JPH03125863A - Refrigerating cycle unit with two stage compression - Google Patents
Refrigerating cycle unit with two stage compressionInfo
- Publication number
- JPH03125863A JPH03125863A JP26240489A JP26240489A JPH03125863A JP H03125863 A JPH03125863 A JP H03125863A JP 26240489 A JP26240489 A JP 26240489A JP 26240489 A JP26240489 A JP 26240489A JP H03125863 A JPH03125863 A JP H03125863A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- gas
- condenser
- liquid
- outlet
- 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
- 230000006835 compression Effects 0.000 title claims abstract description 31
- 238000007906 compression Methods 0.000 title claims abstract description 31
- 239000003507 refrigerant Substances 0.000 claims abstract description 63
- 239000007788 liquid Substances 0.000 claims abstract description 26
- 238000005057 refrigeration Methods 0.000 claims description 21
- 238000001816 cooling Methods 0.000 claims description 4
- 238000009835 boiling Methods 0.000 abstract description 26
- 238000000034 method Methods 0.000 abstract 1
- 239000000203 mixture Substances 0.000 description 5
- 230000002159 abnormal effect Effects 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 238000000926 separation method Methods 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
- F25B2400/13—Economisers
-
- 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
- F25B2400/23—Separators
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は空気調和機等に用いられる冷凍サイクルに関し
特に２段圧縮冷凍サイクル装置の改良に関する。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a refrigeration cycle used in an air conditioner or the like, and particularly relates to an improvement in a two-stage compression refrigeration cycle device.
従来の技術
従来 圧縮機を２台直列に接続して冷媒を２段階に圧縮
する２段圧縮冷凍サイクル１よ 圧縮比が高くなる運転
条件における圧縮効率の向上を目的として採用されてい
も
第２図は従来の２段圧縮冷凍サイクルを示すものであり
、低段側圧縮機１より吐出された冷媒と、凝縮器３を経
て補助絞り装置７を出た冷媒とは中間冷却器５で直接接
触による熱交換を行うとともへ 凝縮器３より、中間冷
却器５内を貫通し 主絞り装置６を介して蒸発器４に液
冷媒を導く配管と熱交換して冷却作用をなし ガス化し
た冷媒は高段側圧縮機２の吸入側に導かれる。Conventional technology Conventional Two-stage compression refrigeration cycle 1, in which two compressors are connected in series to compress the refrigerant in two stages, is adopted for the purpose of improving compression efficiency under operating conditions where the compression ratio is high. shows a conventional two-stage compression refrigeration cycle, in which the refrigerant discharged from the low-stage compressor 1 and the refrigerant exiting the auxiliary throttling device 7 via the condenser 3 come into direct contact with each other in the intercooler 5. The gasified refrigerant performs a cooling effect by exchanging heat with the pipe that leads the liquid refrigerant from the condenser 3 through the intercooler 5 to the evaporator 4 via the main throttling device 6. It is guided to the suction side of the high-stage compressor 2.
このように ２段圧縮冷凍サイクルを採用して中間冷却
を行うことにより、低外気温時の暖房や給湯運転時等の
圧縮比が大きくなる運転条件において、高段側圧縮機の
吐出冷媒ガス温度の異常上昇を防止するととも鳳 冷媒
の圧縮に要する動力を節約することができるものであム
また このような２段圧縮冷凍サイクルの性能をさら
に向上させるた人 高沸点冷媒（Ｒ１１、Ｒ１１４など
）と低沸点冷媒（Ｒ１２、Ｒ２２など）を混合した非共
沸混合冷媒を用いる提案もされている。In this way, by adopting a two-stage compression refrigeration cycle to perform intermediate cooling, the temperature of the refrigerant gas discharged from the high-stage compressor can be reduced under operating conditions where the compression ratio is high, such as during heating or hot water supply operations at low outside temperatures. It is possible to prevent an abnormal rise in refrigerant and to save the power required to compress the refrigerant.It is also possible to further improve the performance of such two-stage compression refrigeration cycles. It has also been proposed to use a non-azeotropic mixed refrigerant, which is a mixture of a low boiling point refrigerant (R12, R22, etc.) and a low boiling point refrigerant.
発明が解決しようとする課題
しかしながら上記従来例のようへ 単に２段圧縮冷凍サ
イクルに非共沸混合冷媒を用いただけで（友 高沸点冷
媒は高温でも圧力が比較的低く、低沸点冷媒は低温でも
圧力がそれほど低くならないといった 各冷媒の特長的
な性質を活かすことができ哄 性能改善の効果が小さい
という問題があつ九
課題を解決するための手段
本発明の２段圧縮冷凍サイクル装置（よ 高段側圧縮風
第１凝縮銖 第２凝縮麻 中間冷却銖主絞り装置 蒸
発器 低段側圧縮機から非共沸混合冷媒を封入する主回
路を構成し 前記第１凝縮器の出口側に気液分離器を設
け、この気液分離器のガス側出口は前記第２１縮器に接
続し また液側出口は補助絞り装置を介して中間冷却器
に接続し 高段側圧縮機に吸入される低段側圧縮機の吐
出冷風 および第２凝縮器で凝縮された液冷媒を冷却で
きる構成としたものである。Problems to be Solved by the Invention However, if a non-azeotropic mixed refrigerant is simply used in a two-stage compression refrigeration cycle as in the conventional example described above, high boiling point refrigerants have relatively low pressure even at high temperatures, and low boiling point refrigerants have relatively low pressure even at low temperatures. The two-stage compression refrigeration cycle device of the present invention (high-stage compression refrigeration cycle device) Side compression air 1st condensing tube 2nd condensing tube Intercooled condenser main throttling device Evaporator Configures the main circuit that encloses the non-azeotropic mixed refrigerant from the low-stage compressor, and separates gas and liquid at the outlet side of the first condenser. The gas-side outlet of this gas-liquid separator is connected to the 21st condenser, and the liquid-side outlet is connected to the intercooler via an auxiliary throttling device, and the low-stage gas is sucked into the high-stage compressor. It is configured to cool the cold air discharged from the side compressor and the liquid refrigerant condensed in the second condenser.
作用
第１凝縮器の出口に設けた気液分離器よって、封入され
た非共沸混合冷媒のうち凝縮し易い高沸点冷媒を液側出
口から抽出し 中間冷却器で蒸発させて高段側圧縮機に
吸入させることにより、高温となる凝縮器側には圧力を
低くできる高沸点冷媒を多くすることができ、逆風 低
温となる蒸発器側には圧力がそれほど低くならなμ 高
沸点冷媒を抽出されて低沸点冷媒の濃度が高くなった混
合冷媒を循環させることができるので、 ２段圧縮冷凍
サイクル全体の圧縮比を小さくし 高段側および低段側
圧縮機での消費動力を低減することができ、成績係数の
向上が図れるものであ一実施例
以上 本発明の一実施例を添付図面に基づいて説明する
。第１図は本発明の一実施例における２段圧縮冷凍サイ
クル装置を示すものであり、 ８は高段側圧縮風 ９は
第１凝縮銖 １０は第２凝縮銖 １１は中間冷却器 １
２は主絞り装置 １３は蒸発器 １４は低段側圧縮機で
あり、これらを順次配管接続することにより、 ２段圧
縮冷凍サイクルの主回路を構成している。また 第１凝
縮器９の出口側には気液分離器１５が設けられ この気
液分離器１５のガス側出口は第２凝縮器へ また液側出
口は補助絞り装置１６を介して中間冷却器ｌｌへ それ
ぞれ接続されていも 中間冷却器１１は低段側圧縮機１
４の吐出側および高段側圧縮機８の吸入側とも接続され
ており、高段側圧縮機８に吸入されるガス冷媒を冷却で
きる構成としている。また この中間冷却器１１の内部
を第２凝縮器１０出口と主絞り装置１２を接続する配管
１７が貫通しており、第２凝縮器１０で凝縮された液冷
媒をさらに冷却できる構成としていもこのような２段圧
縮冷凍サイクル装置において、高沸点冷媒として例えば
Ｒ１１４、低沸点冷媒冷媒として例えばＲ２２を混合し
た非共沸混合冷媒を封入して、運転する場合の動作につ
いて説明する。The gas-liquid separator installed at the outlet of the first condenser extracts the high-boiling refrigerant that is easily condensed from the enclosed non-azeotropic mixed refrigerant from the liquid side outlet, evaporates it in the intercooler, and compresses it on the high stage side. By inhaling it into the machine, it is possible to increase the high boiling point refrigerant that can lower the pressure to the condenser side, where the temperature is high, and the high boiling point refrigerant can be extracted to the evaporator side, where the temperature is high, so that the pressure will not be so low. This allows the refrigerant mixture with a high concentration of low-boiling point refrigerant to be circulated, reducing the compression ratio of the entire two-stage compression refrigeration cycle and reducing power consumption in the high-stage and low-stage compressors. EMBODIMENT OF THE INVENTION One embodiment of the present invention will be described based on the accompanying drawings. FIG. 1 shows a two-stage compression refrigeration cycle device according to an embodiment of the present invention, in which 8 is a high-stage compressed air, 9 is a first condensing tank, 10 is a second condensing tank, 11 is an intercooler 1
2 is a main throttling device, 13 is an evaporator, and 14 is a low-stage compressor, which are connected in sequence through piping to constitute a main circuit of a two-stage compression refrigeration cycle. Further, a gas-liquid separator 15 is provided on the outlet side of the first condenser 9, and the gas-side outlet of this gas-liquid separator 15 is connected to the second condenser, and the liquid-side outlet is connected to the intercooler via an auxiliary throttling device 16. Even if they are connected to ll, the intercooler 11 is connected to the lower stage compressor 1.
4 and the suction side of the high-stage compressor 8, so that the gas refrigerant sucked into the high-stage compressor 8 can be cooled. In addition, a pipe 17 that connects the outlet of the second condenser 10 and the main throttling device 12 passes through the interior of the intercooler 11, so that the liquid refrigerant condensed in the second condenser 10 can be further cooled. In such a two-stage compression refrigeration cycle device, the operation will be described when a non-azeotropic mixed refrigerant mixture of R114 as a high boiling point refrigerant and R22 as a low boiling point refrigerant is sealed and operated.
運転開始前は冷凍サイクル内の混合冷媒の組成Ｃ戴
封入されたままの組成となっており、運転を開始するこ
とにより、高段側圧縮機８より吐出された高温高圧の冷
媒ガス？１ 第１凝縮器９で冷却され 混合冷媒のへ
凝縮し易い高沸点冷媒（Ｒ１１４）が主に凝縮液化し
たの叙 気液分離器１５に導かれる。この気液分離器１
５の上部に設けたガス側出口より、低沸点冷媒（Ｒ２２
）の濃度の高いガス冷媒が第２凝縮器１０に入り、ここ
で完全に凝縮液化する。Before starting operation, the composition of the mixed refrigerant in the refrigeration cycle is C.
It has the same composition as the sealed one, and when the operation starts, high-temperature, high-pressure refrigerant gas is discharged from the high-stage compressor 8. 1. The high boiling point refrigerant (R114), which is easily condensed, is cooled in the first condenser 9 and is led to the gas-liquid separator 15, where it is mainly condensed and liquefied. This gas-liquid separator 1
A low boiling point refrigerant (R22
) enters the second condenser 10 where it is completely condensed and liquefied.
一方、気液分離器１５の底部に設けた液側出口より、抽
出された高沸点冷媒（Ｒ，１１４）の濃度の高い液冷媒
（よ 補助絞り装置１６で中間圧力まで減圧膨張して、
中間冷却器１１に導かれる。ここで、配管１７と熱交換
して第２凝縮器で凝縮された低沸点冷媒（Ｒ２２）の濃
度の高い液冷媒を冷却すると同時に 低段側圧縮機１４
より吐出されたガス冷媒と直接接触による熱交換により
、蒸発気化して混合された状態で高段側圧縮機８に吸入
されも
さらに 配管１７で十分過冷却された低沸点冷媒（Ｒ２
２）の濃度の高い冷媒Ｃヨ 主絞り装置１２により、
蒸発圧力まで減圧膨張し 蒸発器１３に導かれる。ここ
で、外部の熱源により蒸発気化したの坂 低段側圧縮機
１４に吸入され 中間圧力まで圧縮されて、前述したよ
うに中間冷却器ｌｌに導かれるのである。On the other hand, from the liquid side outlet provided at the bottom of the gas-liquid separator 15, the extracted high-boiling point refrigerant (R, 114) is decompressed and expanded to an intermediate pressure by the auxiliary throttling device 16.
It is guided to an intercooler 11. Here, the liquid refrigerant with a high concentration of low boiling point refrigerant (R22) condensed in the second condenser by exchanging heat with the pipe 17 is cooled, and at the same time, the low-stage compressor 14
Through heat exchange through direct contact with the gas refrigerant discharged from the gas refrigerant, the evaporated and mixed state is sucked into the high stage compressor 8, and the low boiling point refrigerant (R2
2) Highly concentrated refrigerant C
It expands under reduced pressure to the evaporation pressure and is led to the evaporator 13. Here, the gas that has been evaporated by an external heat source is sucked into the low-stage compressor 14, compressed to an intermediate pressure, and guided to the intercooler 11 as described above.
このように 本実施例の２段圧縮冷凍サイクルで（上
中間冷却器１１において低段側圧縮機１３の吐出冷媒ガ
スの中間冷却を行うことにより、低外気温時の暖房や給
湯運転時等の圧縮比が大きくなる運転条件において、高
段側圧縮機８の吐出冷媒ガス温度の異常上昇を防止する
ことができるととも番ヘ 第１凝縮器９の出口側に設
けられた気液分離器１５の作用により、封入された非共
沸混合冷媒を高沸点冷媒（Ｒ１１４）と低沸点冷媒（Ｒ
２２）とに分離し 高温となる凝縮器側には圧力を低く
できる高沸点冷媒（Ｒ１１４）を、低温となる蒸発器側
には圧力がそれほど低くならない低沸点冷媒（Ｒ２２）
を多くすることができ、そのため２段圧縮冷凍サイクル
全体の圧縮比を小さくでき、高段側および低段側圧縮機
８、１４での消費動力を低減することができ、成績係数
の向上が図れるものである。In this way, in the two-stage compression refrigeration cycle of this example (upper
By performing intercooling of the refrigerant gas discharged from the low-stage compressor 13 in the intercooler 11, the high-stage compressor 8 can be used under operating conditions where the compression ratio is high, such as during heating or hot water supply operation at low outside temperatures. By the action of the gas-liquid separator 15 provided on the outlet side of the first condenser 9, the enclosed non-azeotropic mixed refrigerant can be separated from the high boiling point. Refrigerant (R114) and low boiling point refrigerant (R
22) The high boiling point refrigerant (R114), which can lower the pressure, is placed on the condenser side, where the temperature is high, and the low boiling point refrigerant (R22), which does not lower the pressure so much, on the evaporator side, where the temperature is low.
Therefore, the compression ratio of the entire two-stage compression refrigeration cycle can be reduced, the power consumption in the high-stage and low-stage compressors 8 and 14 can be reduced, and the coefficient of performance can be improved. It is something.
な耘 本実施例では 高沸点冷媒としてＲ１１４、低沸
点冷媒としてＲ２２を用いて説明したカミ本発明はこれ
に限らず、他の非共沸混合冷媒系を用いる場合にも適応
できることは明かである。In this embodiment, R114 is used as the high boiling point refrigerant and R22 is used as the low boiling point refrigerant.It is clear that the present invention is not limited to this, but can also be applied to cases where other non-azeotropic mixed refrigerant systems are used. .
また 本実施例で（上 高段側圧線区 低段側圧縮機の
２台の圧縮機を用いて説明したカミ 本発明はこれに限
らず、 ２つの圧縮機構を内蔵する１台の圧縮機を高段
（１ｔｌＬ 低段側に使い分ける場合にも適応できる
ことは明らかである。In addition, in this embodiment, the explanation is made using two compressors (upper high stage side pressure line section and low stage side compressor). It is clear that it can also be applied to the case where it is used separately for the high stage (1tlL and low stage side).
発明の効果
以上の説明より明らかなようζへ 本発明の２段圧縮冷
凍サイクル装置（よ 低段側圧縮機の吐出冷媒ガスの中
間冷却を行うことができるので、低外気温時の暖房や給
湯運転時等の圧縮比が大きくなる運転条件において、高
段側圧縮機の吐出冷媒ガス温度の異常上昇を防止するこ
とができるととも顛 高温となる凝縮器側には圧力を低
くできる高沸点冷媒を、低温となる蒸発器側には圧力が
それほど低くならない低沸点冷媒をそれぞれ多くするこ
とができるので、 ２段圧縮冷凍サイクル全体の圧縮比
を小さくよ 高段側および低段側圧縮機での消費動力を
低減することができ、成績係数の向上が図れるものであ
る。Effects of the Invention As is clear from the above explanation, the two-stage compression refrigeration cycle device of the present invention (as shown in Fig. Under operating conditions such as when the compression ratio is high during operation, it is possible to prevent an abnormal rise in the temperature of the refrigerant gas discharged from the high-stage compressor. Since it is possible to increase the amount of low-boiling point refrigerant whose pressure does not become so low on the evaporator side, where the temperature is low, the compression ratio of the entire two-stage compression refrigeration cycle can be reduced. Power consumption can be reduced and the coefficient of performance can be improved.
第１図は本発明の一実施例の２段圧縮冷凍サイクルの構
成＠ 第２図は従来例の２段圧縮冷凍サイクルの構成図
である。
８・・・高段側圧縮１１ｉ１９・・・第１凝縮鳳 １０
・・・第２凝縮鳳 １１・・・中間冷却ｌＬ１２・・・
主絞り装置１３・・・蒸発器 １４・・・低段側圧縮機
１５・・・気液分離縁 １６・・・補助絞り装置FIG. 1 is a configuration diagram of a two-stage compression refrigeration cycle according to an embodiment of the present invention; FIG. 2 is a configuration diagram of a conventional two-stage compression refrigeration cycle. 8...High stage side compression 11i19...1st condensation holder 10
...Second condensation 11...Intermediate cooling 1L12...
Main throttling device 13... Evaporator 14... Low stage compressor 15... Gas-liquid separation edge 16... Auxiliary throttling device
Claims (1)
主絞り装置、蒸発器、低段側圧縮機から非共沸混合冷媒
を封入する主回路を構成し、前記第１凝縮器の出口側に
気液分離器を設け、この気液分離器のガス側出口は前記
第２凝縮器に接続し、液側出口は補助絞り装置を介して
前記中間冷却器に接続し、前記高段側圧縮機に吸入され
る前記低段側圧縮機の吐出冷媒および前記第２凝縮器で
凝縮された液冷媒を冷却できる構成としたことを特徴と
する２段圧縮冷凍サイクル装置。High-stage compressor, first condenser, second condenser, intercooler,
A main circuit is configured in which a non-azeotropic mixed refrigerant is sealed from the main throttling device, evaporator, and low-stage compressor, and a gas-liquid separator is provided on the outlet side of the first condenser. The side outlet is connected to the second condenser, and the liquid side outlet is connected to the intercooler via an auxiliary throttling device, and the refrigerant discharged from the low stage compressor and the refrigerant discharged from the low stage compressor are sucked into the high stage compressor. A two-stage compression refrigeration cycle device characterized by having a configuration capable of cooling the liquid refrigerant condensed in the second condenser.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1262404A JP2712644B2 (en) | 1989-10-06 | 1989-10-06 | Two-stage compression refrigeration cycle device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1262404A JP2712644B2 (en) | 1989-10-06 | 1989-10-06 | Two-stage compression refrigeration cycle device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03125863A true JPH03125863A (en) | 1991-05-29 |
| JP2712644B2 JP2712644B2 (en) | 1998-02-16 |
Family
ID=17375310
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1262404A Expired - Fee Related JP2712644B2 (en) | 1989-10-06 | 1989-10-06 | Two-stage compression refrigeration cycle device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2712644B2 (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2020248589A1 (en) * | 2019-06-14 | 2020-12-17 | 李华玉 | Reverse single working medium steam combined cycle |
| WO2020248591A1 (en) * | 2019-06-13 | 2020-12-17 | 李华玉 | Reverse single-working-media steam combined cycle |
| WO2020248588A1 (en) * | 2019-06-14 | 2020-12-17 | 李华玉 | Reverse single working medium steam combined cycle |
| WO2020248590A1 (en) * | 2019-06-13 | 2020-12-17 | 李华玉 | Reverse single-working-media steam combined cycle |
| WO2021047125A1 (en) * | 2019-09-10 | 2021-03-18 | 李华玉 | Reverse single-working-medium steam combined cycle |
| WO2021068431A1 (en) * | 2019-10-08 | 2021-04-15 | 李华玉 | Single-working-medium combined cycle heat pump device |
| WO2021072988A1 (en) * | 2019-10-16 | 2021-04-22 | 李华玉 | Reverse single-working-medium steam combined cycle and single-working-medium combined cycle heat pump device |
| WO2021072992A1 (en) * | 2019-10-17 | 2021-04-22 | 李华玉 | Single working medium combined circulation heat pump device |
| WO2021072990A1 (en) * | 2019-10-17 | 2021-04-22 | 李华玉 | Single-working medium combined cycle heat pump device |
| WO2021072991A1 (en) * | 2019-10-15 | 2021-04-22 | 李华玉 | Single-working medium combined cycle heat pump device |
| WO2022062272A1 (en) * | 2020-09-27 | 2022-03-31 | 李华玉 | Regenerative thermodynamic cycle and novel regenerative mechanical compression-type heat pump |
| WO2022062270A1 (en) * | 2020-09-22 | 2022-03-31 | 李华玉 | Recuperative thermodynamic cycle and recuperative gas thermal power apparatus |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5213554U (en) * | 1975-07-18 | 1977-01-31 | ||
| JPS5885066A (en) * | 1981-11-16 | 1983-05-21 | 松下電器産業株式会社 | Heat pump device |
-
1989
- 1989-10-06 JP JP1262404A patent/JP2712644B2/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5213554U (en) * | 1975-07-18 | 1977-01-31 | ||
| JPS5885066A (en) * | 1981-11-16 | 1983-05-21 | 松下電器産業株式会社 | Heat pump device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2599865B (en) * | 2019-06-13 | 2023-03-29 | Li Huayu | Reversed single-working-medium vapor combined cycle |
| WO2020248591A1 (en) * | 2019-06-13 | 2020-12-17 | 李华玉 | Reverse single-working-media steam combined cycle |
| GB2599865A (en) * | 2019-06-13 | 2022-04-13 | Li Huayu | Reverse single-working-media steam combined cycle |
| WO2020248590A1 (en) * | 2019-06-13 | 2020-12-17 | 李华玉 | Reverse single-working-media steam combined cycle |
| GB2601642A (en) * | 2019-06-13 | 2022-06-08 | Li Huayu | Reverse single-working-media steam combined cycle |
| GB2601642B (en) * | 2019-06-13 | 2023-03-29 | Li Huayu | Reverse single-working-media steam combined cycle |
| GB2599866B (en) * | 2019-06-14 | 2023-03-29 | Li Huayu | Reversed single-working-medium vapor combined cycle |
| GB2599867A (en) * | 2019-06-14 | 2022-04-13 | Li Huayu | Reverse single working medium steam combined cycle |
| WO2020248589A1 (en) * | 2019-06-14 | 2020-12-17 | 李华玉 | Reverse single working medium steam combined cycle |
| US20220364774A1 (en) * | 2019-06-14 | 2022-11-17 | Huayu Li | Reversed single-working-medium vapor combined cycle |
| US20220282890A1 (en) * | 2019-06-14 | 2022-09-08 | Huayu Li | Reversed single-working-medium vapor combined cycle |
| GB2599866A (en) * | 2019-06-14 | 2022-04-13 | Li Huayu | Reverse single working medium steam combined cycle |
| WO2020248588A1 (en) * | 2019-06-14 | 2020-12-17 | 李华玉 | Reverse single working medium steam combined cycle |
| WO2021047125A1 (en) * | 2019-09-10 | 2021-03-18 | 李华玉 | Reverse single-working-medium steam combined cycle |
| WO2021068431A1 (en) * | 2019-10-08 | 2021-04-15 | 李华玉 | Single-working-medium combined cycle heat pump device |
| WO2021072991A1 (en) * | 2019-10-15 | 2021-04-22 | 李华玉 | Single-working medium combined cycle heat pump device |
| WO2021072988A1 (en) * | 2019-10-16 | 2021-04-22 | 李华玉 | Reverse single-working-medium steam combined cycle and single-working-medium combined cycle heat pump device |
| WO2021072990A1 (en) * | 2019-10-17 | 2021-04-22 | 李华玉 | Single-working medium combined cycle heat pump device |
| WO2021072992A1 (en) * | 2019-10-17 | 2021-04-22 | 李华玉 | Single working medium combined circulation heat pump device |
| WO2022062270A1 (en) * | 2020-09-22 | 2022-03-31 | 李华玉 | Recuperative thermodynamic cycle and recuperative gas thermal power apparatus |
| WO2022062272A1 (en) * | 2020-09-27 | 2022-03-31 | 李华玉 | Regenerative thermodynamic cycle and novel regenerative mechanical compression-type heat pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2712644B2 (en) | 1998-02-16 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |