CN113898427A - Radial support system of supercritical carbon dioxide turbine rotor - Google Patents
Radial support system of supercritical carbon dioxide turbine rotor Download PDFInfo
- Publication number
- CN113898427A CN113898427A CN202111374301.7A CN202111374301A CN113898427A CN 113898427 A CN113898427 A CN 113898427A CN 202111374301 A CN202111374301 A CN 202111374301A CN 113898427 A CN113898427 A CN 113898427A
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- bearing
- turbine rotor
- tilting pad
- radial
- rotor
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- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/28—Supporting or mounting arrangements, e.g. for turbine casing
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- 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
- F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
- F01D21/003—Arrangements for testing or measuring
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- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/04—Antivibration arrangements
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- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/10—Heating, e.g. warming-up before starting
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- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/12—Cooling
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- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/12—Cooling
- F01D25/125—Cooling of bearings
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- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
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- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
- F01D25/162—Bearing supports
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- 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
Abstract
The invention discloses a radial support system of a supercritical carbon dioxide turbine rotor, which comprises a turbine rotor and a plurality of bearing seats; the turbine rotor is provided with a bearing supporting section, a bearing housing is arranged in an inner hole of the bearing seat, a radial tilting pad bearing is arranged in the bearing housing, a plurality of groups of shape memory alloy springs and an annular metal wire mesh block are arranged between the outer wall of a bearing shell of the radial tilting pad bearing and the bearing housing, each group comprises two shape memory alloy springs which are positioned on the same bus of the bearing shell, the two shape memory alloy springs are respectively positioned on two sides of the metal wire mesh block, the bearing supporting section on the turbine rotor is supported in the corresponding radial tilting pad bearing, the bearing seat is connected with a heating/cooling device, and the heating/cooling device can heat or cool the radial tilting pad bearing. The invention has simple structure, can avoid the amplitude peak value of the critical rotating speed of the rotor, ensures that the sCO2 turbine rotor stably passes through the critical rotating speed in the speed increasing and reducing process, and can regulate and control the supporting rigidity.
Description
Technical Field
The invention relates to the technical field of supercritical carbon dioxide turbines, in particular to a radial support system for a rotor of a supercritical carbon dioxide turbine.
Background
Since supercritical carbon dioxide sCO2 has an extremely high fluid density while maintaining low viscosity, turbomachinery of the sCO2 working fluid presents unique challenges to bearing support systems. The unique fluid characteristics of the sCO2 as a working fluid in a power cycle lead to the characteristics of compactness, high speed, high energy density and the like of the sCO2 working medium turbine. Therefore, bearing applications in the sCO2 turbomachinery face challenges related to bearing surface speed and bearing unit load.
At the same time, the existence of the axial multi-stage turbine, a plurality of axial couplings and balance pistons and the large axial space required by dry gas sealing lead to the long axial length and strong flexibility of the sCO2 turbine rotor. In order to ensure the efficiency of the overall power generation system of the sCO2, the operation speed of the sCO2 turbine is higher than the flexible critical speed of the rotor, and the resonance generated by external excitation such as unbalanced force and the flexible mode of the rotor can cause great rotor amplitude near the flexible critical speed of the rotor. How to safely and smoothly pass through the flexible critical rotating speed of the rotor of the sCO2 turbine is a great problem in the mechanical startup and shutdown process of the sCO2 turbine.
To solve the above-mentioned troublesome problem, the conventional radial bearing solution is to use a tilting pad bearing and to fit a squeeze film damper on its outer side. The tilting pad bearing with high stability is used in the scheme to adapt to the high-speed running of the turbine rotor, and the supporting damping is improved by matching with the squeeze film damper. However, the squeeze film damper has a limited effect on increasing the damping, and cannot completely suppress the rotor amplitude which is sharply increased near the critical rotation speed of the turbine rotor; single lift radial bearing damping has limited effect on solving the above problems.
The shape memory alloy SMA has two structural forms of martensite and austenite, the SMA at normal temperature is in a martensite state, and when the temperature is raised to be close to the phase transformation temperature, the SMA can be transformed from the martensite to the austenite. The SMA is made into a spring shape, so that the spring with completely different rigidity at normal temperature and high temperature can be obtained. The metal wire net block is formed by weaving metal wires with small wire diameter into a net and then pressing the net into a block. The metal wires inside the damper are interwoven to form a plurality of dry friction nodes, and the rigidity and the damping of the metal wire mesh block are realized by the coulomb damping effect among the nodes, so the damper is a good metal damper.
The sCO2 integrated power generation system includes a sCO2 turbine, generator, heat exchanger, cooler, compressor, condenser, pump, and heater. After the CO2 works through the sCO2 turbine, the working medium gas after heat exchange through the heat exchanger has higher temperature and can be used as good heating gas; the working medium gas after passing through the cooler has a lower temperature and can be used as good cooling gas.
The integral sCO2 power generation system has good heating and cooling gas, the SMA spring has completely different rigidity when being higher than and lower than the phase transition temperature, the rigidity and the damping can be generated by Coulomb friction of a plurality of dry friction nodes inside the metal wire mesh block after the metal wire mesh block is in interference fit, the three parts are combined with the tilting pad bearing through ingenious structural design, the rigidity damping change of the radial support of the sCO2 turbine rotor in high and low temperature states is realized, the radial support temperature is controlled in real time by controlling the heating and cooling gas, the critical rotating speed position of the turbine rotor is further changed, the suppression of rotor vibration is effectively realized in the process of rotor speed increase and decrease, and the sCO2 turbine rotor is ensured to stably and safely pass through the flexible critical rotating speed.
Disclosure of Invention
In order to solve the technical problems, the invention provides the radial support system of the supercritical carbon dioxide turbine rotor, which has a simple structure, can avoid the amplitude peak value of the critical rotating speed of the rotor, ensures that the sCO2 turbine rotor stably passes through the critical rotating speed in the speed increasing and reducing process, can regulate and control the bearing rigidity, does not need lubricating oil and cooling and heating gas, does not need auxiliary equipment, and can obviously improve the stability and the service life of the sCO2 turbine.
The technical scheme adopted by the invention is as follows:
a radial support system of a supercritical carbon dioxide turbine rotor comprises a turbine rotor and a plurality of bearing seats; the turbine rotor is provided with a plurality of bearing supporting sections, and the number of the bearing supporting sections is the same as that of the bearing seats; the radial tilting pad bearing comprises a bearing seat, a radial tilting pad bearing is arranged in a bearing seat inner hole, a plurality of groups of shape memory alloy springs and an annular metal wire mesh block are arranged between the outer wall of a bearing shell of the radial tilting pad bearing and the supporting shell, each group comprises two shape memory alloy springs positioned on the same bus of the bearing shell, the two shape memory alloy springs are respectively positioned on two sides of the metal wire mesh block, a bearing supporting section on a turbine rotor is supported in the corresponding radial tilting pad bearing, the bearing seat is connected with a heating/cooling device, and the heating/cooling device can heat or cool the radial tilting pad bearing.
The radial support system of the supercritical carbon dioxide turbine rotor comprises two bearing seats, wherein the two bearing seats are positioned at two ends of a turbine shell; the multiple groups of shape memory alloy springs are uniformly arranged along the circumferential direction.
In the radial support system for the supercritical carbon dioxide turbine rotor, the heating/cooling device comprises a cooler and a heat exchanger; the air outlet of the turbine shell is connected with a primary side inlet of the heat exchanger through a pipeline, a primary side outlet of the heat exchanger is connected with a main air outlet pipe and a cooler inlet, the main air outlet pipe is respectively connected with heating holes on the two bearing seats through the two air outlet pipes, the heating holes are communicated with the radial tilting pad bearing, and a valve is arranged on the main air outlet pipe; the outlet of the cooler is connected with a main cold air pipe, the main cold air pipe is respectively connected with cooling holes on the two bearing seats through the two cold air pipes, the cooling holes are communicated to the radial tilting pad bearings, and a valve is arranged on the main cold air pipe.
In the radial support system of the supercritical carbon dioxide turbine rotor, the inlet of the secondary side of the heat exchanger is connected with the outlet of the pump through a pipeline, the inlet of the pump is connected with the outlet of the condenser, the inlet of the condenser is connected with the air outlet of the compressor, the rotating shaft of the compressor is connected with one end of the turbine rotor through a coupler, and the other end of the turbine rotor is connected with the generator rotor through a coupler.
The radial support system of the supercritical carbon dioxide turbine rotor further comprises an eddy current displacement sensor, wherein the eddy current displacement sensor is placed on the bearing seat and used for monitoring the real-time vibration condition of the turbine rotor.
The technical scheme adopted by the invention has the following beneficial effects:
the invention has simple structure, can supply heating or cooling fluid to the bearing seat to regulate and control the temperature of the SMA spring, realizes the active control of radial support stiffness and damping, further inhibits the vibration of the rotor and ensures that the rotor safely and stably passes through the flexible critical rotating speed. According to the support mode of the SMA spring-metal wire mesh block-tilting pad bearing, the SMA spring is introduced, the temperature of the SMA spring is controlled to realize the phase change between martensite and austenite so as to realize the real-time change of radial rigidity, further avoid the peak value of the critical rotation speed amplitude of a rotor, and the metal wire mesh block is introduced to realize the large radial support damping to inhibit the rotor vibration. When the rotating speed of the rotor is close to the critical rotating speed of the rotor, the invention can monitor the real-time vibration condition of the rotor through a preset sensor, and in combination with an sCO2 turbine rotor-bearing test and control system, the heating or cooling fluid supplied to the bearing base is controlled in real time through a designed control algorithm, so that the proper SMA spring temperature is obtained to change the rigidity damping characteristic of the radial support, and the sCO2 turbine rotor is ensured to stably and safely pass through the flexible critical rotating speed.
Drawings
FIG. 1 is a schematic structural diagram of the present invention.
Fig. 2 is a front view of the connection of the support housing and the radial tilt pad bearing of the present invention.
Fig. 3 is a sectional view a-a in fig. 2.
Fig. 4 is a perspective view of the connection of the support housing and the radial tilt pad bearing of the present invention.
Fig. 5 is a schematic diagram of the overall power generation system of the sCO2 using the present invention.
FIG. 6 is a schematic view of a turbine rotor configuration of the present invention.
FIG. 7 is a schematic diagram of an sCO2 turbine rotor amplitude control method according to the invention.
Detailed Description
The invention will be further described with reference to the accompanying drawings.
As shown in fig. 1, the present invention includes a turbine rotor 9, an eddy current displacement sensor, and two bearing blocks 13 (the number of bearing blocks is not limited to two). Two bearing support sections 91 are arranged on the turbine rotor 9 (the number of the bearing support sections 91 is the same as that of the bearing blocks 13). A bearing shell 21 is arranged in an inner hole of the bearing seat 13, as shown in fig. 2-4, a radial tilting pad bearing 22 is arranged in the bearing shell 21, a plurality of groups of Shape Memory Alloy (SMA) springs 23 and an annular metal wire mesh block 24 are arranged between the outer wall of a bearing shell of the radial tilting pad bearing 22 and the bearing shell 21, the plurality of groups of shape memory alloy springs 23 are uniformly arranged along the circumferential direction, each group of shape memory alloy springs 23 comprises two shape memory alloy springs located on the same bus of the bearing shell, and the two shape memory alloy springs are respectively located on two sides of the metal wire mesh block 24. The tilting pad bearing 22 has excellent high speed stability and has lubrication channels inside and enclosed by end caps. The SMA springs 23 have different stiffness characteristics above and below the phase transition temperature; the wire mesh block 24 has a good damping characteristic; the SMA spring 23, the metal wire mesh block 24 and the radial tilting pad bearing 22 formed by matching the three have excellent high-speed stability of the rotor, and simultaneously can effectively avoid the peak amplitude of the critical rotating speed of the turbine rotor through temperature control. Two bearing segments 91 on the turbine rotor 9 are supported in two radial tilting pad bearings 22, respectively, and the bearing blocks are connected to a heating/cooling device, which can heat or cool the radial tilting pad bearings. The eddy current displacement sensor is placed on the bearing seat to monitor the real-time vibration condition of the turbine rotor.
The heating/cooling device comprises a cooler 4 and a heat exchanger 3; the air outlet of the turbine shell 14 is connected with the primary inlet of the heat exchanger 3 through a pipeline, the primary outlet of the heat exchanger 3 is connected with the main air outlet pipe and the inlet of the cooler 4, the main air outlet pipe is respectively connected with the heating holes on the two bearing seats 13 through the two air outlet pipes, the heating holes are communicated to the radial tilting pad bearing, and the main air outlet pipe is provided with a valve 19. The outlet of the cooler 4 is connected with a main cold air pipe, the main cold air pipe is respectively connected with cooling holes on the two bearing seats 13 through the two cold air pipes, the cooling holes are communicated to the radial tilting pad bearings, and the main cold air pipe is provided with a valve 20. Both the SMA spring 23 and the wire mesh block 24 can be heated or cooled by CO2 working medium controlled by valve 19 or valve 20. As shown in fig. 1 and 5, a secondary side inlet of the heat exchanger 3 is connected with an outlet of a pump 7 through a pipeline, an inlet of the pump 7 is connected with an outlet of a condenser 6, an inlet of the condenser 6 is connected with an air outlet of a compressor 5, a rotating shaft of the compressor 5 is connected with one end of a turbine rotor 9 through a coupler, and the other end of the turbine rotor 9 is connected with a rotor of the generator 2 through a coupler.
The high-pressure high-temperature CO2 working medium applies work through the turbine 1 to drive the turbine rotor 9 to rotate, the turbine rotor 9 drives the generator 2 and the compressor 5 to rotate together through the couplers at the two ends, the generator 2 outputs electric energy after rotating, and the compressor 5 compresses the low-pressure CO2 working medium into the high-pressure CO2 working medium after rotating. The CO2 working medium from the sCO2 turbine 1 changes from high pressure to low pressure, the temperature is also reduced, after the working medium enters the heat exchanger 3, the temperature of the low-pressure CO2 working medium is further reduced, and the working medium can be used as the heating gas of the SMA spring. After entering the cooler 4, the low-pressure CO2 working medium continues to drop in temperature, and can be used as cooling gas for the SMA spring. The low-temperature low-pressure CO2 working medium from the cooler 4 is changed into high-pressure CO2 working medium by the work of the compressor 5, enters the condenser 6 and the pump 7, is preheated by the heat exchanger 3, is changed into high-temperature high-pressure CO2 working medium by the heater 8, enters the sCO2 turbine 1 and drives the turbine rotor to rotate. The low pressure CO2 working fluid described above can be used as the fluid for heating/cooling the SMA spring.
As shown in fig. 6, the turbine rotor 9 includes a generator coupling connection section 92, a balance piston 93, a multistage axial turbine 10, a compressor coupling connection section 94, a shaft support section 91, and a dry gas seal connection section 12. The balance piston 93 may axially support the rotor against axial loads generated by turbine work. The multistage axial turbine 10 can effectively utilize a high-temperature and high-pressure CO2 working medium to push a turbine rotor to rotate at a high speed. The dry gas sealing connecting section 12 can effectively seal CO2 working medium by matching with the turbine shell 14, prevent CO2 leakage and isolate high temperature. The sCO2 turbine rotor is very long in axial length and has extremely high flexibility in itself because of the presence of integral balancing and sealing and coupling.
As shown in fig. 7, the turbine rotor 9, which is radially supported by the SMA spring 23-wire mesh block 24-radial tilting pad bearing 22 in the low and high temperature states, has different critical rotation speeds and amplitude peaks, wherein the rotor rotation speed corresponding to the point where both amplitudes are the same is called a shift rotation speed. The critical rotating speed and the amplitude peak value of the rotor in the low-temperature state are positioned on the left side of the conversion rotating speed, and the critical rotating speed and the amplitude peak value of the rotor in the high-temperature state are positioned on the right side of the conversion rotating speed. When the rotating speed of the rotor is increased from rest, the valve 19 is opened to control the high-temperature CO2 working medium to enter the bearing seat 13 and heat the SMA spring 23 to be above the phase change temperature, so that the rotor reaches the change rotating speed in the high-temperature state, then the rotating speed of the rotor is stabilized, the valve 19 is closed, the valve 20 is opened to control the low-temperature CO2 working medium to enter the bearing seat 13 and cool the SMA spring to be below the phase change temperature, and the rotor is continuously increased to the working rotating speed in the low-temperature state. When the rotating speed of the rotor is reduced from the working rotating speed, the valve 20 is opened to control the low-temperature CO2 working medium to enter the bearing seat 13 and cool the SMA spring to be below the phase change temperature, so that the rotating speed of the rotor is changed under the low-temperature state, then the rotating speed of the rotor is stabilized, the valve 20 is closed, the valve 19 is opened to control the high-temperature CO2 working medium to enter the bearing seat 13 and heat the SMA spring to be above the phase change temperature, and the rotor continues to be reduced to be static under the high-temperature state. Through the temperature control method, the peak amplitude of the sCO2 turbine rotor can be effectively avoided, and the rotor is ensured to safely pass through the flexible critical rotating speed in the speed increasing and reducing process.
Claims (5)
1. A radial support system of a supercritical carbon dioxide turbine rotor is characterized in that: comprises a turbine rotor and a plurality of bearing seats; the turbine rotor is provided with a plurality of bearing supporting sections, and the number of the bearing supporting sections is the same as that of the bearing seats; the radial tilting pad bearing comprises a bearing seat, a radial tilting pad bearing is arranged in a bearing seat inner hole, a plurality of groups of shape memory alloy springs and an annular metal wire mesh block are arranged between the outer wall of a bearing shell of the radial tilting pad bearing and the supporting shell, each group comprises two shape memory alloy springs positioned on the same bus of the bearing shell, the two shape memory alloy springs are respectively positioned on two sides of the metal wire mesh block, a bearing supporting section on a turbine rotor is supported in the corresponding radial tilting pad bearing, the bearing seat is connected with a heating/cooling device, and the heating/cooling device can heat or cool the radial tilting pad bearing.
2. The supercritical carbon dioxide turbine rotor radial support system of claim 1, wherein: the two bearing seats are positioned at two ends of the turbine shell; the multiple groups of shape memory alloy springs are uniformly arranged along the circumferential direction.
3. The supercritical carbon dioxide turbine rotor radial support system of claim 1, wherein: the heating/cooling device comprises a cooler and a heat exchanger; the air outlet of the turbine shell is connected with a primary side inlet of the heat exchanger through a pipeline, a primary side outlet of the heat exchanger is connected with a main air outlet pipe and a cooler inlet, the main air outlet pipe is respectively connected with heating holes on the two bearing seats through the two air outlet pipes, the heating holes are communicated with the radial tilting pad bearing, and a valve is arranged on the main air outlet pipe; the outlet of the cooler is connected with a main cold air pipe, the main cold air pipe is respectively connected with cooling holes on the two bearing seats through the two cold air pipes, the cooling holes are communicated to the radial tilting pad bearings, and a valve is arranged on the main cold air pipe.
4. The supercritical carbon dioxide turbine rotor radial support system of claim 3, wherein: the heat exchanger is characterized in that a secondary side inlet of the heat exchanger is connected with an outlet of a pump through a pipeline, an inlet of the pump is connected with an outlet of a condenser, an inlet of the condenser is connected with an air outlet of a compressor, a rotating shaft of the compressor is connected with one end of a turbine rotor through a coupler, and the other end of the turbine rotor is connected with a generator rotor through a coupler.
5. The supercritical carbon dioxide turbine rotor radial support system of claim 1, wherein: the eddy current displacement sensor is placed on the bearing seat and used for monitoring the real-time vibration condition of the turbine rotor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111374301.7A CN113898427A (en) | 2021-11-19 | 2021-11-19 | Radial support system of supercritical carbon dioxide turbine rotor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111374301.7A CN113898427A (en) | 2021-11-19 | 2021-11-19 | Radial support system of supercritical carbon dioxide turbine rotor |
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| Publication Number | Publication Date |
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| CN113898427A true CN113898427A (en) | 2022-01-07 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111374301.7A Pending CN113898427A (en) | 2021-11-19 | 2021-11-19 | Radial support system of supercritical carbon dioxide turbine rotor |
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| CN (1) | CN113898427A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11927105B1 (en) | 2022-09-16 | 2024-03-12 | General Electric Company | Thrust bearings to support axial thrust in pumps |
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2021
- 2021-11-19 CN CN202111374301.7A patent/CN113898427A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11927105B1 (en) | 2022-09-16 | 2024-03-12 | General Electric Company | Thrust bearings to support axial thrust in pumps |
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