ガス化して接
続配管ｉ′。At this time, the second auxiliary heat exchanger 19 of the user side refrigerant cycle and the first auxiliary heat exchanger 18 exchange heat, and the Ganu refrigerant in the user side refrigerant cycle is cooled and liquefied, and the refrigerant amount adjustment tank 2o The refrigerant is sent to the refrigerant conveying device 21 through the refrigerant conveying device 21, and is sent to the user-side heat exchangers 22a, 22b through the connecting pipes 1 and 1, where it is endothermically evaporated, gasified, and transferred to the connecting pipe i'.
ｊ′を通って第２補助熱交換器１ｅに循環することにな
る。j' to be circulated to the second auxiliary heat exchanger 1e.
一方、暖房運転時においては、図中破線の冷媒サイクル
となり、熱源側冷媒サイクルでは、圧縮機１１からの高
温高圧冷媒は四方弁１２から第１補助熱交換器１８に送
られ、放熱して凝縮液化し、逆止弁１７から暖房用減圧
装置１６で減圧し、熱源側熱交換器１３で吸熱蒸発し、
四方弁１２を通って圧縮機１１へ循環する。この時利用
側冷媒サイクルの第２補助熱交換器１９と前記第１補助
熱交換器１８が熱交換し、利用側冷媒サイクル内の液冷
媒が加熱されてガス化し、接続配管１ＭＩを通って利用
側熱交換器２２へ送られ、暖房して放熱液化し接続配管
ｉ、１を通って冷媒搬送装置２１へ送られ、冷媒量調整
タンク２０から第２補助熱交換器１９へ循環する。On the other hand, during heating operation, the refrigerant cycle is indicated by the broken line in the figure, and in the heat source side refrigerant cycle, the high-temperature, high-pressure refrigerant from the compressor 11 is sent from the four-way valve 12 to the first auxiliary heat exchanger 18, radiates heat and condenses. It is liquefied, the pressure is reduced by the heating pressure reducing device 16 from the check valve 17, and it is endothermically evaporated in the heat source side heat exchanger 13.
It circulates through the four-way valve 12 to the compressor 11. At this time, the second auxiliary heat exchanger 19 of the user-side refrigerant cycle and the first auxiliary heat exchanger 18 exchange heat, and the liquid refrigerant in the user-side refrigerant cycle is heated and gasified, and is used through the connecting pipe 1MI. The refrigerant is sent to the side heat exchanger 22, heated, radiated, liquefied, passed through the connecting pipes i and 1, sent to the refrigerant transport device 21, and circulated from the refrigerant amount adjustment tank 20 to the second auxiliary heat exchanger 19.
発明が解決しようとする課題
しかしながら上記の構成では、最大能力は限られており
ピーク負荷に見合った装置能力としなければならない。Problems to be Solved by the Invention However, in the above configuration, the maximum capacity is limited, and the device capacity must be adjusted to match the peak load.
従って設備容量の大きくなりイニシャルコストやランニ
ングコストの増加トなり、省エネルギー課題を有してい
た。As a result, the equipment capacity increases, leading to increases in initial costs and running costs, leading to energy saving issues.
本発明は上記課題に鑑み、短時間のピーク負荷に対応し
た装置を備え設備容量の削減によるイニシャルコストや
ランニングコストの低減とともに省エネルギー化を図っ
た多室冷暖房装置を提供するものである。In view of the above-mentioned problems, the present invention provides a multi-room air conditioning and heating system that is equipped with a device that can handle short-term peak loads and that reduces initial costs and running costs by reducing equipment capacity, as well as saves energy.
課題を解決するための手段
上記課題を解決するために本発明の多室冷暖房装置は、
圧縮機、熱源側熱交換器、冷暖房用減圧装置および第１
補助熱交換器を環状に連接してなる熱源側冷媒サイクル
と、この第１補助交換器と一体に形成し、熱交換する第
２補助熱交換器と冷媒搬送装置および複数の利用側熱交
換器を有する利用側冷媒サイクルと、前記第１補助熱交
換器と並列に蓄熱用熱交換器と、前記第２補助熱交換器
と並列に蓄熱を放熱する放熱用熱交換器と、前記蓄熱用
熱交換器と放熱用熱交換器を有する蓄熱槽とを備えたも
のである。Means for Solving the Problems In order to solve the above problems, the multi-room air conditioning system of the present invention has the following features:
Compressor, heat source side heat exchanger, cooling/heating pressure reducing device, and first
A heat source side refrigerant cycle formed by connecting auxiliary heat exchangers in a ring, a second auxiliary heat exchanger formed integrally with the first auxiliary exchanger and exchanging heat, a refrigerant conveying device, and a plurality of user side heat exchangers. a heat storage heat exchanger in parallel with the first auxiliary heat exchanger, a heat radiation heat exchanger that radiates the stored heat in parallel with the second auxiliary heat exchanger, and the heat storage heat exchanger in parallel with the second auxiliary heat exchanger. It is equipped with an exchanger and a heat storage tank having a heat exchanger for heat radiation.
作 用
本発明は上記した構成によって、夜間に蓄熱槽に蓄熱（
例えば冷房時は氷として）しておき、短時間のピーク負
荷にこの蓄熱を使用することによって、圧縮機の容量を
小さくて、設備容量を削減できることとなる。Effect The present invention has the above-described configuration, and stores heat in the heat storage tank at night.
For example, by storing heat (as ice during cooling) and using this heat storage for short-term peak loads, the capacity of the compressor can be reduced and the installed capacity can be reduced.
実施例
以下本発明の一実施例の多室冷暖房装置について、図面
を参照しながら説明する。第１図は本発明の多室冷暖房
装置の冷媒サイクル図を示すものである。図において蓄
熱を使わない基本の冷媒サイクルは第２図と同じであり
、ここでは、その違っている所、すなわち蓄熱を使用す
る冷媒サイクルについて説明する。EXAMPLE Hereinafter, a multi-room air conditioning system according to an example of the present invention will be described with reference to the drawings. FIG. 1 shows a refrigerant cycle diagram of the multi-room air conditioning system of the present invention. In the figure, the basic refrigerant cycle that does not use heat storage is the same as in FIG. 2, and here we will explain the difference, that is, the refrigerant cycle that uses heat storage.
２３は蓄熱槽で内部に水等の蓄熱材を充てんし、その蓄
熱材と熱交換し蓄熱させる蓄熱用熱交換器２４と、同じ
く蓄熱はと熱交換し暑熱を放熱させる放熱用熱交換器２
１を備えている。A heat storage tank 23 is filled with a heat storage material such as water, and a heat storage heat exchanger 24 stores heat by exchanging heat with the heat storage material, and a heat radiation heat exchanger 2 stores heat by exchanging heat with the heat storage material and radiates hot heat.
1.
２６ａ、２６ｂは第１補助熱交換器と前記蓄熱用熱交換
器２４への冷媒流通を切換える三方切換弁、２７ａ 、
２７ｂは第２補助熱交換器１９と前記放熱用熱交換器２
６への冷媒流量を調整する三方流量弁である１゜
以上のように構成された多室冷暖房装置について以下そ
の動作を説明する。26a and 26b are three-way switching valves that switch the refrigerant flow to the first auxiliary heat exchanger and the heat storage heat exchanger 24; 27a;
27b is the second auxiliary heat exchanger 19 and the heat radiation heat exchanger 2;
The operation of a multi-room air-conditioning/heating system having a three-way flow rate valve that adjusts the flow rate of refrigerant to 6 will be described below.
冷房時熱源側冷媒サイクルの蓄熱運転は、冷房用膨張弁
１４が蓄熱用膨張弁となり、圧縮Ｉａ１１゜四方弁１２
．熱源ｔＩＩＩ熱交換器、逆止弁１６からの冷媒が蓄熱
用膨張弁１４を通過し三方切換弁２６ａを通り蓄熱用熱
交換器２４に流通し、蓄熱材と熱交換して吸熱蒸発し、
三方切換弁２ｅｂを通って四方弁から圧縮機１１へ循環
する。During the heat storage operation of the heat source side refrigerant cycle during cooling, the cooling expansion valve 14 becomes the heat storage expansion valve, and the compression Ia 11° four-way valve 12
．． The refrigerant from the heat source TIII heat exchanger and the check valve 16 passes through the heat storage expansion valve 14, passes through the three-way switching valve 26a, and flows to the heat storage heat exchanger 24, where it exchanges heat with the heat storage material and absorbs heat and evaporates.
It circulates from the four-way valve to the compressor 11 through the three-way switching valve 2eb.
一方、利用側冷媒サイクルの冷房ピーク負荷運転時は、
熱源側冷媒サイクルが第１補助熱交換器１８を蒸発器と
する通常の冷房運転となり、利用側熱交換器２２ ａ
＃ ２２ ｂからの冷媒は接続配管１／ 、 ３／を通
り、負荷に合わせて調整された冷媒の一部は三方流量弁
２７ａから放熱用熱交換器２６に送られ、０℃程度の蓄
熱材によって冷却凝縮して液化し三方流量弁２７ｂへ送
られる。On the other hand, during cooling peak load operation of the user refrigerant cycle,
The heat source side refrigerant cycle enters normal cooling operation using the first auxiliary heat exchanger 18 as an evaporator, and the user side heat exchanger 22 a
The refrigerant from #22b passes through the connecting pipes 1/ and 3/, and a part of the refrigerant adjusted according to the load is sent from the three-way flow valve 27a to the heat exchanger 26 for heat radiation, and is transferred to the heat storage material at about 0°C. The liquid is cooled, condensed, liquefied, and sent to the three-way flow valve 27b.
また接続配管１／、３／を通った三方流量弁２７ｍで負
荷に合わせて調整された残りの冷媒は三方流量弁２７ａ
から第２補助熱交換器１９へ流通し、第１補助熱交換器
１８により冷却液化されて三方流量弁２７ｂに送られ前
記放熱用熱交換器２６からの冷媒と合流し、冷媒量調整
タンク２ｏから冷媒搬送装置２１へ循環する。従って、
この時、利用側冷媒サイクルの冷房能力は、はぼ熱源側
冷媒サイクルの能力と放熱用熱交換器２６の能力の和と
なり増大する。In addition, the remaining refrigerant adjusted according to the load is discharged through the three-way flow valve 27m, which passes through the connecting pipes 1/ and 3/, through the three-way flow valve 27a.
The refrigerant flows from the auxiliary heat exchanger 19 to the second auxiliary heat exchanger 19, is cooled and liquefied by the first auxiliary heat exchanger 18, is sent to the three-way flow valve 27b, joins with the refrigerant from the heat radiating heat exchanger 26, and enters the refrigerant amount adjustment tank 2o. The refrigerant is circulated from there to the refrigerant conveying device 21. Therefore,
At this time, the cooling capacity of the user-side refrigerant cycle increases as it becomes the sum of the capacity of the heat source-side refrigerant cycle and the capacity of the heat radiation heat exchanger 26.
また暖房時熱源側冷媒サイクルの蓄熱運転は、圧縮機１
１．四方弁１２からの冷媒は三方切換弁２６ｂから蓄熱
用熱交換器２４へ送られ蓄熱材で冷却凝縮して液化し、
三方切換弁２６ａから逆止弁１７を通って暖房用膨張弁
１６で減圧され、熱源側熱交換器１３で吸熱蒸発し、四
方弁１２から圧縮機１１へ循環する。In addition, the heat storage operation of the heat source side refrigerant cycle during heating is performed by the compressor 1.
1. The refrigerant from the four-way valve 12 is sent from the three-way switching valve 26b to the heat storage heat exchanger 24, where it is cooled by a heat storage material, condensed, and liquefied.
It passes from the three-way switching valve 26a through the check valve 17, is depressurized by the heating expansion valve 16, is endothermically evaporated in the heat source side heat exchanger 13, and is circulated from the four-way valve 12 to the compressor 11.
一方、利用側冷媒サイクルの暖房ピーク負荷運転時、熱
源側冷媒サイクルは三方切換弁２６Ｊｌ 。On the other hand, during peak heating load operation of the user side refrigerant cycle, the heat source side refrigerant cycle has a three-way switching valve 26Jl.
２６ｂを切換え第１補助熱交換器１８を凝縮器とする通
常の暖房運転を行なう。この時利用側熱交換器２２＆、
２２ｂで放熱凝縮した冷媒は、接続配管ｌ、Ｓを通シ、
冷媒搬送装置２１から冷媒量調整タンク２ｏを通って三
方流量弁２７ｂへ送られる。この三方流量弁２７ｂでは
負荷に合わせて、冷媒の一部は放熱用熱交換器２５へ送
られて蓄熱材で加熱ガス化し、また残りの冷媒は第２補
助熱交換器１９へ送られ、第１補助熱交換器１８で加熱
ガス化し、三方流量弁２７ａでそれぞれのガス冷媒が合
流し、接続配管１１．１／を通って利用側熱交換器２２
ａ 、２２ｂへ循環する。26b is switched to perform normal heating operation using the first auxiliary heat exchanger 18 as a condenser. At this time, the user side heat exchanger 22&,
The refrigerant heat-radiated and condensed in 22b is passed through the connecting pipes l and S.
The refrigerant is sent from the refrigerant transport device 21 to the three-way flow valve 27b through the refrigerant amount adjustment tank 2o. In this three-way flow valve 27b, according to the load, a part of the refrigerant is sent to the radiation heat exchanger 25 where it is heated and gasified by the heat storage material, and the remaining refrigerant is sent to the second auxiliary heat exchanger 19 and the second auxiliary heat exchanger 19. 1 is heated and gasified in the auxiliary heat exchanger 18, and the respective gas refrigerants are combined at the three-way flow valve 27a, and passed through the connecting pipe 11.1/ to the user-side heat exchanger 22.
a, circulates to 22b.
従って、この時利用側冷媒サイクルの暖房能力は、はぼ
熱源側冷媒サイクルの暖房能力と放熱用熱交換器２６の
能力の和となり増大する。Therefore, at this time, the heating capacity of the user-side refrigerant cycle increases as it becomes the sum of the heating capacity of the heat source-side refrigerant cycle and the capacity of the heat radiation heat exchanger 26.
以上のように本実施例によれば、夜間に蓄熱しておくこ
とによって、冷暖房時のピーク負荷時に熱源側冷媒サイ
クルの能力と蓄熱槽の内部に設置された放熱用熱交換器
の能力が加わシ、ピーク負荷に対応することができるの
で、圧縮機の小容量とし設備容量を小さくできることに
なる。従って、イニシャルコスト及びランニングコスト
の低減トなるとともに省エネルギー化に役立つものであ
る。As described above, according to this embodiment, by storing heat at night, the capacity of the heat source side refrigerant cycle and the capacity of the heat radiation heat exchanger installed inside the heat storage tank are increased during peak loads during cooling and heating. Since the compressor can handle peak loads, the capacity of the compressor can be reduced and the equipment capacity can be reduced. Therefore, it is useful for reducing initial cost and running cost and for energy saving.
なお、本実施例では、熱源側冷媒サイクルを運転した蓄
熱利用を説明したが、場合によっては熱源側冷媒サイク
ルを運転しない、蓄熱だけの冷暖房運転も可能であると
ともに起動時に蓄熱を使うことによって立上シ特性が向
上することは言うまでもない。また実施例では蓄熱槽を
含めた室外ユニットとしたが蓄熱槽を熱源側サイクルと
分離してもよい。In this example, the heat storage utilization was explained by operating the heat source side refrigerant cycle. However, in some cases, it is also possible to perform cooling/heating operation using only heat storage without operating the heat source side refrigerant cycle. Needless to say, the mechanical properties are improved. Further, in the embodiment, an outdoor unit including a heat storage tank is used, but the heat storage tank may be separated from the heat source side cycle.
発明の効果
以上のように本発明は、熱源側冷媒サイクルと利用側冷
媒サイクルに分離し、第１補助熱交換器と並列に蓄熱用
熱交換器と、第２補助熱交換器と並列に放熱用熱交換器
と、前記蓄熱用熱交換器と放熱用熱交換器を有する蓄熱
槽を備えたことによリ、夜間に蓄熱し、利用側冷媒サイ
ク〃の冷暖房ピーク負荷時に熱源側冷媒サイクルの能力
に前記放熱用熱交換器の能力が加わり、ピーク負荷に対
応できることとなる。従って、圧縮機を小容量とし設備
容量を小さくできるので、イニシャルコスト及びランニ
ングコストの低減となるとともに省エネルギー化に効果
がある。Effects of the Invention As described above, the present invention separates the refrigerant cycle into a heat source side refrigerant cycle and a user side refrigerant cycle, and includes a heat storage heat exchanger in parallel with the first auxiliary heat exchanger and a heat radiating heat exchanger in parallel with the second auxiliary heat exchanger. By providing a heat exchanger for heating and cooling, and a heat storage tank having the heat exchanger for heat storage and the heat exchanger for heat radiation, heat is stored at night and the heat source side refrigerant cycle is used during peak cooling/heating loads of the user side refrigerant cycle. The capacity of the heat exchanger for heat dissipation is added to the capacity, and it becomes possible to cope with the peak load. Therefore, the capacity of the compressor can be made small and the capacity of the equipment can be reduced, which is effective in reducing initial cost and running cost, as well as energy saving.
第１図は本発明の実施例における冷暖房装置の冷媒サイ
クル図、第２図は本発明の他の実施例における室内ユニ
ットの接続図、第３図は従来の冷暖房装置の冷媒サイク
ル図である。
１３・・・・・・熱源側熱交換器、１８・・・・・・第
１補助熱交換器、１９・・・・・・第２補助熱交換器、
２１・・・・・・冷媒搬送装置、２２・・・・・・利用
側熱交換器、２３・・・・・・蓄熱槽、２４・・・・・
・蓄熱用熱交換器、２６・・・・・・放熱用熱交換器。FIG. 1 is a refrigerant cycle diagram of an air conditioning system according to an embodiment of the present invention, FIG. 2 is a connection diagram of an indoor unit according to another embodiment of the invention, and FIG. 3 is a refrigerant cycle diagram of a conventional air conditioning system. 13... Heat source side heat exchanger, 18... First auxiliary heat exchanger, 19... Second auxiliary heat exchanger,
21... Refrigerant conveyance device, 22... Usage side heat exchanger, 23... Heat storage tank, 24...
- Heat exchanger for heat storage, 26...Heat exchanger for heat radiation.
Claims (1)
び第１補助熱交換器を環状に連接してなる熱源側冷媒サ
イクルと、この第１補助熱交換器と一体に形成し、熱交
換する第２補助熱交換器と冷媒搬送装置および複数の利
用側熱交換器を有する利用側冷媒サイクルと、前記第１
補助熱交換器と並列に蓄熱用熱交換器と、前記第２補助
熱交換器と並列に蓄熱を放熱する放熱用熱交換器と、前
記蓄熱用交換器と放熱用熱交換器を有する蓄熱槽とを備
えた多室冷暖房装置。 （２）圧縮機に能力制御圧縮機を搭載した特許請求の範
囲第１項記載の多室冷暖房装置。（３）熱源側冷媒サイ
クルと利用側冷媒サイクルの使用冷媒の異なる特許請求
の範囲第１項記載の多室冷暖房装置。 （４）第１補助熱交換器と第２補助熱交換器に積層式熱
交換器を使用した特許請求の範囲第１項記載の多室冷暖
房装置。[Scope of Claims] (1) A heat source side refrigerant cycle formed by connecting a compressor, a heat source side heat exchanger, a pressure reducing device for heating and cooling, and a first auxiliary heat exchanger in an annular manner, and the first auxiliary heat exchanger. a user-side refrigerant cycle having a second auxiliary heat exchanger and a refrigerant conveyance device integrally formed to exchange heat, and a plurality of user-side heat exchangers;
A heat storage tank having a heat storage heat exchanger in parallel with the auxiliary heat exchanger, a heat radiation heat exchanger that radiates stored heat in parallel with the second auxiliary heat exchanger, and the heat storage exchanger and the heat radiation heat exchanger. Multi-room air conditioning and heating system equipped with (2) The multi-room air conditioning system according to claim 1, wherein the compressor is equipped with a capacity control compressor. (3) The multi-room air conditioning system according to claim 1, in which the heat source side refrigerant cycle and the usage side refrigerant cycle use different refrigerants. (4) The multi-room air-conditioning system according to claim 1, wherein stacked heat exchangers are used as the first auxiliary heat exchanger and the second auxiliary heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1186507A JP2702784B2 (en) | 1989-07-19 | 1989-07-19 | Multi-room air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1186507A JP2702784B2 (en) | 1989-07-19 | 1989-07-19 | Multi-room air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03144236A true JPH03144236A (en) | 1991-06-19 |
| JP2702784B2 JP2702784B2 (en) | 1998-01-26 |
Family
ID=16189710
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1186507A Expired - Fee Related JP2702784B2 (en) | 1989-07-19 | 1989-07-19 | Multi-room air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2702784B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010216777A (en) * | 2009-03-19 | 2010-09-30 | Hitachi Appliances Inc | Refrigerating machine, and refrigerating and air-conditioning system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105091258B (en) * | 2014-05-23 | 2018-03-16 | 广东美的暖通设备有限公司 | Air conditioner and its cooling control method |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51102064U (en) * | 1975-02-03 | 1976-08-16 |
-
1989
- 1989-07-19 JP JP1186507A patent/JP2702784B2/en not_active Expired - Fee Related
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51102064U (en) * | 1975-02-03 | 1976-08-16 |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010216777A (en) * | 2009-03-19 | 2010-09-30 | Hitachi Appliances Inc | Refrigerating machine, and refrigerating and air-conditioning system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2702784B2 (en) | 1998-01-26 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |