JPH01306758A - Coolor-heater - Google Patents
Coolor-heaterInfo
- Publication number
- JPH01306758A JPH01306758A JP63138851A JP13885188A JPH01306758A JP H01306758 A JPH01306758 A JP H01306758A JP 63138851 A JP63138851 A JP 63138851A JP 13885188 A JP13885188 A JP 13885188A JP H01306758 A JPH01306758 A JP H01306758A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- heat source
- refrigerant cycle
- heat exchanger
- source side
- 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
- 239000003507 refrigerant Substances 0.000 claims abstract description 87
- 238000010438 heat treatment Methods 0.000 claims description 15
- 238000001816 cooling Methods 0.000 claims description 14
- 238000001514 detection method Methods 0.000 claims description 11
- 238000011144 upstream manufacturing Methods 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Air Conditioning Control Device (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は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 INDUSTRIAL APPLICATION The present invention relates to a refrigerant cycle for a heating and cooling system.
従来の技術
従来、熱源側冷媒サイクルと利用側冷媒サイクルに分離
した冷暖房装置の冷媒サイクルは第２図のように構成さ
れていた。第２図において、１は圧縮機、２は熱源側四
方弁、３は熱源側熱交換器、４は冷房用減圧装置、６は
暖房用減圧装置、６は ′暖房時冷房用減圧装置４を
閉成する逆止弁、７は冷房時暖房用減圧装置６を閉成す
る逆止弁、８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。９は第２補助
熱交換器で第１補助熱交換器８と熱交換するように一体
に形成されている。１０は冷媒量調整タンクで冷房時と
暖房時の冷媒量を調整している。１１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
をもっておシ、これらは熱源側ユニットａに収納されて
いる。１２は利用側熱交換器で利用側ユニッ）ｂに収納
され接続配管ｃ、ｃで熱源側ユニットａと接続されてい
る。BACKGROUND OF THE INVENTION Conventionally, the refrigerant cycle of an air-conditioning system is divided into a heat source-side refrigerant cycle and a user-side refrigerant cycle, as shown in FIG. In Fig. 2, 1 is a compressor, 2 is a four-way valve on the heat source side, 3 is a heat exchanger on the heat source side, 4 is a pressure reducing device for cooling, 6 is a pressure reducing device for heating, and 6 is a pressure reducing device 4 for cooling during heating. 7 is a check valve that closes the pressure reducing device 6 for heating during cooling; 8 is a first auxiliary heat exchanger; these are connected in an annular manner to form a heat source side refrigerant cycle. A second auxiliary heat exchanger 9 is integrally formed to exchange heat with the first auxiliary heat exchanger 8. 10 is a refrigerant amount adjustment tank that adjusts the amount of refrigerant during cooling and heating. Reference numeral 11 denotes a refrigerant conveying device which has a reversible characteristic such that the outflow direction of the refrigerant is opposite during cooling and heating, and is housed in the heat source side unit a. Reference numeral 12 denotes a heat exchanger on the user side, which is housed in the user side unit b) and connected to the heat source side unit a through connecting pipes c and c.
前記第２補助熱交換器９と冷媒量調整タンク１Ｑ、冷媒
搬送装置１１、利用側熱交換器１２および接続配管ａ、
ｃを環状に接続し利用側冷媒サイクルを形成している。The second auxiliary heat exchanger 9, the refrigerant amount adjustment tank 1Q, the refrigerant transport device 11, the user-side heat exchanger 12, and the connecting pipe a,
c are connected in a ring to form a user-side refrigerant cycle.
以上のように構成された冷暖房装置についてその動作を
説明する。The operation of the heating and cooling system configured as described above will be explained.
冷房運転時は図中実線矢印の冷媒サイクルとなり、熱源
側冷媒サイクルでは、圧縮機１からの高温高圧ガスは四
方弁２を通り熱源側熱交換器３で放熱して凝縮液化し逆
止弁６を通って冷房用膨張弁４で減圧され第１補助熱交
換器８で蒸発して熱源叫四方が２を通り圧縮機１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９
と前記・第１補助熱交換器８が熱交換し、利用側冷媒サ
イクル内のガス冷媒が冷却されて液化し、冷媒量調整タ
ンク１ｏを通って冷媒搬送装置１１に送られ、この冷媒
搬送装置１１によって接続゛配管Ｃを通って利用側熱交
換器１２へ送られて冷房して吸熱蒸発し、ガス化して接
続配管Ｃを通って第２補助熱交換器９に循環することに
なる。During cooling operation, the refrigerant cycle is indicated by the solid arrow in the figure. In the heat source side refrigerant cycle, high temperature, high pressure gas from the compressor 1 passes through the four-way valve 2, radiates heat in the heat source side heat exchanger 3, condenses and liquefies, and passes through the check valve 6. The heat source is depressurized by the cooling expansion valve 4 and evaporated by the first auxiliary heat exchanger 8, and the heat source is circulated through 2 to the compressor 1. At this time, the second auxiliary heat exchanger 9 of the refrigerant cycle on the user side
The first auxiliary heat exchanger 8 exchanges heat, and the gas refrigerant in the user-side refrigerant cycle is cooled and liquefied, and is sent to the refrigerant conveyance device 11 through the refrigerant amount adjustment tank 1o, and the refrigerant conveyance device 11, it is sent to the user-side heat exchanger 12 through the connecting pipe C, where it is cooled, endothermically evaporated, gasified, and circulated through the connecting pipe C to the second auxiliary heat exchanger 9.
一方、暖房運転時においては、図中破線矢印の冷媒サイ
クルとなり、熱源側冷媒サイクルでは、圧縮機１からの
高温高圧冷媒は熱源側四方７＋−２から第１補助交換器
８に送られ、放熱して凝縮液化し、逆止弁７から暖房用
減圧装置６で減圧し、熱源側熱交換器３で吸熱蒸発し熱
源側四方弁２を通って圧縮機１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９と前記第１補助熱
交換器８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Ｃを通って利用側熱交換
器１２へ送られ、暖房して放熱液化し接続配管Ｃを通っ
て冷媒搬送装置１１へ送られ、冷媒量調整タンク１０か
ら第２補助熱交換器９へ循環する。On the other hand, during heating operation, the refrigerant cycle is indicated by the dashed arrow in the figure, and in the heat source side refrigerant cycle, the high temperature and high pressure refrigerant from the compressor 1 is sent from the heat source side 7 + - 2 to the first auxiliary exchanger 8, and heat is radiated. It is condensed and liquefied, the pressure is reduced by the heating pressure reducing device 6 through the check valve 7, it is endothermically evaporated in the heat source side heat exchanger 3, and is circulated through the heat source side four-way valve 2 to the compressor 1. At this time, the second auxiliary heat exchanger 9 of the user-side refrigerant cycle and the first auxiliary heat exchanger 8 exchange heat, and the liquid refrigerant in the user-side refrigerant cycle is heated and gasified, and is used through the connecting pipe C. The refrigerant is sent to the side heat exchanger 12, heated, liquefied, and sent through the connecting pipe C to the refrigerant transport device 11, and circulated from the refrigerant amount adjustment tank 10 to the second auxiliary heat exchanger 9.
発明が解決しようとする課題
しかしながら上記のような構成では、利用側冷媒サイク
ルの冷媒搬送装置の能力は一定であシ、利用側ユニット
の負荷が変動しても利用側ユニットの能力は変化せず、
最終的には熱源側ユニットの運転停止をくり返すことに
なる。従って被空調室の室温変動が大きくなシネ快であ
るとともに、熱源側ユニットの能力に関係なく制御して
いるので効率が低下することになる。Problems to be Solved by the Invention However, in the above configuration, the capacity of the refrigerant transport device of the user-side refrigerant cycle is constant, and even if the load on the user-side unit changes, the capacity of the user-side unit does not change. ,
Eventually, the operation of the heat source unit will have to be stopped repeatedly. Therefore, the room temperature in the air-conditioned room is subject to large fluctuations, and the efficiency is reduced because the control is performed regardless of the capacity of the heat source side unit.
この課題を解決するために、圧縮機を能力制御形にする
ことも考えられるが、コスト的に高くなる課題を有して
いた。In order to solve this problem, it has been considered to make the compressor a capacity control type, but this has the problem of increasing cost.
本発明は、上記課題に鑑み、簡単な方法で利用側ユニッ
トの能力制御ができる冷暖房装置を提供するものである
３゜
課題を解決するだめの手段
上記課題を解決するために、本発明の冷暖房装置は、熱
源側冷媒サイクルと利用側冷媒サイクルの差圧を検出す
る差圧検出装置と、この差圧検出装置で検出した差圧で
冷媒搬送装置の能力を制御する制御装置を備えたもので
ある。In view of the above-mentioned problems, the present invention provides an air-conditioning and heating system that can control the capacity of a user unit in a simple manner. The device is equipped with a differential pressure detection device that detects the differential pressure between the heat source side refrigerant cycle and the usage side refrigerant cycle, and a control device that controls the capacity of the refrigerant conveyance device based on the differential pressure detected by the differential pressure detection device. be.
作 用
本発明は上記した構成によって、利用側冷媒サイクルの
負荷及び熱源側冷媒サイクルの能力に合った冷媒搬送装
置の能力とし、効率のよい利用側冷媒サイクルの冷媒循
環量とすることができることとなる。Effects The present invention has the above-described configuration, which allows the capacity of the refrigerant conveying device to match the load of the user-side refrigerant cycle and the capacity of the heat source-side refrigerant cycle, and the amount of refrigerant circulated in the user-side refrigerant cycle to be efficient. Become.
実施例
以下本発明の一実施例の冷暖房装置について、図面を参
照しながら説明する。第１図は本発明の実施例における
冷暖房装置の冷媒サイクルを示すものである。第１図に
おいて、冷媒搬送装置１１はインバータ１３によって能
力制御されている。EXAMPLE Hereinafter, a heating and cooling system according to an example of the present invention will be described with reference to the drawings. FIG. 1 shows a refrigerant cycle of a heating and cooling system according to an embodiment of the present invention. In FIG. 1, the capacity of the refrigerant conveying device 11 is controlled by an inverter 13.
また、１４は差圧検出装置で、熱源側冷媒サイクル内の
第１補助熱交換器８と四方弁２の間の冷媒圧力と利用側
冷媒サイクル内の冷媒搬送装置１１の前又は後との差力
を検出し、１５はこの差圧検出装置１４で検出した差圧
によって、インバータ１３の周波数を制御し、冷媒搬送
装置１１の能力を制御している。Further, 14 is a differential pressure detection device, which detects the difference between the refrigerant pressure between the first auxiliary heat exchanger 8 and the four-way valve 2 in the heat source side refrigerant cycle and the pressure before or after the refrigerant conveying device 11 in the user side refrigerant cycle. 15 controls the frequency of the inverter 13 and the capacity of the refrigerant conveyance device 11 based on the differential pressure detected by the differential pressure detection device 14.
その他は前記従来例と同じであり、ここでは同一符号を
用いて示し説明を省略する。またこの冷媒サイクルの動
作についても前記従来例と同じであシ詳細は省略するが
、熱源側冷媒サイクルの能力及び利用側ユニットｂの負
荷に合わせて、冷媒搬送装置１１の搬送能力を制御し、
利用側冷媒サイクルの冷媒循環量の制御によって、第２
補助熱交換器９と利用側熱交換器１２の熱交換能力を制
御し、利用側冷媒サイクルの能力を制御するものである
。The rest is the same as the conventional example, and the same reference numerals are used here to omit the explanation. The operation of this refrigerant cycle is also the same as that of the conventional example, and although the details are omitted, the transport capacity of the refrigerant transport device 11 is controlled in accordance with the capacity of the heat source side refrigerant cycle and the load of the user side unit b,
By controlling the refrigerant circulation amount of the user side refrigerant cycle, the second
It controls the heat exchange capacity of the auxiliary heat exchanger 9 and the utilization side heat exchanger 12, and controls the capacity of the utilization side refrigerant cycle.
また、熱源側冷媒サイクルの能力は、外気ｎ１１！度及
び第１補助熱交換器８の熱交換能力が第２補助熱交換器
９の熱交換能力に制御されるため、利用側冷媒サイクル
の能力にバランスすることになる。In addition, the capacity of the heat source side refrigerant cycle is outside air n11! Since the temperature and the heat exchange capacity of the first auxiliary heat exchanger 8 are controlled by the heat exchange capacity of the second auxiliary heat exchanger 9, they are balanced with the capacity of the user-side refrigerant cycle.
以上のように、本実施例によれば、熱源側冷媒サイクル
と利用側冷媒サイクルの差力を検出する差圧検出装置と
、この差圧検出装置で検出した差圧により、冷媒搬送装
置の能力を制御する制御装置を備えたことにより、熱源
側冷媒サイクルの能力及び利用側ユニットの負荷に合っ
た利用側冷媒サイクルの能力とすることができるので、
被空調室の温度が安定し快適性が向上するとともに、熱
源側ユニットの運転停止の回数が少なく、かつ効率アッ
プとなり省エネルギに寄与することができる。なお、利
用側ユニットが複数台の場合にも適用できることは言う
までもなく、また冷媒搬送装置の能力制御は台数制御で
も同じ効果が得られる。As described above, according to this embodiment, the capacity of the refrigerant conveyance device is determined by the differential pressure detection device that detects the differential force between the heat source side refrigerant cycle and the usage side refrigerant cycle, and the differential pressure detected by this differential pressure detection device. By providing a control device that controls the heat source side refrigerant cycle, the capacity of the user side refrigerant cycle can be adjusted to match the capacity of the heat source side refrigerant cycle and the load of the user side unit.
The temperature of the air-conditioned room is stabilized and comfort is improved, and the number of shutdowns of the heat source side unit is reduced, and efficiency is increased, contributing to energy savings. It goes without saying that this method can also be applied to a case where there are a plurality of units on the user side, and the same effect can be obtained by controlling the capacity of the refrigerant conveyance device by controlling the number of units.
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
媒サイクルの差圧を検出する差圧検出装置と、この差圧
検出装置で検出した差圧により冷媒搬送装置の能力を制
御する制御装置を備えたので、簡単な構成で熱源側ユニ
ット及び利用側ユニットの負荷に合った利用側冷媒サイ
クルの能力（冷媒循環量）とすることができるので、被
空調室の温度が安定し、快適性が向上するとともに、熱
源側ユニットの運転停止の回数が少なく、かつ効率が向
上する効果がある。Effects of the Invention As described above, the present invention includes a differential pressure detection device that detects the differential pressure between the heat source side refrigerant cycle and the usage side refrigerant cycle, and the ability of the refrigerant conveyance device to be controlled by the differential pressure detected by this differential pressure detection device. Since the control device is equipped with a control device, the capacity of the user-side refrigerant cycle (refrigerant circulation amount) can be adjusted to match the load of the heat source side unit and the user-side unit with a simple configuration, so the temperature of the air-conditioned room is stabilized. This has the effect of improving comfort, reducing the number of shutdowns of the heat source side unit, and improving efficiency.
第１図は本発明の一実施例における冷暖房装置の冷媒サ
イクル図、第２図は従来の冷暖房装置の冷媒サイクル図
である。
３・・・・・熱源側熱交換器、８・・・・第１補助熱交
換器、９・・・・・・第２補助熱交換器、１１・・・・
・・冷媒搬送装置、１２・・・・・・利用側熱交換器、
１４・・・・・・差圧検出装置、１６・・・・・・制御
装置。
代理人の氏名 弁理士 中 尾 敏 男 ほか１名３−
一慕ｙ！績ＩＪＩ支挟五
第１図FIG. 1 is a refrigerant cycle diagram of a heating and cooling system according to an embodiment of the present invention, and FIG. 2 is a diagram of a refrigerant cycle of a conventional heating and cooling system. 3... Heat source side heat exchanger, 8... First auxiliary heat exchanger, 9... Second auxiliary heat exchanger, 11...
... Refrigerant conveyance device, 12 ... User side heat exchanger,
14... Differential pressure detection device, 16... Control device. Name of agent: Patent attorney Toshio Nakao and 1 other person3-
I love you! Performance IJI support figure 1
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補助熱交換器と能力制御型の冷媒搬送装置お
よび利用側熱交換器を環状に連接した利用側冷媒サイク
ルと、前記熱源側冷媒サイクルと利用側冷媒サイクルの
差圧を検出する差圧検出装置と、この差圧検出装置で検
出した差圧により前記冷媒搬送装置の能力を制御する制
御装置とを備えたことを特徴とする冷暖房装置。A heat source side refrigerant cycle is formed by connecting a compressor, a heat source side four-way valve, a heat source side heat exchanger, a pressure reducing device, and a first auxiliary heat exchanger in an annular manner, and this first auxiliary heat exchanger is integrally formed. A user-side refrigerant cycle in which a second auxiliary heat exchanger to be exchanged, a capacity-controlled refrigerant transfer device, and a user-side heat exchanger are connected in an annular manner, and a difference that detects a differential pressure between the heat source-side refrigerant cycle and the user-side refrigerant cycle. A heating and cooling device comprising: a pressure detection device; and a control device that controls the capacity of the refrigerant conveying device based on the differential pressure detected by the differential pressure detection device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63138851A JPH01306758A (en) | 1988-06-06 | 1988-06-06 | Coolor-heater |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63138851A JPH01306758A (en) | 1988-06-06 | 1988-06-06 | Coolor-heater |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH01306758A true JPH01306758A (en) | 1989-12-11 |
Family
ID=15231648
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63138851A Pending JPH01306758A (en) | 1988-06-06 | 1988-06-06 | Coolor-heater |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH01306758A (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5134445A (en) * | 1974-09-18 | 1976-03-24 | Sanyo Electric Co | HIITOHONPUSOCHI |
| JPS588956A (en) * | 1981-07-10 | 1983-01-19 | 株式会社システム・ホ−ムズ | Heat pump type air conditioner |
| JPS62116846A (en) * | 1985-11-15 | 1987-05-28 | Hitachi Ltd | Control device for the number of operating refrigerating machines |
-
1988
- 1988-06-06 JP JP63138851A patent/JPH01306758A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5134445A (en) * | 1974-09-18 | 1976-03-24 | Sanyo Electric Co | HIITOHONPUSOCHI |
| JPS588956A (en) * | 1981-07-10 | 1983-01-19 | 株式会社システム・ホ−ムズ | Heat pump type air conditioner |
| JPS62116846A (en) * | 1985-11-15 | 1987-05-28 | Hitachi Ltd | Control device for the number of operating refrigerating machines |
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