JPS6330487B2 - - Google Patents
Info
- Publication number
- JPS6330487B2 JPS6330487B2 JP57233929A JP23392982A JPS6330487B2 JP S6330487 B2 JPS6330487 B2 JP S6330487B2 JP 57233929 A JP57233929 A JP 57233929A JP 23392982 A JP23392982 A JP 23392982A JP S6330487 B2 JPS6330487 B2 JP S6330487B2
- Authority
- JP
- Japan
- Prior art keywords
- air
- cooling
- cylindrical casing
- compressed air
- turbine
- 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
Links
- 238000001816 cooling Methods 0.000 claims description 38
- 238000010438 heat treatment Methods 0.000 claims description 7
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 10
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000011810 insulating material Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005338 heat storage Methods 0.000 description 1
- 238000005381 potential energy Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
- F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
-
- 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
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Wind Motors (AREA)
Description
【発明の詳細な説明】
この発明は空気熱タービンに関し、詳しくは圧
縮空気及びこの圧縮空気の有するポテンシヤル熱
エネルギをも駆動源とし得る空気熱タービンに関
する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an air heat turbine, and more particularly to an air heat turbine which can also use compressed air and the potential thermal energy of the compressed air as a driving source.
従来、動力源を圧縮空気とする空気タービンが
広く知られているが、この種駆動装置の動力源と
なる圧縮空気を作り出す際、空気圧縮により生じ
る熱、又は冷却熱などは全く利用されることなく
無駄に棄てられていた。 Conventionally, air turbines that use compressed air as a power source are widely known, but when producing the compressed air that is the power source for this type of drive device, the heat generated by air compression or cooling heat is not used at all. It was wasted and wasted.
従つて、いかに空気タービン自体の駆動効率を
良くしても圧縮空気を作り出す際に発生する熱を
有効に利用しなければ全体としての効率の良化は
一定限度以上は望めない。 Therefore, no matter how much the driving efficiency of the air turbine itself is improved, unless the heat generated when producing compressed air is effectively used, the overall efficiency cannot be improved beyond a certain limit.
この発明は上記に鑑み、圧縮空気を作り出す際
に発生する熱、冷却熱をも動力源として利用し
得、もつて非常に効率の良い空気熱タービンを提
供することを目的としてなされたものであつて、
二段のタービン羽根を有した回転軸を受容する円
筒形ケーシングの一端に、前記円筒形ケーシング
と同軸に円環形状をなす断熱熱膨脹室が設けら
れ、該断熱熱膨脹室内には加熱媒体管路が配設さ
れていると共に外周には冷却圧縮空気送入口及び
前記タービン羽根に対面する端面には空気噴出口
が複数個設けられており、前記円筒形ケーシング
内面には前記二段のタービン羽根間へ内径方向に
延出し、かつ、外部より加熱可能とされた固定羽
根が多数設けられ、さらに前記円筒形ケーシング
他端の開放面には冷却空気吹出口を有した冷却筒
が同軸状に延設されて成ることを特徴とするもの
である。 In view of the above, the present invention was made with the purpose of providing an extremely efficient air-thermal turbine that can utilize heat generated when compressed air is produced, as well as cooling heat, as a power source. hand,
An adiabatic thermal expansion chamber having an annular shape is provided coaxially with the cylindrical casing at one end of a cylindrical casing that receives a rotating shaft having two stages of turbine blades, and a heating medium pipe line is provided in the adiabatic thermal expansion chamber. A cooling compressed air inlet is provided on the outer periphery and a plurality of air jet ports are provided on the end face facing the turbine blade, and a plurality of air jet ports are provided on the inner surface of the cylindrical casing between the two stages of the turbine blades. A large number of fixed blades extending in the inner diameter direction and capable of being heated from the outside are provided, and a cooling tube having a cooling air outlet is coaxially extended from the open surface of the other end of the cylindrical casing. It is characterized by consisting of:
以下、この発明を実施例により説明する。 This invention will be explained below with reference to Examples.
第１図はこの発明の実施例の断面図である。 FIG. 1 is a sectional view of an embodiment of the invention.
この発明の空気熱タービンＡは、二段にわたつ
てタービン羽根１Ａ，１Ｂが設けられた回転軸２
を受容する円筒形ケーシング３の一端３Ａに、前
記円筒形ケーシング３と同軸に円環形状をなす断
熱熱膨脹室４が一体的に設けられ、この断熱熱膨
脹室４内には加熱媒体管路５がコイル状に配設さ
れていると共に、外周には冷却圧縮空気送入口
６、及び前記タービン羽根１Ａに対面する端面４
Ａには空気噴出口７，７が円周状に配列されて複
数個設けられており、前記円筒形ケーシング３内
面３Ｂには二段のタービン羽根１Ａ，１Ｂ間へ内
径方向に延出して、外部より加熱可能とされた固
定羽根８が多数設けられ、さらに前記円筒形ケー
シング他端３Ｃの開放面には冷却空気吹出口９，
９を有した冷却筒１０が同軸状に延設されて構成
されている。 The air heat turbine A of the present invention has a rotating shaft 2 on which turbine blades 1A and 1B are provided in two stages.
An adiabatic thermal expansion chamber 4 having an annular shape is integrally provided coaxially with the cylindrical casing 3 at one end 3A of the cylindrical casing 3 that receives the cylindrical casing 3, and a heating medium conduit 5 is provided in the adiabatic thermal expansion chamber 4. It is arranged in a coil shape, and has a cooling compressed air inlet 6 on the outer periphery and an end face 4 facing the turbine blade 1A.
A is provided with a plurality of air jet ports 7, 7 arranged circumferentially, and on the inner surface 3B of the cylindrical casing 3, extending in the inner radial direction between the two stages of turbine blades 1A, 1B, A large number of fixed blades 8 which can be heated from the outside are provided, and cooling air outlets 9 are provided on the open surface of the other end 3C of the cylindrical casing.
A cooling cylinder 10 having a cooling cylinder 9 is configured to extend coaxially.
上記冷却筒１０内には、同心状に冷却空気室１
０１が設けられており、冷却空気吹出口９，９は
冷却空気室１０１外周に設けられ、かつ、該冷却
空気室１０１に冷却空気を送入する管１０２には
図示を省略したが逆止弁が設けられている。 Inside the cooling cylinder 10, a cooling air chamber 1 is arranged concentrically.
01, cooling air outlets 9, 9 are provided on the outer periphery of the cooling air chamber 101, and a check valve (not shown) is provided in the pipe 102 that feeds cooling air into the cooling air chamber 101. is provided.
上記実施例において、図中１１は熱媒通路であ
り、固定羽根８を加熱するために設けられたもの
であつて、固定羽根８取付面以外の他の面は断熱
材１２……１２により熱的に保護されている。 In the above embodiment, reference numeral 11 in the figure is a heat medium passage, which is provided to heat the fixed blade 8, and the surface other than the mounting surface of the fixed blade 8 is heated by heat insulating material 12...12. protected.
又、断熱熱膨脹室４における冷却圧縮空気送入
口６の有効開口断面積Ａと、空気噴出口７の有効
開口断面積ａとは、空気噴出口７の総数をｎとす
るとＡ≧naの関係とされ、Ａ＞naの場合は、冷
却圧縮空気送入口６に、図示は省略したが逆止弁
が設けられる。 In addition, the effective opening cross-sectional area A of the cooling compressed air inlet 6 in the adiabatic thermal expansion chamber 4 and the effective opening cross-sectional area a of the air outlet 7 have a relationship of A≧na, where n is the total number of air outlets 7. If A>na, the cooling compressed air inlet 6 is provided with a check valve (not shown).
又、固定羽根８は、図示のように、第２段目の
タービン羽根１Ｂに臨ませて配置することが望ま
しい。 Further, it is desirable that the fixed blade 8 be disposed so as to face the second stage turbine blade 1B as shown in the figure.
尚、図中１３，１３はベアリング、１４は熱媒
体管路５の外部断熱材である。 In the figure, 13 and 13 are bearings, and 14 is an external heat insulating material for the heat medium pipe line 5.
次に、この発明の空気熱タービンＡの作動につ
いて説明する。 Next, the operation of the air heat turbine A of the present invention will be explained.
まず、熱媒体管路５に加熱水、又は高温水蒸気
などの熱媒が流通され、同時に断熱熱膨脹室４に
は冷却圧縮空気が冷却圧縮空気送入口６より送入
される。 First, a heat medium such as heated water or high-temperature steam is passed through the heat medium pipe 5, and at the same time, cooled compressed air is introduced into the adiabatic thermal expansion chamber 4 from the cooled compressed air inlet 6.
このとき断熱熱膨脹室４内においては冷却圧縮
空気が熱媒体管路５により急激に熱せられ、この
結果、圧力が急激に上昇する。そして、空気噴出
口７，７より噴出し、この衝動によりタービン羽
根１Ａが回転する。 At this time, the cooled compressed air is rapidly heated in the adiabatic thermal expansion chamber 4 by the heat medium pipe 5, and as a result, the pressure rises rapidly. Then, air is ejected from the air ejection ports 7, 7, and the turbine blade 1A rotates due to this impulse.
第１段目のタービン羽根１Ａにある程度の仕事
量をうばわれた圧縮空気はさらに第２段目のター
ビン羽根１Ｂへと固定羽根８で整流されて流れる
が、このとき固定羽根８より加熱され再び圧力を
増し、第２段目のタービン羽根１Ｂに衝動を与
え、円筒形ケーシング３の開放面へと放出され
る。 The compressed air that has been subjected to a certain amount of work by the first-stage turbine blade 1A further flows to the second-stage turbine blade 1B after being rectified by the fixed blade 8, but at this time, it is heated by the fixed blade 8 and re-circulated. It increases the pressure, imparts an impulse to the second stage turbine blade 1B, and is ejected into the open surface of the cylindrical casing 3.
このとき、円筒形ケーシング３の開放面３Ｃに
は冷却空気吹出口９，９を有した冷却筒１０が延
設されているため、冷却筒１０内は低温化され、
円筒形ケーシング３内との圧力差を生じ、背圧を
生じさせるから円筒形ケーシング３内の空気流を
付勢する作用を行うのである。 At this time, since a cooling cylinder 10 having cooling air outlets 9, 9 is extended to the open surface 3C of the cylindrical casing 3, the temperature inside the cooling cylinder 10 is reduced.
This creates a pressure difference with the inside of the cylindrical casing 3 and generates back pressure, which acts to bias the airflow inside the cylindrical casing 3.
尚、上記において、冷却空気は冷却空気送入口
１０２を経て冷却空気室１０１に入り、冷却筒１
０内を通過する空気から熱を奪つて膨脹し、吹出
口９から噴出されるのである。 In the above, cooling air enters the cooling air chamber 101 through the cooling air inlet 102 and enters the cooling cylinder 1.
The air absorbs heat from the air passing through it, expands, and is ejected from the air outlet 9.
上記全体の作用における冷却圧縮空気は、空気
圧縮機により作られる圧縮空気から発熱熱量をう
ばつてできるものであり、かつ、加熱熱媒は上記
圧縮空気からうばつた熱を利用して加熱されたも
のが用いられる。 The cooling compressed air in the above-mentioned overall operation is produced by extracting the calorific value from the compressed air produced by the air compressor, and the heating heat medium is heated using the heat extracted from the compressed air. is used.
尚、冷却圧縮空気及び断熱膨脹用熱媒の発生装
置として、第２図に示すような風力システム装置
Ｂを利用すれば、自然エネルギの有効利用ともな
り、又無公害の動力源となつて非常に都合が良
い。 In addition, if a wind power system device B as shown in Fig. 2 is used as a generator of cooling compressed air and a heat medium for adiabatic expansion, it will be possible to effectively utilize natural energy and become a pollution-free power source. It is convenient for
この第２図における風力システム装置Ｂは、風
車２０及びこの風車２０によつて駆動される第
１、第２の圧縮機２１，２２を有し、第１の圧縮
機２１により空気圧縮を行い圧縮空気タンク２３
に圧縮空気を蓄積すると共に、第１の圧縮機２１
より圧縮空気タンク２３に至る管路２４に第２の
圧縮機２２により駆動される熱媒回路２６を設け
熱交換器２５で第１の圧縮機２１により圧縮され
た空気の熱量を例えば貯水槽２７内の水に熱交換
させ熱水として蓄えておく構成とされたものであ
る。 The wind power system device B in FIG. 2 includes a wind turbine 20 and first and second compressors 21 and 22 driven by the wind turbine 20. air tank 23
The compressed air is stored in the first compressor 21.
A heat medium circuit 26 driven by a second compressor 22 is provided in a pipe line 24 leading to a compressed air tank 23, and a heat exchanger 25 transfers the amount of heat of the air compressed by the first compressor 21 to a water storage tank 27. It is designed to exchange heat with the water inside and store it as hot water.
そして、本発明の空気熱タービンＡの駆動源と
しての冷却圧縮空気を上記システム装置Ｂの圧縮
タンク２３より取り出し、又、熱媒としての熱水
を上記システム装置Ｂの貯水槽２７より取り出し
て利用するのである。 Cooled compressed air as a driving source for the air-thermal turbine A of the present invention is taken out from the compression tank 23 of the system device B, and hot water as a heat medium is taken out from the water storage tank 27 of the system device B and used. That's what I do.
尚、熱媒は、主として空気熱タービンＡの断熱
熱膨脹室４内の加熱用として用いられ、固定羽根
８の加熱には、熱媒回路２６の一部に再熱回路２
６′を設け、この回路の熱が利用される。 The heat medium is mainly used for heating the adiabatic thermal expansion chamber 4 of the air-thermal turbine A, and a reheat circuit 2 is provided in a part of the heat medium circuit 26 to heat the fixed blades 8.
6' is provided, and the heat of this circuit is utilized.
尚、上記風力システム装置Ｂにより蓄積される
冷却圧縮空気の最大蓄積圧力は30Kg／cm2及び温度
が−30℃まで可能であり、又、熱交換により得ら
れる熱媒温度は最高200℃まで高めることができ、
従つて蓄熱体を水とすれば水温を100℃まで上昇
させることが可能である。 Furthermore, the maximum accumulated pressure of the cooling compressed air accumulated by the above-mentioned wind power system equipment B is 30 kg/cm 2 and the temperature can be up to -30℃, and the temperature of the heating medium obtained by heat exchange can be increased to a maximum of 200℃. It is possible,
Therefore, if the heat storage body is water, it is possible to raise the water temperature to 100°C.
この場合、上記システム装置Ｂより定常的に取
り出し得る冷却圧縮空気として、圧力10Kg／cm2、
−20℃とし、熱媒体の熱水温度を90℃とすれば、
この発明における空気熱タービンＡの断熱熱膨脹
室４内での冷却圧縮空気の圧力膨脹率は約３倍強
に達し、駆動源となる空気噴出圧がいちじるしく
増幅され効率の良化が図れるのである。 In this case, the cooling compressed air that can be taken out regularly from the system device B has a pressure of 10 kg/cm 2 ,
If the temperature is −20℃ and the hot water temperature of the heat medium is 90℃,
In this invention, the pressure expansion rate of the cooled compressed air in the adiabatic thermal expansion chamber 4 of the air-thermal turbine A reaches approximately three times or more, and the air jet pressure serving as the driving source is significantly amplified, thereby improving efficiency.
この発明は以上のように構成され、空気の有す
るポテンシヤルエネルギを圧力と熱とに分離し、
しかもこれらを有効に利用するので、非常に効率
が良く、かつ、電力、風力、水力、蒸気力、圧縮
ガス力のいずれをも増強することができる。 This invention is configured as described above, and separates the potential energy of air into pressure and heat.
Moreover, since these are used effectively, it is extremely efficient and can enhance any of electric power, wind power, water power, steam power, and compressed gas power.
又、この発明の空気熱タービンは、動力源に空
気を利用するので無公害であり、かつ、エネルギ
資源の枯渇のおそれも全くないなど種々の効果を
有する。 Furthermore, since the air-thermal turbine of the present invention uses air as a power source, it is non-polluting and has various effects such as no fear of depletion of energy resources.
第１図はこの発明の実施例の断面図、第２図は
この発明の駆動システムの一例を示す説明図であ
る。
Ａ……空気熱タービン、１Ａ，１Ｂ……タービ
ン羽根、２……回転軸、３……円筒形ケーシン
グ、３Ａ……円筒形ケーシング一端、３Ｂ……円
筒形ケーシング内面、４……断熱熱膨脹室、４Ａ
……断熱熱膨脹室端面、５……加熱媒体管路、６
……冷却圧縮空気送入口、７……空気噴出口、８
……固定羽根、９……冷却空気吹出口、１０……
冷却筒、１０２……背圧低下用冷却圧縮空気送入
口、１０１……冷却空気室。
FIG. 1 is a sectional view of an embodiment of the invention, and FIG. 2 is an explanatory diagram showing an example of a drive system of the invention. A... Air heat turbine, 1A, 1B... Turbine blade, 2... Rotating shaft, 3... Cylindrical casing, 3A... One end of cylindrical casing, 3B... Inner surface of cylindrical casing, 4... Adiabatic thermal expansion chamber , 4A
...Adiabatic thermal expansion chamber end surface, 5...Heating medium pipe line, 6
...Cooling compressed air inlet, 7...Air jet port, 8
... Fixed vane, 9 ... Cooling air outlet, 10 ...
Cooling cylinder, 102... Cooling compressed air inlet for reducing back pressure, 101... Cooling air chamber.
Claims (1)
る円筒形ケーシングの一端に、前記円筒形ケーシ
ングと同軸に円環形状をなす断熱熱膨脹室が設け
られ、該断熱熱膨脹室内には加熱媒体管路が配設
されていると共に外周には冷却圧縮空気送入口及
び前記タービン羽根に対面する端面には空気噴出
口が複数個設けられており、前記円筒形ケーシン
グ内面には前記二段のタービン羽根間へ内径方向
に延出し、かつ、外部より加熱可能とされた固定
羽根が多数設けられ、さらに前記円筒形ケーシン
グ他端の開放面には冷却空気吹出口を有した冷却
筒が同軸状に延設されて成ることを特徴とする空
気熱タービン。1. An adiabatic thermal expansion chamber having an annular shape is provided coaxially with the cylindrical casing at one end of a cylindrical casing that receives a rotating shaft having two stages of turbine blades, and a heating medium pipe is installed in the adiabatic thermal expansion chamber. A cooling compressed air inlet is provided on the outer periphery and a plurality of air jet ports are provided on the end face facing the turbine blade, and a cooling compressed air inlet is provided on the outer periphery, and a plurality of air jet ports are provided on the end face facing the turbine blade, and the inner surface of the cylindrical casing is provided with a cooling compressed air inlet and a plurality of air jet ports are provided on the inner surface of the cylindrical casing. A large number of fixed blades are provided that extend in the inner diameter direction and can be heated from the outside, and a cooling cylinder having a cooling air outlet is coaxially extended on the open surface of the other end of the cylindrical casing. An air heat turbine characterized by comprising:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57233929A JPS59115431A (en) | 1982-12-22 | 1982-12-22 | Air heat turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57233929A JPS59115431A (en) | 1982-12-22 | 1982-12-22 | Air heat turbine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59115431A JPS59115431A (en) | 1984-07-03 |
| JPS6330487B2 true JPS6330487B2 (en) | 1988-06-17 |
Family
ID=16962813
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57233929A Granted JPS59115431A (en) | 1982-12-22 | 1982-12-22 | Air heat turbine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59115431A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT202000029366A1 (en) * | 2020-12-02 | 2022-06-02 | Be Initia S R L | TURBOGAS GROUP WITH ELECTROMAGNETIC INDUCTION AND AEROSPACE THRUSTERS INCLUDING THE SAID TURBOGAS GROUP |
-
1982
- 1982-12-22 JP JP57233929A patent/JPS59115431A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59115431A (en) | 1984-07-03 |
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