JPH06562Y2 - Combined system of steam and gas turbine and refrigerator - Google Patents
Combined system of steam and gas turbine and refrigeratorInfo
- Publication number
- JPH06562Y2 JPH06562Y2 JP1987123787U JP12378787U JPH06562Y2 JP H06562 Y2 JPH06562 Y2 JP H06562Y2 JP 1987123787 U JP1987123787 U JP 1987123787U JP 12378787 U JP12378787 U JP 12378787U JP H06562 Y2 JPH06562 Y2 JP H06562Y2
- Authority
- JP
- Japan
- Prior art keywords
- steam
- turbine
- gas turbine
- exhaust gas
- refrigerator
- 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 - Lifetime
Links
- 238000010521 absorption reaction Methods 0.000 claims description 21
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 18
- 239000002131 composite material Substances 0.000 claims description 3
- 238000000605 extraction Methods 0.000 claims description 3
- 229920006395 saturated elastomer Polymers 0.000 claims description 3
- 239000007789 gas Substances 0.000 description 53
- 238000010438 heat treatment Methods 0.000 description 10
- 239000000446 fuel Substances 0.000 description 9
- 238000005057 refrigeration Methods 0.000 description 6
- 238000001816 cooling Methods 0.000 description 4
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 2
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000001301 oxygen Substances 0.000 description 2
- 229910052760 oxygen Inorganic materials 0.000 description 2
- 238000010248 power generation Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000000740 bleeding effect Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 239000001294 propane Substances 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
- Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
Landscapes
- Engine Equipment That Uses Special Cycles (AREA)
Description
【考案の詳細な説明】 〔産業上の利用分野〕 本考案はガスタービンの排ガスによって蒸気を発生し、
この蒸気で蒸気タービンと吸収冷凍機を駆動する複合シ
ステムに関する。[Detailed Description of the Invention] [Industrial field of application] The present invention generates steam by the exhaust gas of a gas turbine,
The present invention relates to a combined system that drives a steam turbine and an absorption refrigerator with this steam.
従来、ガスタービンプラントを主体とした複合システム
のうち、公知、公用および刊行物に記載されたものは、
次のものがある。Conventionally, among complex systems mainly composed of gas turbine plants, those described in publicly known, official and publications are:
There are the following:
(1)蒸気タービンとガスタービンとの複合システム ガスタービンの排ガスまたは排ガス中の酸素を使って燃
料を燃焼させて蒸気を発生し、この蒸気によって蒸気タ
ービンを駆動するもの。(1) Combined system of steam turbine and gas turbine A system that uses oxygen in the exhaust gas or exhaust gas of a gas turbine to burn fuel to generate steam, which drives the steam turbine.
(2)ガスタービンと冷凍機の複合システム ガスタービンの排ガスまたは排ガス中の酸素を使って燃
料を燃焼させて蒸気を発生し、この蒸気を吸収冷凍機の
再生器に導入してその熱源とするもの。(2) Combined system of gas turbine and refrigerator A gas turbine exhaust gas or oxygen in the exhaust gas is used to burn fuel to generate steam, and this steam is introduced into the regenerator of the absorption refrigerator and used as its heat source. thing.
(3)LNG冷熱利用ガスタービン複合システム LNGの冷熱によって、フロン、メタン、エンタおよびプ
ロパン等の媒体によるランキンサイクルによって負荷を
駆動し、ガス化した天然ガスをガスタービンの燃料とす
るもの。(3) Gas turbine composite system using LNG cold heat A system that uses a cold heat of LNG to drive a load by a Rankine cycle using a medium such as CFCs, methane, enta and propane, and uses gasified natural gas as fuel for a gas turbine.
(4)ディーゼルエンジンとガスタービンの複合システム ディーゼルエンジンの排ガスによって排ガスタービンを
駆動し、負荷を得るもの。(4) Diesel engine and gas turbine combined system A system that drives an exhaust gas turbine with exhaust gas from a diesel engine to obtain a load.
上記従来の複合システムには次の問題があった。 The above-mentioned conventional complex system has the following problems.
(1)総合効率が必ずしも高くない。(1) Overall efficiency is not always high.
(2)大規模地域の冷暖房には充分に適さない。(2) Not well suited for air conditioning and heating in large areas.
本考案は上記問題点の解決手段として、ガスタービンの
排ガスによって蒸気を発生し、この蒸気を蒸気タービン
に供給すると共に吸収冷凍機の熱源として利用する複合
システムにおいて、 上記ガスタービンがオープンサイクル単純１軸または２
軸形ガスタービンよりなると共に、当該ガスタービンの
排ガスによって過熱蒸気を発生する排ガスボイラと、当
該排ガスボイラにて発生した過熱蒸気によって駆動され
る蒸気タービンと、 上記排ガスボイラにて発生した過熱蒸気または飽和蒸気
または高温水、あるいは蒸気タービンの中間段からの抽
気を熱源として駆動される吸収冷凍機と、 上記ガスタービンと蒸気タービンとの合成負荷と上記吸
収冷凍機の負荷を夫々独立して調節する制御系統とを具
備してなることを特徴とする蒸気およびガスタービンと
冷凍機の複合システムを提供しようとするもである。As a solution to the above problems, the present invention provides a complex system in which steam is generated from exhaust gas of a gas turbine, the steam is supplied to the steam turbine and is also used as a heat source of an absorption chiller, and the gas turbine has an open cycle simple 1 Axis or 2
An exhaust gas boiler that is composed of a shaft gas turbine and that generates superheated steam by the exhaust gas of the gas turbine, a steam turbine that is driven by superheated steam that is generated by the exhaust gas boiler, and a superheated steam that is generated by the exhaust gas boiler or An absorption refrigerator driven by saturated steam or high-temperature water, or extraction air from the intermediate stage of the steam turbine as a heat source, a combined load of the gas turbine and steam turbine, and a load of the absorption refrigerator are independently adjusted. Another object of the present invention is to provide a combined system of a steam and gas turbine and a refrigerator, which is characterized by comprising a control system.
本考案は上記のように構成されるので熱源と電力とのバ
ランスに合せて、蒸気タービンへ供給される蒸気量を調
節し、かつ蒸気タービンの形式も復水式と抽気復水式と
を適宜選択でき、冷凍機側を独立させ、供給蒸気量を自
動制御させることによって、部分負荷から全負荷に亘っ
て高効率運転を行なわせることが可能となる。Since the present invention is configured as described above, the amount of steam supplied to the steam turbine is adjusted in accordance with the balance between the heat source and the electric power, and the steam turbine is of the condensing type or the bleeding / condensing type as appropriate. It is possible to make selection, and by making the refrigerator side independent and automatically controlling the supply steam amount, it becomes possible to perform high-efficiency operation from partial load to full load.
又、電力側は冷凍負荷に追随して、ガスタービン燃焼器
に流入する燃料量を調節し、蒸気タービンの蒸気加減弁
を全開させた状態で、高い効率の蒸気タービン・ガスタ
ービン複合サイクルを営ませることも可能となる。In addition, the electric power side follows the refrigeration load and adjusts the amount of fuel that flows into the gas turbine combustor, and operates the steam turbine / gas turbine combined cycle with high efficiency while fully opening the steam control valve of the steam turbine. It is possible to do it.
従って、冬期は蒸気による暖房を効率的に実施でき、夏
期は蒸気を熱源として吸収冷凍機を稼働させて冷水によ
る冷房をやはり効率的に実施できる。又、熱量の豊かさ
から大規模地域冷暖房の適用に勝れる。Therefore, heating by steam can be efficiently performed in winter, and absorption chiller can be operated by using steam as a heat source to cool air by cold water efficiently in summer. In addition, it is superior to the application of large-scale district heating and cooling due to its rich heat capacity.
本考案の一実施例を第１図を参照して説明する。なお、
説明の便宜上、本実施例における要素の順に行なう。An embodiment of the present invention will be described with reference to FIG. In addition,
For convenience of description, the elements will be described in this order in this embodiment.
(1)ガスタービン系 軸流圧縮機１で圧縮された空気は燃焼器２で燃焼して高
圧温度のガスとなり、タービン３で大気圧に排ガスボイ
ラ４での抵抗を加算した圧力まで膨脹する。この出力か
ら軸流圧縮機１の入力を差引いたものがガスタービン出
力となって、発電熱Ｎを駆動する。(1) Gas Turbine System The air compressed by the axial compressor 1 is combusted in the combustor 2 to become a high-pressure gas, and the turbine 3 expands to a pressure obtained by adding the resistance in the exhaust gas boiler 4 to the atmospheric pressure. A value obtained by subtracting the input of the axial compressor 1 from this output becomes the output of the gas turbine, and drives the heat N for power generation.
図の場合タービン３は単純１軸形であるが、その動力を
工場プロセス用の機械駆動に供する場合にはタービン３
を２軸とし、可変速出力タービンによって機械を駆動す
る。In the case of the figure, the turbine 3 is a simple one-shaft type, but when the power is used for mechanical drive for a factory process, the turbine 3 is used.
Has two axes, and the machine is driven by a variable speed output turbine.
(2)排ガスボイラ系 給水ポンプ５によって給水された純水は、図に示されて
いない節炭器、脱硝装置、蒸発器および加熱器によって
構成される排ガスボイラ４で蒸気となる。(2) Exhaust Gas Boiler System Pure water supplied by the water supply pump 5 becomes steam in the exhaust gas boiler 4 including a economizer, a denitration device, an evaporator and a heater, which are not shown in the figure.
なお排ガスボイラ４を経たタービン３の排ガスは、煙突
６から大気へ放出される。The exhaust gas of the turbine 3 that has passed through the exhaust gas boiler 4 is released from the chimney 6 to the atmosphere.
(3)蒸気タービン系 排ガスボイラ４で発生した蒸気は、主蒸気止め弁７およ
び蒸気加減弁８を経て蒸気タービン９に流入し、仕事を
したのち、復水器１０、復水ポンプ１１、脱気器１２お
よび逆止弁１３を経て、給水ポンプ５によって排ガスポ
ンプ４に給水され、循環系を構成する。(3) Steam turbine system The steam generated in the exhaust gas boiler 4 flows into the steam turbine 9 through the main steam stop valve 7 and the steam control valve 8, and after doing work, the condenser 10, the condensate pump 11, and the degasser Water is supplied to the exhaust gas pump 4 by the water supply pump 5 through the air container 12 and the check valve 13 to form a circulation system.
なお図では、脱気器１２の加熱蒸気は蒸気タービン９の
中間段からの抽気によつているが、排ガスボイラ４内に
脱気器１２を設置して直接脱気を行なってもよい。Although the heating steam of the deaerator 12 is extracted from the intermediate stage of the steam turbine 9 in the figure, the deaerator 12 may be installed in the exhaust gas boiler 4 to perform deaeration directly.
(4)吸収冷凍機系 排ガスボイラ４で発生した蒸気は、蒸気タービン９と２
分流されて、吸収冷凍機１４の熱源に供される。(4) Absorption refrigerator system Steam generated in the exhaust gas boiler 4 is generated by the steam turbines 9 and 2
It is split and supplied to the heat source of the absorption refrigerator 14.
この蒸気は主蒸気止め弁１５、減温ノズル１６、フィル
タ１７、ドレンセパレータ１８、減圧装置１９および蒸
気加減弁２０を経て、吸収冷凍機１４に流入する。The steam flows into the absorption refrigerator 14 through the main steam stop valve 15, the temperature reducing nozzle 16, the filter 17, the drain separator 18, the pressure reducing device 19, and the steam control valve 20.
図に示されていない再生器で、冷凍機循環溶液を加熱し
て冷媒の一部を蒸発気化させた蒸気は凝縮して純水とな
り、ドレントラップ２１および逆止弁２２を経て、蒸気
タービン９側からの純水と合流して、給水ポンプ５によ
って排ガスボイラ４に供給される。In a regenerator not shown in the figure, the vapor that has a part of the refrigerant evaporated and vaporized by heating the refrigerator circulation solution is condensed into pure water, passes through the drain trap 21 and the check valve 22, and then passes through the steam turbine 9 It is merged with pure water from the side and supplied to the exhaust gas boiler 4 by the water supply pump 5.
符号２３は減温ノズルに噴出される純水の加圧タンク、
符号２４は安全弁、符号３２はスチームトラップであ
る。Reference numeral 23 is a pressurized tank of pure water ejected from the temperature reducing nozzle,
Reference numeral 24 is a safety valve, and reference numeral 32 is a steam trap.
なお吸収冷凍機１４で生成された冷水は、空調機２５で
冷房に供されたのち冷水タンク２６、フィルタ２７、冷
水ポンプ２８および止め弁２９を経て、吸収冷凍機１４
内にあって図に示されていない蒸発器に流入して、循環
系を構成する。The cold water generated by the absorption refrigerator 14 is cooled by the air conditioner 25, and then passes through the cold water tank 26, the filter 27, the cold water pump 28, and the stop valve 29, and then the absorption refrigerator 14 is cooled.
It flows into an evaporator which is inside and not shown in the figure to form a circulation system.
(5)制御系統 中央制御盤３０に電力負荷(KW)と冷凍負荷（冷凍トン：
一昼夜に０゜Cの水１トンを氷にする能力）を入力する
と、コンピュータによる演算回路により総合熱効率を考
慮した電力負荷と冷凍負荷の合成値に対応するガスター
ビン燃料流量調節弁３１へ、その開度指令としての電気
信号が送られる。(5) Control system Electric power load (KW) and refrigeration load (refrigeration ton:
When inputting the ability to turn 1 ton of water at 0 ° C into ice all day and night), the calculation circuit by the computer inputs to the gas turbine fuel flow rate control valve 31 corresponding to the combined value of the electric power load and the refrigerating load considering the total thermal efficiency. An electric signal as an opening command is sent.
同時に冷凍負荷に係る吸収冷凍機出口冷水の温度設定の
電気信号が送られる。この温度によって蒸気加減弁２０
の開度が制御され、部分負荷から全負荷に亘る冷凍負荷
の自動制御装置が独立して行なわれる。At the same time, an electric signal for setting the temperature of the cooling water at the outlet of the absorption refrigerator related to the refrigeration load is sent. Depending on this temperature, the steam control valve 20
Is controlled, and the automatic control device for the refrigerating load from partial load to full load is independently performed.
一方電力負荷は蒸気加減弁８の絞り作用によって行なわ
れる。この絞り作用は蒸気圧力を減圧して、蒸気タービ
ンの出力を下げる。このため蒸気加減弁８の弁リフトは
中央制御盤３０にフィードバックされて、ガスタービン
燃料流量調節弁３１の開度を減少させ、所要の電力負荷
に対して、蒸気加減弁８を常に全開させて、広い範囲に
亘って蒸気タービン９を高効率運転させる。On the other hand, the electric power load is applied by the throttling action of the steam control valve 8. This throttling action reduces the steam pressure and reduces the output of the steam turbine. Therefore, the valve lift of the steam control valve 8 is fed back to the central control panel 30 to reduce the opening degree of the gas turbine fuel flow rate control valve 31 and always fully open the steam control valve 8 for a required power load. The steam turbine 9 is operated with high efficiency over a wide range.
なお、蒸気タービン９の排圧は真空であるため、復水ポ
ンプ１１で加圧して、吸収冷凍機１４からの戻り水と同
じ圧力にして合流させるが、圧力不均衡による逆流を防
止するために、逆止弁１３、同２２が夫々両系統に配設
される。Since the exhaust pressure of the steam turbine 9 is a vacuum, the condensate pump 11 pressurizes the steam turbine 9 so that it has the same pressure as the return water from the absorption refrigerator 14 and joins, but in order to prevent backflow due to pressure imbalance. , Check valves 13 and 22 are arranged in both systems.
次に別の実施例について第２図により説明する。Next, another embodiment will be described with reference to FIG.
第２図は蒸気タービン９を抽気復水式とし、その中間段
から抽出した蒸気を吸収冷凍機１４の熱源としたもの
で、他は第１図と変らない。In FIG. 2, the steam turbine 9 is of the extraction / condensation type, and the steam extracted from the intermediate stage is used as the heat source of the absorption refrigerating machine 14. Others are the same as in FIG.
本実施例はガスタービン３、蒸気タービン９、および吸
収冷凍機１４の設計条件によって、第１図の実施例より
も高い総合熱効率をえることができる場合がある。In the present embodiment, depending on the design conditions of the gas turbine 3, the steam turbine 9 and the absorption refrigerator 14, it may be possible to obtain a higher total thermal efficiency than the embodiment of FIG.
なお、工場ロセス用の温熱は排ガスボイラで発生した蒸
気を適用し、地域冷暖房の暖房にも当該蒸気が適用され
る。Note that the steam generated in the exhaust gas boiler is applied to the heat for the factory process, and the steam is also applied to the heating for district cooling and heating.
なお、吸収冷凍機１４の熱源として、排ガスボイラ４内
にあって図に示されていない蒸発器から抽出した飽和蒸
気または節炭器から抽出した高温水を使ってもよい。As the heat source of the absorption refrigerator 14, saturated steam extracted from an evaporator (not shown) in the exhaust gas boiler 4 or high temperature water extracted from a economizer may be used.
上記実施例の複合システムの下記の定義による総合熱効
率は70〜80％に達する。The total thermal efficiency of the composite system of the above example reaches 70-80% as defined below.
f ：ガスタービンの燃料量 kg/H LHV：燃料の低位発熱量 Kcal/kg NG：ガスタービンによる発生電力 KW NS：蒸気タービンによる発生電力 KW Ｇ ：冷凍負荷 冷凍トン HL：水の潜熱 ８０Kcal/kg 一方ガスタービンと蒸気タービンの複合サイクルプラン
トの総合熱効率は40〜50％、ガスタービンと冷凍機の複
合サイクルプラントの総合熱効率は60〜70％である。 f: Fuel amount of gas turbine kg / H LHV: Lower heating value of fuel Kcal / kg N G : Electric power generated by gas turbine KW N S : Electric power generated by steam turbine KW G: Refrigeration load Refrigeration ton H L : Latent heat of water 80Kcal / kg On the other hand, the combined thermal efficiency of the combined cycle plant of gas turbine and steam turbine is 40-50%, and the combined thermal efficiency of the combined cycle plant of gas turbine and refrigerator is 60-70%.
本考案は上記のように構成されるので次の効果を有す
る。即ち、大規模地域冷暖房と電力自給プラントまたは
工場プロセス用冷温熱と自家発電プラントにおいて、従
来にない高い熱効率を全ての負荷に亘って得ることがで
きる。又、実施に移す際、各要素毎には従来のデータを
活用しやすく実用性に富むという利点もある。Since the present invention is configured as described above, it has the following effects. That is, in a large-scale district heating / cooling and electric power self-supplying plant or a cooling / heating heat for factory process and a private power generation plant, it is possible to obtain unprecedented high thermal efficiency over all loads. In addition, when it is put into practice, there is an advantage that conventional data can be easily utilized for each element and is highly practical.
第１図は本考案の一実施例の系統図、第２図は同じく別
の実施例の系統図である。 １…軸流圧縮機、２…燃焼器、３…タービン、 ４…排ガスボイラ、 ８…蒸気加減弁（蒸気タービン用）、 ９…蒸気タービン、 １４…吸収冷凍機、 20…蒸気加減弁（吸収冷凍機用） 25…空調機、 30…中央制御盤、 31…ガスタービンの燃料流量調節弁。FIG. 1 is a system diagram of an embodiment of the present invention, and FIG. 2 is a system diagram of another embodiment. DESCRIPTION OF SYMBOLS 1 ... Axial flow compressor, 2 ... Combustor, 3 ... Turbine, 4 ... Exhaust gas boiler, 8 ... Steam control valve (for steam turbine), 9 ... Steam turbine, 14 ... Absorption refrigerator, 20 ... Steam control valve (absorption) Refrigerator) 25 ... Air conditioner, 30 ... Central control panel, 31 ... Gas turbine fuel flow control valve.
Claims (1)
を蒸気タービンに供給すると共に吸収冷凍機の熱源とし
て利用する複合システムにおいて、 上記ガスタービンがオープンサイクル単純１軸または２
軸形ガスタービンよりなると共に、当該ガスタービンの
排ガスによって過熱蒸気を発生する排ガスボイラと、当
該排ガスボイラにて発生した過熱蒸気によって駆動され
る蒸気タービンと、 上記排ガスボイラにて発生した過熱蒸気または飽和蒸気
または高温水、あるいは蒸気タービンの中間段からの抽
気を熱源として駆動される吸収冷凍機と、 上記ガスタービンと蒸気タービンとの合成負荷と上記吸
収冷凍機の負荷を夫々独立して調節する制御系統とを具
備してなることを特徴とする蒸気およびガスタービンと
冷凍機の複合システム。1. A composite system in which steam is generated by the exhaust gas of a gas turbine, and the steam is supplied to the steam turbine and used as a heat source of an absorption refrigerating machine, wherein the gas turbine is an open cycle simple uniaxial shaft or two shafts.
An exhaust gas boiler that is composed of a shaft gas turbine and that generates superheated steam by the exhaust gas of the gas turbine, a steam turbine that is driven by superheated steam that is generated by the exhaust gas boiler, and a superheated steam that is generated by the exhaust gas boiler or An absorption refrigerator driven by saturated steam or high-temperature water, or extraction air from the intermediate stage of the steam turbine as a heat source, a combined load of the gas turbine and steam turbine, and a load of the absorption refrigerator are independently adjusted. A combined system of a steam and gas turbine and a refrigerator, which comprises a control system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1987123787U JPH06562Y2 (en) | 1987-08-14 | 1987-08-14 | Combined system of steam and gas turbine and refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1987123787U JPH06562Y2 (en) | 1987-08-14 | 1987-08-14 | Combined system of steam and gas turbine and refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6428761U JPS6428761U (en) | 1989-02-20 |
| JPH06562Y2 true JPH06562Y2 (en) | 1994-01-05 |
Family
ID=31372959
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1987123787U Expired - Lifetime JPH06562Y2 (en) | 1987-08-14 | 1987-08-14 | Combined system of steam and gas turbine and refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06562Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4100462B2 (en) * | 1997-09-30 | 2008-06-11 | 株式会社ぱど | Heat utilization system |
-
1987
- 1987-08-14 JP JP1987123787U patent/JPH06562Y2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6428761U (en) | 1989-02-20 |
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