WO2011099891A1 - Installation motrice à turbocompresseur - Google Patents

Installation motrice à turbocompresseur Download PDF

Info

Publication number
WO2011099891A1
WO2011099891A1 PCT/RU2011/000018 RU2011000018W WO2011099891A1 WO 2011099891 A1 WO2011099891 A1 WO 2011099891A1 RU 2011000018 W RU2011000018 W RU 2011000018W WO 2011099891 A1 WO2011099891 A1 WO 2011099891A1
Authority
WO
WIPO (PCT)
Prior art keywords
gas
compressor
injectors
turbine
passive
Prior art date
Application number
PCT/RU2011/000018
Other languages
English (en)
Russian (ru)
Inventor
Талгат Хайдарович ГАРИПОВ
Original Assignee
Garipov Talgat Haidarovich
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Garipov Talgat Haidarovich filed Critical Garipov Talgat Haidarovich
Publication of WO2011099891A1 publication Critical patent/WO2011099891A1/fr

Links

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
    • F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/34—Gas-turbine plants characterised by the use of combustion products as the working fluid with recycling of part of the working fluid, i.e. semi-closed cycles with combustion products in the closed part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers

Definitions

  • the invention of a turbocharged propulsion system relates to power engineering and is intended for energy production.
  • Closed circuit gas turbine units include a condenser connected to the process circuit, recuperators, gas cooler-superheater, compressor, steam power turbines, gas turbine and pump, in which the working medium, gas, for example, is carbon dioxide.
  • the working medium gas, for example, is carbon dioxide.
  • the disadvantages of the known plants include the fact that the efficiency of the known plants is low due to the large combined heat loss to the environment. Also, the use of well-known gas turbine plants leads to an increase in material costs and environmental pollution.
  • the technical results of the claimed invention are aimed at creating a turbocompressor propulsion system, the mechanical equilibrium of which during operation will be in an unstable equilibrium, in which a compressor unit with a circulation circuit will be used for gas compression, in which the gas compression work in the compressor does not exceed the external work obtained by the turbine of this turbocompressor propulsion system, in view of the use of several arallelno included injectors; in which the shaft of the compressor unit is connected kinematically with the shaft of the turbine of the propulsion system; which will be clean for the environment, as well as in it, to increase its effective work, the gas compressed at the compressor unit with the circulation circuit will be supplied to the turbine inlet of the engine unit from the exits of the injectors, and the gas cooled during its expansion on the turbine will be sent for circulation into the cycle and utilized.
  • the turbocompressor engine installation comprises a turbine, a gas dryer, a gas valve and a compressor unit with a circulation circuit, the circuit diagram of which consists of a compressor, the output of which is connected to the input to the output receiver, the output of which is connected through the valve to the line discharge, and the second output from the output receiver is connected to the active inputs of at least two injectors connected in parallel, in which the outputs are connected to the input to the input receiver, the output from which it is connected to the compressor inlet, and the passive inlets of the injectors are connected to a filter located in the surrounding gas medium, while in the turbocompressor engine installation, the turbine outlet is connected by a pipeline with passive inlets to the injectors of the compressor installation with a circulation circuit, and the entrance to the turbine, connected to the discharge line of the compressor unit with a circulation circuit, the input to which, in order to reduce the compressor's compression work and create a working circulation circuit, has been changed, and therefore it is connected through the valve with the second
  • FIG. 1 shows a schematic diagram of a turbocompressor propulsion system.
  • FIG. 2 is a theoretical diagram of the ideal cycle of a turbocharged propulsion system in s - T coordinates, where s is entropy, T is temperature, p in isobar line of upper working pressure, p n isobar line lower working pressure, p and isobar line of preliminary working pressure, ij, i 3 , i 4 - enthalpies at characteristic points.
  • Turbocharged propulsion system (see drawing of figure 1), further turbocharged installation, is designed to produce mechanical energy of rotation of the shaft.
  • the turbocharger installation includes a compressor unit with a circulation circuit 1 (patent 2 380579 RU), then a compressor unit and a gas turbine 2, then a turbine.
  • Turbine 2 can be used, for example, centripetal.
  • the nominal gas turbine 2 capacity corresponds to the maximum capacity of compressor unit 1.
  • Compressor unit 1 comprises a centrifugal compressor 3, in which, for example, isothermal compression of gas is carried out.
  • the technological scheme of the compressor unit is presented as follows.
  • the output from the compressor 3 is connected by a pipeline to the input to the receiver of the output 4.
  • the receiver of the output 4 is connected via valve 5 to the discharge pipe 6 (with the discharge line).
  • the output from the receiver of the output 4 is connected by a pipeline with the active inputs to the injectors 7.
  • the injectors 7, in an amount of at least two, are included in parallel in the compressor installation circuit.
  • the number of injectors 7 included in the compressor installation 1 may be, for example, sixteen.
  • the injector 7 represents a hollow body elongated along the axis, into which a nozzle is inserted from one side, in front of which there is a passive chamber (passive volume), and a confuser is located along the nozzle axis, which passes into a diffuser, directed to exit the injector.
  • the active inputs of the injectors 7 are the inputs to the nozzles into which compressed (active) gas is supplied for the operation of the injectors.
  • injectors 7 are combined into a collector connected to the receiver of input 8.
  • the output from the receiver of input 8 is connected to the entrance to the compressor 3.
  • the passive inputs of the injectors 7 are the inputs to the passive chambers of the injectors, into which uncompressed, passive gas is supplied for the operation of the injectors.
  • the passive inputs at the injectors 7 are combined into a collector, which is connected by a pipeline to the filter 11. The entrance to the filter 11
  • the productivity of the compressor unit 1 for gas is determined by the capacity of the injectors 7, which also depends on the gas pressure at the active and passive inputs of the injectors.
  • a compressor installation with a circulation circuit 1 95 is designed to obtain a higher pressure of compressed gas in the discharge line 6 and a higher gas suction performance at a nominal compression ratio of compressor 3, which are achieved through the use of several injectors connected in parallel to the circulation circuit 7. Accordingly, the start of the squeezed (compression) gas by the compressor 3 ° is shifted to the high-pressure region (see Fig. 2).
  • the pressure differs little from the gas pressure at the compressor inlet, and is, for example, 0.03 MPa (0.3 atm.)
  • the inlet to the discharge pipe 6 is connected to the outlet of the receiver
  • the exit from the turbine 2 is connected by a pipeline to the collector of passive inputs to the injectors 7 of the compressor installation.
  • the inlet to the turbine 2 is connected to the outlet of the discharge pipe 6 of the compressor unit.
  • the entrance to the pipeline for discharge 6 of the compressor unit, in order to create a working circulation circuit, is changed and connected to the input receiver.
  • the second output from the receiver input 8 of the compressor unit is connected a pipeline with an inlet of a valve installed on the discharge pipeline 6.
  • a collector that combines the passive inputs of the injectors 7 of the compressor unit is connected by a pipeline to the outlet of the filling valve 9.
  • the filling valve 9, installed on the suction line, is designed to fill and refuel the entire technological internal volume turbocompressor installation with gas (air) from the environment.
  • the inlet to the filling valve 9 is connected by a pipeline through a gas dryer 10 to the filter 11 of the compressor unit.
  • the drive shaft of the compressor 3 of the compressor unit is connected kinematically (using a clutch or gearbox) with the power shaft of the turbine, and then with an electric generator.
  • the pipeline connecting the outlet of the turbine 2 with the passive inputs of the injectors is isolated from the outside by heat influx.
  • the tightness of the technological cavity of a turbocompressor propulsion system is provided by known methods.
  • the turbocharger installation is equipped with a battery and a starter.
  • the compressor 3 injects gas, which was at the time of start-up in the receiver of the inlet 8 under ambient pressure, compresses it conditionally isothermally and pumps it into circulation in the circulation circuit.
  • gas is supplied to it from the surrounding external environment.
  • the gas of the external environment passes through the filter 11 and the dehumidifier 10.
  • the gas enters the passive inlet manifold through the pipeline and enters the volumes of the passive chambers in parallel with the installed injectors 7.
  • the gas passes through the volumes of the injectors 7 and leaves them in the volume of the receiver of the input 8.
  • the gas entering the receiver of the input 8 is pumped by the compressor 3, isothermally compressed and pumped to
  • 155 nozzle perimeter increases the speed of the passive gas.
  • the gases are mixed and enter the volumes of the diffusers of the injectors with great speed. Since the perimeter of the sum of the outlet cross sections of the nozzles of the injectors depends on their number, more passive gas will be entrained in the confusers than into one nozzle, if the nozzle cross-sectional area is equal to the area of all the outlet cross-sections of the nozzle nozzles.
  • pre-compression of the gas occurs in the injectors.
  • Pre-compressed gas enters the receiver input 8, and gas is pumped from the compressor.
  • the compressor 3 the gas preliminarily compressed in the injectors is pressurized and pumped for circulation into the circulation circuit. Compressed to a new value, the gas leaves the receiver output 4 and through the pipeline
  • the circulation circuit is directed to the active inputs of the injectors into the nozzles of the injectors.
  • the active gas entrains into the confusers the gas located in the passive chambers of the injectors and enters diffusers, where the gas velocity drops, and the pressure and, therefore, the internal energy of the gas increase to a new value.
  • Compressor 3 compresses (compresses) the gas to a new pressure value with an increase in the internal energy of the gas and pumps it into circulation in the circulation circuit. After a certain number of such circulations, the gas pressure in the receiver output 4 and at the outlet of the compressor circuit
  • the turbocharger installation switches to a stationary mode of operation. Useful work is sent to the consumer.
  • the valve 5 of the compressor installation partially opens or closes. As a result, the starter turns off. Process gas pressure
  • Process 3-2 indicates the work that the active (compressed) gas does when compressing the passive gas
  • process 4-2 indicates the compression of the passive gas coming from the output of the turbine 2.
  • this effect of injection compression by injectors 7, connected in parallel in the circuit is a process that is generated inside the cycle of the turbocompressor unit and (accompanies the process) reduces the gas compression work in the compressor 3. That is, the gas supplied to the working compressor 3 of the compressor unit already has compression work
  • the amount of heat supplied to the cycle is determined by the area l-3-s 3 -S] -l. From this amount of heat, it is necessary to take the area of operation of the compressor 3, which it spent on compressing the gas pre-compressed by the injectors 7. As shown above, increasing the number of injectors to
  • 270 injectors 7 of active and passive gas will be five areas 2-3-s 3 -s 2 -2 and determined by the area 3-s 3 -s 2 '-2'-3. Then we subtract from the heat brought into the cycle the area l-3'-s 3 -s r l, which is the amount of heat allocated from the cycle. Work against friction is neglected. Total, a positive area of 1-2'-4'-1 is useful work directed to the consumer. Moreover, if positive
  • turbomotive press engine installation as an unstable mechanical system will, further increasing the shaft speed, deviate further from the equilibrium state, because the force acts scapular gas reactions

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention se rapporte au domaine de la production électrique, et concerne une installation motrice à turbocompresseur qui comprend une installation de compression efficace avec un circuit de remise en circulation (1), une turbine (2), un clapet d'alimentation (9) et un dispositif de séchage des gaz (10). Dans l'installation de compression (1), le compresseur (3) est connecté à un récepteur de sortie (4) dont une sortie est connectée aux entrées actives de plusieurs injecteurs qui sont connectés en parallèle et dont les sorties sont connectées au récepteur d'entrée (8) ayant sa sortie connectée au compresseur, tandis que l'autre sortie est connectée par un clapet (5) à la turbine connectée au compresseur par un arbre commun. La sortie de la turbine est connectée aux entrées passives des injecteurs (7), ce qui fait que le gaz, ayant fourni de la force par détente et étant devenu passif, sort de la turbine et entre dans les injecteurs où il est comprimé par le gaz actif venant du compresseur. Le gaz comprimé passif venant des injecteurs entre dans la turbine, et le gaz actif ayant une pression réduite entre dans le compresseur où il est encore comprimé. La circulation ininterrompue des flux de gaz est obtenue par force obtenue sur la turbine qui est supérieure à la force de compression supplémentaire du gaz par le compresseur.
PCT/RU2011/000018 2010-02-11 2011-01-18 Installation motrice à turbocompresseur WO2011099891A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
RU2010104724 2010-02-11
RU2010104724/06A RU2010104724A (ru) 2010-02-11 2010-02-11 Турбокомпрессорная двигательная установка

Publications (1)

Publication Number Publication Date
WO2011099891A1 true WO2011099891A1 (fr) 2011-08-18

Family

ID=44367960

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/RU2011/000018 WO2011099891A1 (fr) 2010-02-11 2011-01-18 Installation motrice à turbocompresseur

Country Status (2)

Country Link
RU (1) RU2010104724A (fr)
WO (1) WO2011099891A1 (fr)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013054172A1 (fr) * 2011-10-12 2013-04-18 Richard Gaillard Centrale électrique à flux d'air pulsé en circuit fermé
WO2018125535A1 (fr) 2016-12-29 2018-07-05 X Development Llc Utilisation d'air externe pour une commande d'inventaire à cycle fermé
US10907510B2 (en) 2016-12-28 2021-02-02 Malta Inc. Storage of excess heat in cold side of heat engine
US10907513B2 (en) 2010-03-04 2021-02-02 Malta Inc. Adiabatic salt energy storage
US10920674B2 (en) 2016-12-28 2021-02-16 Malta Inc. Variable pressure inventory control of closed cycle system with a high pressure tank and an intermediate pressure tank
US10920667B2 (en) 2016-12-28 2021-02-16 Malta Inc. Pump control of closed cycle power generation system
US11053847B2 (en) 2016-12-28 2021-07-06 Malta Inc. Baffled thermoclines in thermodynamic cycle systems
US11156385B2 (en) 2012-09-27 2021-10-26 Malta Inc. Pumped thermal storage cycles with working fluid management
US11286804B2 (en) 2020-08-12 2022-03-29 Malta Inc. Pumped heat energy storage system with charge cycle thermal integration
US11352951B2 (en) 2016-12-30 2022-06-07 Malta Inc. Variable pressure turbine
US11396826B2 (en) 2020-08-12 2022-07-26 Malta Inc. Pumped heat energy storage system with electric heating integration
US11454167B1 (en) 2020-08-12 2022-09-27 Malta Inc. Pumped heat energy storage system with hot-side thermal integration
US11480067B2 (en) 2020-08-12 2022-10-25 Malta Inc. Pumped heat energy storage system with generation cycle thermal integration
US11486305B2 (en) 2020-08-12 2022-11-01 Malta Inc. Pumped heat energy storage system with load following
US11655759B2 (en) 2016-12-31 2023-05-23 Malta, Inc. Modular thermal storage
US11678615B2 (en) 2018-01-11 2023-06-20 Lancium Llc Method and system for dynamic power delivery to a flexible growcenter using unutilized energy sources
US11852043B2 (en) 2019-11-16 2023-12-26 Malta Inc. Pumped heat electric storage system with recirculation
US11982228B2 (en) 2020-08-12 2024-05-14 Malta Inc. Pumped heat energy storage system with steam cycle

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2131045C1 (ru) * 1997-06-16 1999-05-27 Гарипов Талгат Хайдарович Криогенная газотурбинная установка с замкнутой схемой
RU99103278A (ru) * 1999-02-18 2000-12-20 Т.Х. Гарипов Газотурбинная установка с газодинамическим нагревом и автоматический газодинамический нагреватель
RU2005126962A (ru) * 2005-08-26 2007-03-10 Талгат Хайдарович Гарипов (RU) Теплоэнергетическая газовая установка с газодинамическим нагревом рабочего тела и автоматический газодинамический нагреватель с фронтальным акустическим объемом

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2131045C1 (ru) * 1997-06-16 1999-05-27 Гарипов Талгат Хайдарович Криогенная газотурбинная установка с замкнутой схемой
RU99103278A (ru) * 1999-02-18 2000-12-20 Т.Х. Гарипов Газотурбинная установка с газодинамическим нагревом и автоматический газодинамический нагреватель
RU2005126962A (ru) * 2005-08-26 2007-03-10 Талгат Хайдарович Гарипов (RU) Теплоэнергетическая газовая установка с газодинамическим нагревом рабочего тела и автоматический газодинамический нагреватель с фронтальным акустическим объемом

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
M.P. VUKALOVICH ET AL.: "Termodinamika.", MASHINOSTROENIE, 1972, MOSCOW, pages 28 - 29 *
V. M BRODYANSKY.: "Vechny dvigatel-prezhde i teper.", ENERGOATOMIZDAT, 1989, MOSCOW, pages 85 - 87 *

Cited By (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10907513B2 (en) 2010-03-04 2021-02-02 Malta Inc. Adiabatic salt energy storage
US11761336B2 (en) 2010-03-04 2023-09-19 Malta Inc. Adiabatic salt energy storage
WO2013054172A1 (fr) * 2011-10-12 2013-04-18 Richard Gaillard Centrale électrique à flux d'air pulsé en circuit fermé
US11754319B2 (en) 2012-09-27 2023-09-12 Malta Inc. Pumped thermal storage cycles with turbomachine speed control
US11156385B2 (en) 2012-09-27 2021-10-26 Malta Inc. Pumped thermal storage cycles with working fluid management
US11454168B2 (en) 2016-12-28 2022-09-27 Malta Inc. Pump control of closed cycle power generation system
US11371442B2 (en) 2016-12-28 2022-06-28 Malta Inc. Variable pressure inventory control of closed cycle system with a high pressure tank and an intermediate pressure tank
US10920674B2 (en) 2016-12-28 2021-02-16 Malta Inc. Variable pressure inventory control of closed cycle system with a high pressure tank and an intermediate pressure tank
US10920667B2 (en) 2016-12-28 2021-02-16 Malta Inc. Pump control of closed cycle power generation system
US11053847B2 (en) 2016-12-28 2021-07-06 Malta Inc. Baffled thermoclines in thermodynamic cycle systems
US10907510B2 (en) 2016-12-28 2021-02-02 Malta Inc. Storage of excess heat in cold side of heat engine
US11927130B2 (en) 2016-12-28 2024-03-12 Malta Inc. Pump control of closed cycle power generation system
US11591956B2 (en) 2016-12-28 2023-02-28 Malta Inc. Baffled thermoclines in thermodynamic generation cycle systems
US11512613B2 (en) 2016-12-28 2022-11-29 Malta Inc. Storage of excess heat in cold side of heat engine
CN110366632B (zh) * 2016-12-29 2022-06-10 马耳他股份有限公司 使用外部空气进行闭合循环库存控制
US10907548B2 (en) 2016-12-29 2021-02-02 Malta Inc. Use of external air for closed cycle inventory control
EP3563043A4 (fr) * 2016-12-29 2020-11-18 Malta Inc. Utilisation d'air externe pour une commande d'inventaire à cycle fermé
WO2018125535A1 (fr) 2016-12-29 2018-07-05 X Development Llc Utilisation d'air externe pour une commande d'inventaire à cycle fermé
CN110366632A (zh) * 2016-12-29 2019-10-22 马耳他股份有限公司 使用外部空气进行闭合循环库存控制
US11578622B2 (en) 2016-12-29 2023-02-14 Malta Inc. Use of external air for closed cycle inventory control
US11352951B2 (en) 2016-12-30 2022-06-07 Malta Inc. Variable pressure turbine
US11655759B2 (en) 2016-12-31 2023-05-23 Malta, Inc. Modular thermal storage
US11678615B2 (en) 2018-01-11 2023-06-20 Lancium Llc Method and system for dynamic power delivery to a flexible growcenter using unutilized energy sources
US11852043B2 (en) 2019-11-16 2023-12-26 Malta Inc. Pumped heat electric storage system with recirculation
US11396826B2 (en) 2020-08-12 2022-07-26 Malta Inc. Pumped heat energy storage system with electric heating integration
US11578650B2 (en) 2020-08-12 2023-02-14 Malta Inc. Pumped heat energy storage system with hot-side thermal integration
US11480067B2 (en) 2020-08-12 2022-10-25 Malta Inc. Pumped heat energy storage system with generation cycle thermal integration
US11454167B1 (en) 2020-08-12 2022-09-27 Malta Inc. Pumped heat energy storage system with hot-side thermal integration
US11840932B1 (en) 2020-08-12 2023-12-12 Malta Inc. Pumped heat energy storage system with generation cycle thermal integration
US11846197B2 (en) 2020-08-12 2023-12-19 Malta Inc. Pumped heat energy storage system with charge cycle thermal integration
US11486305B2 (en) 2020-08-12 2022-11-01 Malta Inc. Pumped heat energy storage system with load following
US11885244B2 (en) 2020-08-12 2024-01-30 Malta Inc. Pumped heat energy storage system with electric heating integration
US11286804B2 (en) 2020-08-12 2022-03-29 Malta Inc. Pumped heat energy storage system with charge cycle thermal integration
US11982228B2 (en) 2020-08-12 2024-05-14 Malta Inc. Pumped heat energy storage system with steam cycle

Also Published As

Publication number Publication date
RU2010104724A (ru) 2011-08-20

Similar Documents

Publication Publication Date Title
WO2011099891A1 (fr) Installation motrice à turbocompresseur
US4404805A (en) Method of and system for power generation by supercharged internal combustion engine
WO2009066178A4 (fr) Moteurs thermiques
PL83504B1 (fr)
CN104806313A (zh) 一种等温压缩空气储能系统及方法
CN103775148A (zh) 自冷式热力做功方法
WO2012051785A1 (fr) Système de compression de gaz turbocompound
CN107605554A (zh) 自冷式热力循环方法
CN201810391U (zh) 涡轮复合气体压缩系统
CN107476996B (zh) 发电机组
TW202108951A (zh) 用於發電的熱泵、能量產生系統及熱交換系統
CN202273762U (zh) 涡轮增压气体压缩系统
CN202202959U (zh) 高压工质源气体压缩机
CN102305207B (zh) 制冷系统自增压气力泵
CN102374688B (zh) 热声压缩机驱动的制冷系统
RU2365827C2 (ru) Устройство для изменения температуры воздуха помещения
CA2450105C (fr) Procede de fonctionnement et d'agencement d'un moteur a pistons a air comprime
CN102383935B (zh) 涡轮增压气体压缩系统
CN210068476U (zh) 一种高效的两级压缩空压机主机
WO2021034221A1 (fr) Installation de génération électrique à gaz et vapeur selon le cycle d'anthony
CN202228175U (zh) 低温进气发动机
CN110005588A (zh) 一种多缸活塞式膨胀—压缩机
RU2661418C1 (ru) Турбокомпрессорная тепловая машина, работающая по замкнутому термодинамическому циклу с внутренней регенерацией тепла
RU2380579C1 (ru) Компрессорная установка с циркуляционным контуром
CN114294253B (zh) 一种混联式压缩膨胀机及控制方法

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11742537

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 11742537

Country of ref document: EP

Kind code of ref document: A1