CN112627913B - Radial flow turbine axial force self-adaptive control system - Google Patents
Radial flow turbine axial force self-adaptive control system Download PDFInfo
- Publication number
- CN112627913B CN112627913B CN202011385972.9A CN202011385972A CN112627913B CN 112627913 B CN112627913 B CN 112627913B CN 202011385972 A CN202011385972 A CN 202011385972A CN 112627913 B CN112627913 B CN 112627913B
- Authority
- CN
- China
- Prior art keywords
- turbine
- motor
- heat exchanger
- axial force
- end heat
- 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.)
- Active
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/005—Sealing means between non relatively rotating elements
-
- 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
- F01K13/00—General layout or general methods of operation of complete plants
- F01K13/006—Auxiliaries or details not otherwise provided for
-
- 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
- F01K13/00—General layout or general methods of operation of complete plants
- F01K13/02—Controlling, e.g. stopping or starting
-
- 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
- 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
- F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
- F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
- F01K25/103—Carbon dioxide
-
- 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
- Y02E10/20—Hydro energy
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Hydraulic Turbines (AREA)
Abstract
The invention aims to provide an axial force self-adaptive regulation and control system of a runoff turbine, which comprises the runoff turbine, a generator, a hot end heat exchanger, a cold end heat exchanger, a liquid storage tank and a booster pump, wherein two ends of the booster pump are respectively connected with an outlet of the liquid storage tank and an inlet of the hot end heat exchanger, an outlet of the hot end heat exchanger is connected with an air inlet of the turbine, an air outlet of the turbine is connected with an inlet of the cold end heat exchanger, an outlet of the cold end heat exchanger is connected with the liquid storage tank, and the runoff turbine is connected with the generator. Aiming at the problems that the radial flow turbine in the high-speed integrated generating set has larger axial force, so that the design of a thrust bearing is more difficult and the like, the invention adopts a method for actively controlling the pressure of the annular chamber at the back of the turbine by arranging a reasonable sealing structure so as to achieve the aim of actively regulating and controlling the axial force, can balance more than 90 percent of the axial force and greatly reduce the design difficulty of the high-speed thrust bearing.
Description
Technical Field
The invention relates to a turbine regulating system, in particular to a turbine axial force regulating system.
Background
In recent years, in Organic Rankine Cycle (ORC) and S-CO 2 In the power generation devices such as Brayton cycle, Kalina cycle, residual pressure and residual energy, the high-speed integrated power generation unit has the characteristics of small volume, light weight, high power density, high efficiency, zero working medium leakage and the likeDots are becoming more and more widely used. The high-speed integrated generator set mainly comprises a high-speed main shaft, a runoff turbine, a high-speed generator, a high-speed magnetic suspension/air bearing and the like. Because the main shaft has high rotating speed, the diameter of a thrust disc of the thrust bearing is limited by the influences of wind abrasion loss, material strength, rotor dynamic balance performance and the like, and the bearing capacity of the thrust bearing is directly related to the size of the thrust disc.
Because the bearing capacity of the thrust bearing is limited, and the axial force generated by the pressure difference at two sides of the radial flow turbine is always larger than the bearing capacity of the thrust bearing, other measures must be taken to balance the axial force, and methods such as a balance hole or a balance disc are mostly adopted in the industry at present.
The balance hole is a circle of small holes formed in the rear cover plate of the impeller and close to the hub, so that the pressure difference between an annular chamber on the back of the impeller and an impeller flow channel is reduced, and the axial force is reduced. However, the balance holes formed in the impeller not only reduce the strength of the impeller, but also affect the flow field when the airflow flows into or out of the impeller flow channel from the balance holes, increase the flow channel loss, and reduce the aerodynamic efficiency and the cavitation resistance.
The balance disc is arranged on the main shaft, and axial thrust generated by pressure difference of gas on two sides can be used for partially offsetting axial force of the rotor, but the arrangement of the balance disc not only increases the windmilling loss, but also increases the length and weight of the main shaft, and reduces the rigidity.
It can be seen that no matter the balance holes or the balance discs have negative effects on the unit, only part of axial force can be offset, and meanwhile, the adaptability to variable working conditions is poor and active regulation and control cannot be achieved.
Disclosure of Invention
The invention aims to provide a radial flow turbine axial force self-adaptive control system which actively balances axial force and reduces the design difficulty of a thrust bearing.
The purpose of the invention is realized as follows:
the invention relates to a radial flow turbine axial force self-adaptive control system, which is characterized in that: the system comprises a runoff turbine, a generator, a hot end heat exchanger, a cold end heat exchanger, a liquid storage tank and a booster pump, wherein two ends of the booster pump are respectively connected with an outlet of the liquid storage tank and an inlet of the hot end heat exchanger, an outlet of the hot end heat exchanger is connected with an air inlet of the turbine, an air outlet of the turbine is connected with an inlet of the cold end heat exchanger, an outlet of the cold end heat exchanger is connected with the liquid storage tank, and the runoff turbine is connected with the generator.
The present invention may further comprise:
1. the runoff turbine includes turbine casing, turbine atmoseal, the generator includes motor casing, the motor atmoseal, set up the turbine atmoseal between motor casing and the turbine casing, the both sides of turbine atmoseal are turbine sprue and impeller back annular chamber respectively, set up the motor atmoseal in the motor casing, the both sides of motor atmoseal are impeller back annular chamber and the inside chamber of motor respectively, set up drainage air inlet and water conservancy diversion gas outlet on the motor casing that impeller back annular chamber locates, set up the motor on the inside chamber casing of motor and let off the class mouth.
2. And the outlet of the hot end heat exchanger is connected with a drainage control pipe on a pipeline of the turbine air inlet, the drainage control pipe is connected with the drainage air inlet, and a drainage control valve is arranged on the drainage control pipe.
3. The diversion air outlet is connected with a diversion air outlet pipe, the diversion air outlet pipe is connected with an inlet of the cold-end heat exchanger, and an air pump and a check valve are installed on the diversion air outlet pipe.
4. The motor drainage port is connected with a diversion air outlet pipe in front of the check valve through a motor drainage valve.
The invention has the advantages that: aiming at the problems that the radial flow turbine in the high-speed integrated generating set has larger axial force, so that the design of a thrust bearing is more difficult and the like, the invention adopts a method for actively controlling the pressure of the annular chamber at the back of the turbine by arranging a reasonable sealing structure so as to achieve the aim of actively regulating and controlling the axial force, can balance more than 90 percent of the axial force and greatly reduce the design difficulty of the high-speed thrust bearing.
Drawings
FIG. 1 is a schematic structural view of the present invention;
figure 2 is a schematic view of a radial flow turbine generator.
Detailed Description
The invention will now be described in more detail by way of example with reference to the accompanying drawings in which:
the invention relates to an adaptive control system for axial force of a radial flow turbine of a high-speed integrated generator set in an ORC power generation device, which is combined with a figure 1-2 and comprises a booster pump 1-1, a radial flow turbine 1-2, a hot end heat exchanger 1-3, a PLC1-4, a drainage control valve 1-5, an impeller air inlet pressure measuring device 1-6, an impeller back annular chamber pressure measuring device 1-7, an air pump 1-8, an air pumping control valve 1-9, a high-speed generator 1-10, a motor drain valve 1-11, a check valve 1-12, a cold end heat exchanger 1-13, an impeller air outlet pressure measuring device 1-14, a liquid storage/air tank and the like 1-15.
The booster pump 1-1, the hot end heat exchanger 1-3, the runoff turbine 1-2, the cold end heat exchanger 1-13, the liquid storage tank 1-15 and the like are sequentially connected in series through metal pipelines and are an ORC main heat circulation system;
one end of a drainage control valve 1-5 is connected with an outlet pipeline of the hot end heat exchanger 1-3, and the other end is connected with a drainage air inlet N2, which is a drainage pipeline;
the flow guide air outlet N3, the air pump 1-8, the air pumping control valve 1-9 and the check valve 1-12 are sequentially connected in series and are connected into an inlet pipeline of the cold end heat exchanger 1-13 to form an air pumping pipeline;
one end of the motor drain valve 1-11 is connected with the motor drain port N4, and the other end is merged into the pipelines before the check valve 1-12 of the air suction pipeline and after the control valve 1-9 of the air suction pipeline, and is a motor drain pipeline;
the pressure measuring device 1-6 at the air inlet of the impeller is arranged on a main pipeline close to the front of the air inlet N1 of the turbine, the pressure measuring device 1-7 at the back of the impeller is arranged on a pipeline close to the rear of the air guide outlet N3, and the pressure measuring device 1-14 at the air outlet of the impeller is arranged on a pipeline close to the rear of the air outlet N5 of the turbine and is a pressure measuring module.
The pressure measuring devices 1-6, 1-7 and 1-14 and the control valves 1-5, 1-9 and 1-11 are sequentially connected with the PLC1-4 through control cables to carry out data processing and analysis in the PLC1-4 to form a control module;
a part of the structure of the high-speed integrated generator set is described by combining a figure 2, and the high-speed integrated generator set mainly comprises a turbine air seal 2-1, a motor shell 2-2, a motor air seal 2-3, a bearing seat 2-4, a main shaft 2-5, a turbine impeller 2-6 and a turbine shell 2-7.
The turbine air seal 2-1 isolates a main runner of the turbine from an annular chamber at the back of the impeller, and the motor air seal 2-3 isolates the annular chamber at the back of the impeller from an inner chamber of the motor to form a controllable space of a pressure air conditioner;
the turbine air inlet N1 and the turbine air outlet N5 are arranged on a turbine housing 2-7, the diversion air inlet N2 and the diversion air outlet N3 are arranged on a motor housing 2-2 where an annular chamber at the back of the impeller is located, and the motor discharge port N4 is arranged on a motor inner chamber housing 2-2.
Static seals such as O-shaped rings and the like are uniformly arranged at the joints among static parts such as a turbine steam seal 2-1, a turbine shell 2-7, a motor shell 2-2, a motor gas seal 2-3, a bearing seat 2-4 and the like;
according to the first Newton law, the axial force generated by the runoff turbine is equal to the reaction force exerted by the thrust bearing in magnitude and opposite in direction, and the magnitude of the axial force of the runoff turbine can be monitored in real time by monitoring the reaction force exerted by the thrust bearing of the high-speed generator. In addition, according to experimental experience, the magnitude of the axial force of the radial-flow turbine is related to the turbine inlet pressure Pi, the turbine outlet pressure Po and the turbine back annular chamber pressure Pb. If Pi and Po are larger, the thrust direction points to the motor side; if Pb is large, the thrust direction is directed to the turbine side. Therefore, the axial force of the radial-flow turbine can be obtained by monitoring the numerical values of Pi, Po and Pb in real time and calculating according to an empirical formula or monitoring the reaction force of the thrust bearing, and the magnitude and the direction of the axial thrust can be regulated and controlled by properly adjusting the Pb value by taking the magnitude as a judgment basis.
Starting a booster pump 1-1, boosting the liquid working medium, then flowing into a hot end heat exchanger 1-3, and heating to be in a high-pressure gas state; the high-pressure gaseous working medium flows into a turbine impeller through a turbine air inlet N1 to do work through expansion, the pressure is reduced, the temperature is reduced, and then the high-pressure gaseous working medium flows out of a turbine air outlet N5; the dead steam flowing out of the turbine outlet N5 flows into a condenser 1-13 to be cooled into liquid and stored in a 1-15 liquid storage tank; then the booster pump 1-1 is pressurized and sent into the hot end heat exchanger 1-3 to complete a cycle.
After high-pressure gas enters the flow channel from the turbine inlet N1, the radial-flow turbine 1-2 generates pressure difference between the flow surface and the back annular chamber of the radial-flow turbine 1-2 due to the obstruction of the turbine steam seal 2-1, and axial force is generated under the action of the pressure difference. Pi, Po and Pb are respectively measured through pressure measuring devices 1-6, 1-14 and 1-7, and the measurement results are transmitted to a PLC1-4 to be analyzed and calculated to obtain an axial force F.
If the axial force points to the motor side and the numerical value exceeds the early warning value Fw +, the PLC gives a command to open the control valve 1-5, so that the high-pressure gaseous working medium at the outlet of the hot-end heat exchanger 1-3 enters the annular chamber at the back of the turbine through the drainage air inlet N2, the pressure Pb of the high-pressure gaseous working medium is increased, and the value of the axial force F is gradually reduced to an allowable value;
if the axial force points to the turbine side and the value exceeds the early warning value Fw-, the PLC gives an instruction to close the control valves 1-5, sequentially opens the control valves 1-9 and the air extracting pump 1-8, extracts the working medium in the annular chamber at the back of the turbine from the flow guide air outlet N3 and sends the working medium into the heat exchanger 1-13 at the cold end, so that the pressure Pb of the chamber is reduced, and the value of the axial force F is gradually reduced to an allowable value.
The motor air seal 2-3 separates the annular chamber at the back of the turbine from the motor cavity, working media leaking into the motor from the motor air seal 2-3 can flow out through a motor leakage port N4, and the control valve 1-11 can control the flow leaked out of the motor in real time.
Check valves 1-12 prevent back flow of air from the cold side heat exchanger inlet line into the motor.
Claims (4)
1. Radial flow turbine axial force self-adaptation control system, characterized by: the system comprises a runoff turbine, a generator, a hot end heat exchanger, a cold end heat exchanger, a liquid storage tank and a booster pump, wherein two ends of the booster pump are respectively connected with an outlet of the liquid storage tank and an inlet of the hot end heat exchanger;
the runoff turbine includes turbine casing, turbine atmoseal, the generator includes motor casing, motor atmoseal, sets up the turbine atmoseal between motor casing and the turbine casing, and the both sides of turbine atmoseal are turbine sprue and impeller back annular chamber respectively, sets up the motor atmoseal in the motor casing, and the both sides of motor atmoseal are impeller back annular chamber and motor inside chamber respectively, sets up drainage air inlet and water conservancy diversion gas outlet on the motor casing that impeller back annular chamber locates, sets up the motor opening that leaks on the inside chamber housing of motor.
2. The radial flow turbine axial force adaptive control system of claim 1, which is characterized in that: and the outlet of the hot end heat exchanger is connected with a drainage control pipe on a pipeline of the turbine air inlet, the drainage control pipe is connected with the drainage air inlet, and a drainage control valve is arranged on the drainage control pipe.
3. The radial flow turbine axial force adaptive control system of claim 2, which is characterized in that: the diversion air outlet is connected with a diversion air outlet pipe, the diversion air outlet pipe is connected with an inlet of the cold-end heat exchanger, and an air pump and a check valve are installed on the diversion air outlet pipe.
4. The adaptive radial flow turbine axial force control system of claim 3, which is characterized in that: the motor drainage port is connected with the diversion air outlet pipe in front of the check valve through the motor drainage valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011385972.9A CN112627913B (en) | 2020-12-01 | 2020-12-01 | Radial flow turbine axial force self-adaptive control system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011385972.9A CN112627913B (en) | 2020-12-01 | 2020-12-01 | Radial flow turbine axial force self-adaptive control system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112627913A CN112627913A (en) | 2021-04-09 |
| CN112627913B true CN112627913B (en) | 2022-08-19 |
Family
ID=75307274
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011385972.9A Active CN112627913B (en) | 2020-12-01 | 2020-12-01 | Radial flow turbine axial force self-adaptive control system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112627913B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113153437B (en) * | 2021-04-15 | 2022-07-01 | 中国航发湖南动力机械研究所 | High-power-magnitude axial force adjusting structure of power turbine rotor |
| CN114483664A (en) * | 2021-12-31 | 2022-05-13 | 北京动力机械研究所 | External hanging type axial force balance shafting structure |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101694168A (en) * | 2008-06-17 | 2010-04-14 | 斯奈克玛公司 | Turbomachine with long lasting position-holding system |
| CN102220881A (en) * | 2010-04-19 | 2011-10-19 | 霍尼韦尔国际公司 | Turbocharger with axial turbine and parallel flow compressor |
| CN110469376A (en) * | 2019-08-29 | 2019-11-19 | 中国船舶重工集团公司第七一九研究所 | Brayton cycle electricity generation system and method |
| CN210861785U (en) * | 2019-09-30 | 2020-06-26 | 天津商业大学 | Intelligent household energy space-time transmission and distribution system |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5141389A (en) * | 1990-03-20 | 1992-08-25 | Nova Corporation Of Alberta | Control system for regulating the axial loading of a rotor of a fluid machine |
| US5659205A (en) * | 1996-01-11 | 1997-08-19 | Ebara International Corporation | Hydraulic turbine power generator incorporating axial thrust equalization means |
| US6036433A (en) * | 1998-06-29 | 2000-03-14 | General Electric Co. | Method of balancing thrust loads in steam turbines |
| US6705086B1 (en) * | 2002-12-06 | 2004-03-16 | General Electric Company | Active thrust control system for combined cycle steam turbines with large steam extraction |
| US7112036B2 (en) * | 2003-10-28 | 2006-09-26 | Capstone Turbine Corporation | Rotor and bearing system for a turbomachine |
| US6892540B1 (en) * | 2004-05-27 | 2005-05-17 | General Electric Company | System and method for controlling a steam turbine |
| WO2016073252A1 (en) * | 2014-11-03 | 2016-05-12 | Echogen Power Systems, L.L.C. | Active thrust management of a turbopump within a supercritical working fluid circuit in a heat engine system |
| KR101667386B1 (en) * | 2014-12-24 | 2016-10-19 | 포스코에너지 주식회사 | Steam turbine improved axial performance |
| ITUA20162125A1 (en) * | 2016-03-30 | 2017-09-30 | Exergy Spa | Radial turbomachinery with axial thrust compensation |
-
2020
- 2020-12-01 CN CN202011385972.9A patent/CN112627913B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101694168A (en) * | 2008-06-17 | 2010-04-14 | 斯奈克玛公司 | Turbomachine with long lasting position-holding system |
| CN102220881A (en) * | 2010-04-19 | 2011-10-19 | 霍尼韦尔国际公司 | Turbocharger with axial turbine and parallel flow compressor |
| CN110469376A (en) * | 2019-08-29 | 2019-11-19 | 中国船舶重工集团公司第七一九研究所 | Brayton cycle electricity generation system and method |
| CN210861785U (en) * | 2019-09-30 | 2020-06-26 | 天津商业大学 | Intelligent household energy space-time transmission and distribution system |
Non-Patent Citations (3)
| Title |
|---|
| 泵作透平时叶轮轴向力的数值计算与分析;屈晓云等;《中国农村水利水电》;20130715(第07期);全文 * |
| 浅谈增压透平膨胀机轴向力的分析及平衡;孙充渊等;《杭氧科技》;20160630(第02期);全文 * |
| 高速透平机械轴位移故障自愈调控系统研究;高金吉等;《机械科学与技术》;20051128(第11期);全文 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112627913A (en) | 2021-04-09 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN112627913B (en) | Radial flow turbine axial force self-adaptive control system | |
| CN103089339B (en) | For active clearance control system and the method for combustion gas turbine | |
| CN110905609B (en) | High-parameter ORC turbine power generation equipment applied to engine waste heat recovery and ORC device | |
| CN110242375A (en) | A kind of twin-stage organic rankine cycle system and its working method based on air-bearing | |
| CN113833534A (en) | Supercritical carbon dioxide turbine shaft seal air supply and leakage recovery system and method | |
| CN201671660U (en) | Steam turbine with steam extraction being changed into back pressure type | |
| CN108204256B (en) | System for eliminating blowing loss and realizing zero steam admission of low-pressure cylinder and working method thereof | |
| CN103717838B (en) | Comprise the steam turbine of thrust balancing piston | |
| CN113153455B (en) | Radial flow turbine axial force self-adaptive control method | |
| CN210164503U (en) | High-parameter ORC turbine power generation equipment applied to engine waste heat recovery and ORC device | |
| CN111412030A (en) | Supercritical carbon dioxide expander based on integrated cooling system | |
| CN104405457B (en) | A kind of energy gradient utilization system of back pressure turbine heat supply | |
| CN216767564U (en) | Supercritical fluid and gas turbine combined cycle system | |
| RU2392452C2 (en) | Steam turbine warming method | |
| CN216429687U (en) | Supercritical carbon dioxide turbine shaft seal air supply and air leakage recovery system | |
| JP7129916B2 (en) | Turbogenerator for generating electrical energy, associated operating and installation methods | |
| CN216112187U (en) | High-precision adjusting valve suitable for deep peak regulation working condition of thermal power plant | |
| CN201714437U (en) | Steam turbine with steam extraction back pressure type changed from double-steam-extraction condensing type | |
| CN114856730A (en) | Closed circulating cooling system of supercritical carbon dioxide turbine and adjusting method | |
| JP7362664B2 (en) | Axial load management system | |
| CN212130569U (en) | Supercritical carbon dioxide expander based on integrated cooling system | |
| CN212744095U (en) | Turbine apparatus and system | |
| Liu et al. | Current development and prospect of turbine in otec | |
| CN210599121U (en) | Steam turbine supercharger | |
| CN204238990U (en) | A kind of energy gradient utilization system of back pressure turbine heat supply |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |