JPH03182638A - Gas turbine driven refrigerator - Google Patents
Gas turbine driven refrigeratorInfo
- Publication number
- JPH03182638A JPH03182638A JP32226389A JP32226389A JPH03182638A JP H03182638 A JPH03182638 A JP H03182638A JP 32226389 A JP32226389 A JP 32226389A JP 32226389 A JP32226389 A JP 32226389A JP H03182638 A JPH03182638 A JP H03182638A
- Authority
- JP
- Japan
- Prior art keywords
- gas turbine
- refrigerant
- heat exchanger
- refrigerator
- intake air
- 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 43
- 238000001704 evaporation Methods 0.000 claims abstract description 6
- 239000007788 liquid Substances 0.000 claims description 9
- 239000007789 gas Substances 0.000 abstract description 42
- 238000001816 cooling Methods 0.000 abstract description 17
- 239000000446 fuel Substances 0.000 abstract description 7
- 238000002485 combustion reaction Methods 0.000 abstract description 5
- 230000008020 evaporation Effects 0.000 abstract description 5
- 239000000567 combustion gas Substances 0.000 abstract description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 7
- 238000010586 diagram Methods 0.000 description 6
- 239000000498 cooling water Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Landscapes
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明はガスタービンで駆動するガスタービン駆動冷凍
機に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a gas turbine-driven refrigerator that is driven by a gas turbine.
〔従来技術及び発明が解決しようとする課題〕ガスター
ビン駆動冷凍機においては、ガスタービンの出力は入口
空気温度が上昇すると燃焼室への空気温度が上昇する。[Prior Art and Problems to be Solved by the Invention] In a gas turbine-driven refrigerator, the output of the gas turbine increases as the temperature of the inlet air increases, the temperature of the air flowing into the combustion chamber increases.
そのため、タービン入口温度を一定値以下に抑える量の
燃料しか注入できないという問題がある。Therefore, there is a problem that only an amount of fuel can be injected to keep the turbine inlet temperature below a certain value.
一方、ガスタービンの入口空気温度は熱交換器により冷
却するのに、通常用いられている水−空気熱交換器では
、熱交換における相対温度が小さいため、伝熱面積が大
きくなるという欠点がある。また、伝熱面積の増加は、
ガスタービンの吸気側の損失増加をもたらし、ガスター
ビンの有効出力が減少となるという問題もある。On the other hand, although the inlet air temperature of a gas turbine is cooled by a heat exchanger, the normally used water-air heat exchanger has the disadvantage that the heat transfer area becomes large because the relative temperature during heat exchange is small. . In addition, the increase in heat transfer area is
There is also the problem that the loss on the intake side of the gas turbine increases and the effective output of the gas turbine decreases.
本発明は上述の点に鑑みてなされたもので、上記問題点
を除去し、ガスタービンの吸気空気を冷却する熱交換器
の伝熱面積が小さくでき、且つガスタービンの吸気側の
損失増加をもたらすことなく、ガスタービンの有効出力
が減少することのないガスタービン駆動冷凍機を提供す
ることにあ上記課題を解決するため本発明は、ガスター
ビン駆動冷凍機において、ガスタービン吸気口に設けた
熱交換器に通常導く７℃の冷水のかわりに、冷凍機の凝
縮器出口の液体状の冷媒の一部を導き、該冷媒の蒸発に
よりガスタービンの吸気空気を冷却し、該冷媒を冷凍機
に戻すように構成したことを特徴とする。The present invention has been made in view of the above-mentioned points, and eliminates the above-mentioned problems, reduces the heat transfer area of the heat exchanger that cools the intake air of the gas turbine, and reduces the increase in loss on the intake side of the gas turbine. An object of the present invention is to provide a gas turbine-driven refrigerator in which the effective output of the gas turbine is not reduced. Instead of the 7°C cold water normally introduced into the heat exchanger, a portion of the liquid refrigerant at the outlet of the condenser of the refrigerator is introduced, and the evaporation of the refrigerant cools the intake air of the gas turbine. It is characterized by being configured so that it returns to .
〔作用〕
上記の如く凝縮器出口の液体状の冷媒の蒸発によりガス
タービンの吸気生気を冷却するようにしたので、吸気空
気が冷凍機の冷媒により直接冷却されるので熱交換にお
ける相対温度を大きくでき、熱交換器の伝熱面積を小さ
くすることができ、ガスタービン吸気側の損失を減少さ
せることができる。[Function] As described above, the intake air of the gas turbine is cooled by the evaporation of the liquid refrigerant at the condenser outlet, so the relative temperature during heat exchange is increased because the intake air is directly cooled by the refrigerant of the refrigerator. Therefore, the heat transfer area of the heat exchanger can be reduced, and the loss on the gas turbine intake side can be reduced.
以下、本発明の実施例を図面に基づいて説明する。 Embodiments of the present invention will be described below based on the drawings.
第１図は本発明のガスタービン駆動冷凍機のシステム構
成を示す図である。同図において、１はガスタービンの
吸気ダクト、２はガスタービンの圧縮機、３はガスター
ビンの燃焼室、４はガスタービンの出力タービン、５は
ガスタービンの排気ダクト、６は冷凍機の圧縮機、７は
冷凍機の凝縮器、８は冷凍機の蒸発器、９は冷凍機の冷
水配管、１０は冷媒分岐配管、１１は冷凍機の冷却水配
管、１２はガスタービンの燃料制御弁、１３は冷媒流量
制御弁、１４は吸気冷却熱交換器、１５は冷凍機膨張弁
、１６はガスタービンの排気温度検出器、１７壮ガスタ
一ビン入口吸気温度検知器である。FIG. 1 is a diagram showing the system configuration of a gas turbine-driven refrigerator according to the present invention. In the figure, 1 is the intake duct of the gas turbine, 2 is the compressor of the gas turbine, 3 is the combustion chamber of the gas turbine, 4 is the output turbine of the gas turbine, 5 is the exhaust duct of the gas turbine, and 6 is the compressor of the refrigerator. 7 is a condenser of the refrigerator, 8 is an evaporator of the refrigerator, 9 is a cold water pipe of the refrigerator, 10 is a refrigerant branch pipe, 11 is a cooling water pipe of the refrigerator, 12 is a gas turbine fuel control valve, 13 is a refrigerant flow rate control valve, 14 is an intake air cooling heat exchanger, 15 is a refrigerator expansion valve, 16 is a gas turbine exhaust temperature detector, and 17 is an intake air temperature detector at the gas turbine inlet.
吸気ダクト１から吸入された空気（温度３２’Ｃ）は吸
気冷却熱交換器１４で冷却され（温度１５°Ｃ）、圧縮
機２に入り圧縮される。燃焼室３には圧縮ｗ＆２からの
圧縮空気と燃料制御弁１２を通して燃料が注入され、燃
焼ガスが出力タービン４に送り出され、排気ダクト５を
通して排ガスは排出される。Air (temperature: 32'C) taken in from the intake duct 1 is cooled by the intake cooling heat exchanger 14 (temperature: 15°C), enters the compressor 2, and is compressed. Compressed air from compressed w&2 and fuel are injected into the combustion chamber 3 through the fuel control valve 12, combustion gas is sent to the power turbine 4, and exhaust gas is exhausted through the exhaust duct 5.
出力タービン４の回転により、圧縮機６が回転され、該
圧縮機６により圧縮された冷媒は凝縮器７に入り、冷却
水配管１１を流れる冷却水（温度３２°Ｃ）に熱を与え
（温度３７°Ｃに上昇）、凝縮する。凝縮した液体状の
冷媒は冷凍機膨張弁１５を通して蒸発器８に送られる。The rotation of the output turbine 4 rotates the compressor 6, and the refrigerant compressed by the compressor 6 enters the condenser 7, which gives heat to the cooling water (temperature 32°C) flowing through the cooling water pipe 11 (temperature 37°C) and condense. The condensed liquid refrigerant is sent to the evaporator 8 through the refrigerator expansion valve 15.
蒸発器８では冷水配管９に流れ込む冷水（温度１２°Ｃ
）を液体状の冷媒の蒸発熱（気化熱）で冷却して（温度
７°Ｃ）送り出す。In the evaporator 8, cold water (temperature 12°C) flows into the cold water pipe 9.
) is cooled (at a temperature of 7°C) by the heat of evaporation of the liquid refrigerant and sent out.
一方、凝縮器７の液体状冷媒は冷媒分岐配管１０でその
一部が分離され、冷媒流量制御弁１３を通して吸気冷却
熱交換器１４に送られ、吸気冷却熱交換器１４において
、冷媒の蒸発により吸気ダクト１から吸入されるガスタ
ービンの吸気空気を冷却する。On the other hand, a part of the liquid refrigerant in the condenser 7 is separated in the refrigerant branch pipe 10 and sent to the intake air cooling heat exchanger 14 through the refrigerant flow rate control valve 13, where the refrigerant is evaporated. The intake air of the gas turbine taken in from the intake duct 1 is cooled.
上記の如く吸気ダクト１に設けられた吸気冷却熱交換器
１４に冷凍機の凝縮器７から液体状冷媒の一部を導き、
該液体状冷媒の蒸発により吸気空気を冷却するので、従
来のガスタービン吸気口に設けた熱交換器に通常７°Ｃ
の冷水を導く方式に比較し、熱交換における相対温度を
大きくできるから、吸気冷却熱交換器１４の伝熱面積を
小さくすることができる。As described above, a part of the liquid refrigerant is introduced from the condenser 7 of the refrigerator to the intake air cooling heat exchanger 14 provided in the intake duct 1,
Since the intake air is cooled by the evaporation of the liquid refrigerant, the heat exchanger installed at the conventional gas turbine intake typically has a temperature of 7°C.
Compared to the method of introducing cold water, the relative temperature during heat exchange can be increased, so the heat transfer area of the intake air cooling heat exchanger 14 can be reduced.
また、冷媒流量制御弁１３で凝縮器７から吸気冷却熱交
換器１４に流入する冷媒流量を制御することにより、吸
気冷却熱交換器１４の出口の空気温度を所定の目標値（
例えば１５°Ｃ）に常に維持することが可能となる。In addition, by controlling the flow rate of refrigerant flowing from the condenser 7 into the intake air cooling heat exchanger 14 with the refrigerant flow control valve 13, the air temperature at the outlet of the intake air cooling heat exchanger 14 is adjusted to a predetermined target value (
For example, it is possible to constantly maintain the temperature at 15°C.
第２図は本発明の他のガスタービン駆動冷凍機のシステ
ム構成を示す図である。同図において、第１図と同一符
号を付した部分は同−又は相当部分を示し、その奏する
作用も同一であるので説明は省略する（また、他の図面
においても同様とする）。図示するように、本実施例で
は、吸気冷却熱交換器１４から冷凍機に戻る冷媒を蒸発
器８に導いている。FIG. 2 is a diagram showing the system configuration of another gas turbine-driven refrigerator according to the present invention. In this figure, parts with the same reference numerals as those in FIG. 1 indicate the same or equivalent parts, and since their functions are the same, the explanation will be omitted (the same applies to other drawings). As shown in the figure, in this embodiment, the refrigerant that returns to the refrigerator from the intake air cooling heat exchanger 14 is guided to the evaporator 8.
上記構成とすることにより、冷凍機の凝縮器７と蒸発器
８の圧力差により冷媒を移送させることができる。With the above configuration, the refrigerant can be transferred due to the pressure difference between the condenser 7 and the evaporator 8 of the refrigerator.
第３図は本発明の他のガスタービン駆動冷凍機のシステ
ム構成を示す図である。図示するように、本実施例では
、冷媒分岐配管１０の途中にポンプ１８を設け、該ポン
プ１８により吸気冷却熱交換器１４と凝縮器７を循環す
る冷媒を強制循環させる構成とした。FIG. 3 is a diagram showing the system configuration of another gas turbine-driven refrigerator according to the present invention. As shown in the figure, in this embodiment, a pump 18 is provided in the middle of the refrigerant branch pipe 10, and the pump 18 is configured to forcefully circulate the refrigerant circulating through the intake air cooling heat exchanger 14 and the condenser 7.
上記構成とすることにより、ポンプ１８を駆動する動力
は必要であるが、冷媒ガスを吸気冷却熱交換器１４から
凝縮器７に戻すことが冷凍機の負荷にはならない。With the above configuration, although power is required to drive the pump 18, returning the refrigerant gas from the intake cooling heat exchanger 14 to the condenser 7 does not place a load on the refrigerator.
第４図は本発明の他のガスタービン駆動冷凍機のシステ
ム構成を示す図である。図示するように、本実施例では
、凝縮器７から吸気冷却熱交換器１４に流す液体状冷媒
を蒸発器８内を通して、冷却（過冷却）して、吸気冷却
熱交換器１４に導いている。FIG. 4 is a diagram showing the system configuration of another gas turbine-driven refrigerator according to the present invention. As shown in the figure, in this embodiment, the liquid refrigerant flowing from the condenser 7 to the intake air cooling heat exchanger 14 is passed through the evaporator 8, cooled (subcooled), and guided to the intake air cooling heat exchanger 14. .
上記構成とすることにより、冷媒分岐配管１０中でベー
パーロックの発生を防止できる。With the above configuration, vapor lock can be prevented from occurring in the refrigerant branch pipe 10.
以上説明したように本発明によれば、下記のような優れ
た効果が得られる。As explained above, according to the present invention, the following excellent effects can be obtained.
〈１〉例えば吸気空気の気温が１５℃の時のガスタービ
ン出力に比べて、気温３２℃の時の出力は約１８％減少
するが、吸気空気の冷却により、１５°Ｃの時と同一の
軸入力が得られる。一方、吸気冷却に必要な冷凍能力は
軸入力の１〜２％に過ぎない。従って総合効率が向上す
る。<1> For example, compared to the gas turbine output when the intake air temperature is 15°C, the output when the air temperature is 32°C is approximately 18% lower, but due to cooling of the intake air, the output is the same as when the air temperature is 15°C. Axis input can be obtained. On the other hand, the refrigerating capacity required for intake air cooling is only 1 to 2% of the shaft input. Therefore, overall efficiency is improved.
（２〉ガスタービンの熱効率は例えば気温１５℃の時の
方が気温３２℃の時より０．５〜１％向上するから、ガ
スタービンの熱効率を向上させることができる。(2> Since the thermal efficiency of the gas turbine is improved by 0.5 to 1% when the temperature is 15° C. than when the temperature is 32° C., the thermal efficiency of the gas turbine can be improved.
（３）ガスタービン吸気ダクトに設けられた熱交換器の
伝熱面積は例えば７°Ｃの冷水を用いた場合より、本発
明では冷媒温度を例えば４°Ｃとすると約２８％も減少
させることから、ガスタービンの吸気側の損失増加も従
来例と比べて少なく抑えることができ、ガスタービンの
有効出力を従来例に比で増やすことができる。(3) The heat transfer area of the heat exchanger installed in the gas turbine intake duct is reduced by about 28% when the refrigerant temperature is set to 4°C, for example, compared to when cold water at 7°C is used. Therefore, the increase in loss on the intake side of the gas turbine can be suppressed to a smaller level than in the conventional example, and the effective output of the gas turbine can be increased compared to the conventional example.
第１図は本発明のガスタービン駆動冷凍機のシダ
ステム構成を示す図、第２図乃至第６図（まそれぞれ本
発明の他のガスタービン駆動冷凍機のシステム構成を示
す図である。
図中、１・・・・吸気ダクト、２・・・・圧縮機、３・
・・・燃焼室、４・・・・出力タービン、５・・・・排
気ダクト、６・・・・圧縮機、７・・・・凝縮器、８・
・・・蒸発器、９・・・・冷水配管、１０・・・・冷媒
分岐配管、１１・・・・冷却水配管、１２・・・・燃料
制御弁、１３・・・・冷媒流量制御弁、１４・・・・吸
気冷却熱交換器、５・・・・冷凍機膨張弁、
６・・・・排気温度検出
器、
７・・・・ガスタービン入口吸気温度検知器、１８・・
・・ポンプ。FIG. 1 is a diagram showing the system configuration of a gas turbine-driven refrigerator of the present invention, and FIGS. 2 to 6 (each are diagrams showing the system configuration of other gas turbine-driven refrigerators of the present invention. , 1... Intake duct, 2... Compressor, 3...
... Combustion chamber, 4... Output turbine, 5... Exhaust duct, 6... Compressor, 7... Condenser, 8...
...Evaporator, 9...Cold water piping, 10...Refrigerant branch pipe, 11...Cooling water pipe, 12...Fuel control valve, 13...Refrigerant flow rate control valve , 14... Intake air cooling heat exchanger, 5... Refrigerator expansion valve, 6... Exhaust temperature detector, 7... Gas turbine inlet intake air temperature detector, 18...
··pump.
Claims (3)
ンにより駆動される圧縮機方式のガスタービン駆動冷凍
機において、 前記凝縮器出口の液体状の冷媒の一部を前記冷凍機外に
導き、ガスタービン吸気ダクトに設けられた熱交換器に
送り、該冷媒の蒸発によりガスタービンの吸気空気を冷
却し、該冷媒を前記冷凍機に戻すことを特徴とするガス
タービン駆動冷凍機。(1) In a compressor-type gas turbine-driven refrigerator that is equipped with a compressor, a condenser, and an evaporator and is driven by a gas turbine, a part of the liquid refrigerant at the outlet of the condenser is drained outside the refrigerator. A gas turbine-driven refrigerator characterized in that the refrigerant is guided, sent to a heat exchanger provided in a gas turbine intake duct, cools the intake air of the gas turbine by evaporating the refrigerant, and returns the refrigerant to the refrigerator.
において、 前記ガスタービン吸気温度を所定の目標値に維持するた
めに前記凝縮器出口から前記ガスタービン吸気ダクトに
設けられた熱交換器に送る冷媒流量を制御する手段を設
けたことを特徴とするガスタービン駆動冷凍機。(2) In the gas turbine-driven refrigerator according to claim (1), a heat exchanger is provided from the condenser outlet to the gas turbine intake duct to maintain the gas turbine intake air temperature at a predetermined target value. A gas turbine-driven refrigerator, characterized in that it is provided with means for controlling the flow rate of refrigerant sent to the refrigerator.
において、 前記ガスタービン吸気ダクトに設けられた熱交換器に前
記冷凍機の凝縮器出口から送り、熱交換器から冷凍機に
戻す冷媒をポンプにより送る構成とするか、 又は凝縮器出口から取り出した前記一部の冷媒を前記冷
凍機の蒸発器内で過冷却させる構成とすることを特徴と
するガスタービン駆動冷凍機。(3) In the gas turbine-driven refrigerator according to claim (1), refrigerant is sent from a condenser outlet of the refrigerator to a heat exchanger provided in the gas turbine intake duct, and is returned from the heat exchanger to the refrigerator. A gas turbine-driven refrigerator, characterized in that the refrigerant is sent by a pump, or the part of the refrigerant taken out from the condenser outlet is supercooled in an evaporator of the refrigerator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32226389A JPH03182638A (en) | 1989-12-11 | 1989-12-11 | Gas turbine driven refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32226389A JPH03182638A (en) | 1989-12-11 | 1989-12-11 | Gas turbine driven refrigerator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH03182638A true JPH03182638A (en) | 1991-08-08 |
Family
ID=18141699
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP32226389A Pending JPH03182638A (en) | 1989-12-11 | 1989-12-11 | Gas turbine driven refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH03182638A (en) |
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| US5321944A (en) * | 1992-01-08 | 1994-06-21 | Ormat, Inc. | Power augmentation of a gas turbine by inlet air chilling |
| KR100530751B1 (en) * | 1997-11-27 | 2006-02-28 | 삼성테크윈 주식회사 | Composite energy generating system |
| JP2011017341A (en) * | 2002-09-30 | 2011-01-27 | Bp Corp North America Inc | Method and system for providing power for coolant compression reduced in carbon dioxide emission amount and electrical power for light hydrocarbon gas liquefying process |
| EP2446122A4 (en) * | 2009-06-22 | 2015-07-15 | Echogen Power Systems Inc | SYSTEM AND METHOD FOR MANAGING HEAT PROBLEMS IN ONE OR MORE INDUSTRIAL PROCEDURES |
| US10094288B2 (en) | 2012-07-24 | 2018-10-09 | Icr Turbine Engine Corporation | Ceramic-to-metal turbine volute attachment for a gas turbine engine |
| CN110173356A (en) * | 2019-06-10 | 2019-08-27 | 中节能城市节能研究院有限公司 | A kind of gas turbine inlet gas compressor group cooling based on refrigerant |
| US10934895B2 (en) | 2013-03-04 | 2021-03-02 | Echogen Power Systems, Llc | Heat engine systems with high net power supercritical carbon dioxide circuits |
| US11187112B2 (en) | 2018-06-27 | 2021-11-30 | Echogen Power Systems Llc | Systems and methods for generating electricity via a pumped thermal energy storage system |
| US11293309B2 (en) | 2014-11-03 | 2022-04-05 | Echogen Power Systems, Llc | Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system |
| US11435120B2 (en) | 2020-05-05 | 2022-09-06 | Echogen Power Systems (Delaware), Inc. | Split expansion heat pump cycle |
| US11629638B2 (en) | 2020-12-09 | 2023-04-18 | Supercritical Storage Company, Inc. | Three reservoir electric thermal energy storage system |
| US12331664B2 (en) | 2023-02-07 | 2025-06-17 | Supercritical Storage Company, Inc. | Waste heat integration into pumped thermal energy storage |
| US12516855B2 (en) | 2022-10-27 | 2026-01-06 | Supercritical Storage Company, Inc. | High-temperature, dual rail heat pump cycle for high performance at high-temperature lift and range |
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Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5321944A (en) * | 1992-01-08 | 1994-06-21 | Ormat, Inc. | Power augmentation of a gas turbine by inlet air chilling |
| KR100530751B1 (en) * | 1997-11-27 | 2006-02-28 | 삼성테크윈 주식회사 | Composite energy generating system |
| JP2011017341A (en) * | 2002-09-30 | 2011-01-27 | Bp Corp North America Inc | Method and system for providing power for coolant compression reduced in carbon dioxide emission amount and electrical power for light hydrocarbon gas liquefying process |
| EP2446122A4 (en) * | 2009-06-22 | 2015-07-15 | Echogen Power Systems Inc | SYSTEM AND METHOD FOR MANAGING HEAT PROBLEMS IN ONE OR MORE INDUSTRIAL PROCEDURES |
| US10094288B2 (en) | 2012-07-24 | 2018-10-09 | Icr Turbine Engine Corporation | Ceramic-to-metal turbine volute attachment for a gas turbine engine |
| US10934895B2 (en) | 2013-03-04 | 2021-03-02 | Echogen Power Systems, Llc | Heat engine systems with high net power supercritical carbon dioxide circuits |
| US11293309B2 (en) | 2014-11-03 | 2022-04-05 | Echogen Power Systems, Llc | Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system |
| US11187112B2 (en) | 2018-06-27 | 2021-11-30 | Echogen Power Systems Llc | Systems and methods for generating electricity via a pumped thermal energy storage system |
| CN110173356A (en) * | 2019-06-10 | 2019-08-27 | 中节能城市节能研究院有限公司 | A kind of gas turbine inlet gas compressor group cooling based on refrigerant |
| US11435120B2 (en) | 2020-05-05 | 2022-09-06 | Echogen Power Systems (Delaware), Inc. | Split expansion heat pump cycle |
| US11629638B2 (en) | 2020-12-09 | 2023-04-18 | Supercritical Storage Company, Inc. | Three reservoir electric thermal energy storage system |
| US12516855B2 (en) | 2022-10-27 | 2026-01-06 | Supercritical Storage Company, Inc. | High-temperature, dual rail heat pump cycle for high performance at high-temperature lift and range |
| US12331664B2 (en) | 2023-02-07 | 2025-06-17 | Supercritical Storage Company, Inc. | Waste heat integration into pumped thermal energy storage |
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