CN204783121U - Low discharge turbo -expander - Google Patents
Low discharge turbo -expander Download PDFInfo
- Publication number
- CN204783121U CN204783121U CN201520402959.8U CN201520402959U CN204783121U CN 204783121 U CN204783121 U CN 204783121U CN 201520402959 U CN201520402959 U CN 201520402959U CN 204783121 U CN204783121 U CN 204783121U
- Authority
- CN
- China
- Prior art keywords
- turbine
- blade
- expander
- turbo
- runner
- 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.)
- Withdrawn - After Issue
Links
Landscapes
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
The utility model discloses a low discharge turbo -expander of organic working medium. At least the organic working medium entry and the export that have including casing and casing, turbo -expander is established ties by two -stage turbine structure and constitutes, and first order turbine comprises turbine entad, and second level turbine comprises centrifugal turbine. The utility model discloses turbo -expander, its core energy conversion parts are the first order entad turbine nozzle and runner, mainly change about 80% energy, and another energy conversion parts are second level centrifugation turbine, mainly accomplish about 20% energy conversion, the extremely thick design of turbine blade adoption thickness, the runner adopts runner and speed reduction runner design with higher speed respectively, second level turbine export adoption diffuser structure, the utility model discloses combine the radial flow turbine pattern, provided the turbine blade of a novel shape line to little thermal current flow condition to combine this turbine blade shape, designed a neotype low discharge high efficiency turbo -expander.
Description
Technical field
The utility model belongs to dynamic power machine design field, especially belongs to a kind of low temperature exhaust heat and reclaims mechanical designing technique, particularly a kind of small flow turbo-expander.
Background technique
In the industrial production, waste heat energy ubiquity.The blast furnace gas of metallurgy industry, Iron Works vaporization cooling water, open hearth vaporization cooling water, the catalysis of petrochemical industry oil refining apparatus, cracking, coking cooling water, the roasting in chemical industry gas washing in SA production, burn sulphur operation etc. and all there is a large amount of waste heat.
These waste heat energy are divided into high temperature, middle temperature, low temperature three class usually, temperature higher than 650 DEG C be high-temperature residual heat, between 230 DEG C ~ 650 DEG C is middle temperature waste heat, lower than less than 230 DEG C be low temperature exhaust heat.For the recycling of middle high-temperature residual heat, a lot of and technology maturation of mode, such as, exhaust heat boiler recovery waste heat can be adopted to produce the water vapor of High Temperature High Pressure, water vapor enters steam turbine set acting and drives electrical power generators to export electric energy.And for the low temperature exhaust heat existed with forms such as flue gas, steam, high-temperature cooling waters, because its grade is not high, reuse efficiency is then much lower, even cannot reclaim.How efficiently, economically low grade heat energy huge for these total amounts is converted into the electric energy of high-quality, be the focus of association area scientific research personnel research both at home and abroad at present.
At present, the recovery for the low temperature exhaust heat energy mainly adopts organic rankie cycle (ORC) power generation system, can be electric energy by the thermal energy of low-quality thermal source by this system.Organic Rankine bottoming cycle take low-boiling-point organic compound as the Rankine cycle of working medium, primarily of the large parts composition of vaporizer, turbo-expander, condenser and working medium pump four, organic working medium absorbs heat in vaporizer from waste heat thermal source, the gaseous state of tool certain pressure and temperature is become from liquid state, gaseous working medium enters expansion work in turbo-expander, thus drive electrical generators or drag other dynamic power machine rotate.The gaseous working medium of discharging after turbo-expander decrease temperature and pressure is within the condenser to cooling water heat release, and working medium condenses into liquid state, and last liquid refrigerant flows in vaporizer again by working medium pump, constantly periodic duty.Turbo-expander is then the transformation of energy core component in organic working medium cycle power generation system.
The turbo-expander used in organic rankie cycle (ORC) power generation system and conventional water vapor steam turbine be nothing difference in essence in principle, its basic principle is still and utilizes nozzle and impeller that high temperature and high pressure gas is converted into high-velocity fluid, is then that the shaft work of rotating machinery exports by the kinetic transformation of high-velocity fluid.But because organic working medium is different from water vapour, must particular design be carried out when carrying out the design of organic working medium turbo-expander.
External organic working medium turbo-expander was developed to radial-flow type centripetal turbine machine by former xial flow steam turbine at present, radial-flow type centripetal turbine facility have the features such as loss is little, efficiency is high, rotating speed is high, volume is little, are the directions of organic working medium turbo-expander development.
Radial-flow type centripetal turbine decompressor is used for the recovery of low temperature exhaust heat, and current technology comparative maturity, isentropic efficiency can reach more than 80%.But, require larger thermal source flow.For some dispersions, the low temperature exhaust heat of small flow reclaims, radial-flow type centripetal turbine decompressor reuse efficiency is lower, or cannot reclaim.
Summary of the invention
The utility model discloses a kind of small flow turbo-expander of organic working medium according to the deficiencies in the prior art.Problem to be solved in the utility model is the recovery for improving the small flow low temperature exhaust heat energy further, proposes a kind of organic working medium turbo-expander of more excellent structure.
The utility model is achieved through the following technical solutions:
A kind of small flow turbo-expander, at least comprise the organic working medium entrance and exit that housing and housing have, it is characterized in that: turbo-expander is made up of two-stage turbine structures in series, first order turbine is made up of centripetal turbine, and second level turbine is made up of centrifugal turbine.
Described first order turbine comprises first order ring runner that organic working medium entrance connects, first order stator inside first order ring runner and centripetal turbine; Centripetal turbine comprises symmetrically arranged multiple centripetal blade, and each centripetal front side of vane and trailing edge are circular arc line, and vacuum side of blade is the camber line be formed by connecting by spline curve, and leaf head is circular arc chamfering; The platform flow channel width formed between adjacent centripetal blade is evenly reduced to outlet section by entrance.
Multiple nozzle entrance width that described first order stator is formed are greater than exit width.
Described second level turbine comprise be arranged at first order turbine outlet center second level stator, centrifugal turbine outside the stator of the second level, centrifugal turbine periphery diffusion runner and export with organic working medium the second level ring runner be connected; Centrifugal turbine comprises symmetrically arranged multiple centrifugal blade, and each centrifugal blade working surface, the back side and trailing edge are circular arc line, and centrifugal blade head is circular arc chamfering; The platform flow channel width formed between adjacent centrifugal blade first reduces rear increase by entrance to outlet section, and throat width is greater than exit width.
Described diffusion runner has blade to enlarge pressure runner or without blade to enlarge pressure runner; Have blade to enlarge pressure runner to be arranged around annular diffusion runner by the straight sheet evenly arranged, each straight sheet is arranged along diffusion runner radial skew.
Described centripetal blade and centrifugal blade are hollow-core construction or solid construction.
Described centripetal blade adopts the extremely thick design of thickness, and blade thickness reaches 40mm.
Described centrifugal blade adopts the extremely thick design of thickness, and blade thickness reaches 35mm.
Described centripetal blade and centrifugal blade height are straight line at the Changing Pattern in leaf height direction.
Described two-stage turbine is two axle construction of coaxial configuration or separation; The two-stage turbine of coaxial configuration drives same axis of rotation; Two axle construction be separated are that centripetal turbine drives an axis of rotation, and centrifugal turbine drives another rotating shaft to rotate backward.
The utility model turbo-expander is mainly used in organic Rankine bottoming cycle generating, and internal flow medium is organic working medium.Organic Rankine bottoming cycle take low-boiling-point organic compound as the Rankine cycle of working medium, primarily of the large parts composition of vaporizer, turbo-expander, condenser and working medium pump four, organic working medium absorbs heat in vaporizer from waste heat thermal source, the gaseous state of tool certain pressure and temperature is become from liquid state, gaseous working medium enters expansion work in turbo-expander, thus drive electrical generators or drag other dynamic power machine rotate.The gaseous working medium of discharging from turbo-expander is within the condenser to cooling water heat release, and working medium condenses into liquid state, and last liquid refrigerant flows in vaporizer again by working medium pump, constantly periodic duty.
The utility model internal flow medium is organic working medium, and preferred working medium is R245fa, and other organic working medium (as R23 etc.) or carbon dioxide also can use.
For the recovery of low-temperature heat source, extensively adopt organic rankie cycle system in the world at present, the core component that turbo-expander is changed as this system capacity, has had part company to make many products abroad.But under the restrictive condition of the little output power of little input flow rate, at present disclosed patent or document less.
Turbo-expander input hot-fluid flow is less, then can be fewer for the energy of conversion, and output power is less, and whole device volume is less, and runner is narrower, and flow losses are larger; But favourable one side is, the restriction being subject to heat from heat source size is less, and the scope of use is more extensive.The utility model, with reference to existing radial turbine pattern, proposes a kind of turbine blade of New shaped line mainly for little hot-fluid flow condition, and in conjunction with this turbine blade shape, devises a kind of novel small flow high efficiency turbo-expander.
General turbine flow is all much larger than the flow in the utility model design.If traditionally, the mass flow rate of turbo-expander is designed to 0.6kg/s, then the structure of turbo-expander then must be accomplished very little, be therefore unfavorable for processing and manufacture, and passages losses is larger.If adopt other forms of turbine, such as screw type turbine, although meet the little requirement of flow, energy recovery efficiency is very low, and the processing cost of screw rod is higher.
The utility model turbo-expander, its core energy conversion elements is first order centripetal turbine nozzle and runner, and the energy of main conversion about 80%, this grade of turbine runner is acceleration channels, and Peak Flow Rate does not reach local velocity of sound, belongs to subsonic speed runner.Main pressure recovery energy.
This grade of turbine wheel blade adopts the extremely thick design of thickness, and its design class like portion of runner runner, but has its obvious characteristic.The similar petal of blade shape, trailing edge and working surface are circular arc line, and vacuum side of blade is then formed by connecting by several spline curve, and leaf head is circular arc chamfering.
Runner the best is made up of 8 blades, and runner is from outer inlets to interior side outlet, and width of flow path evenly reduces, and because blade height numerical value is less, is only 10 millimeter, and in order to easy to process, leaf height direction adopts the stacking rule of straight line.Blade number can choose other numerical value according to flow difference, and leaf height direction also can adopt other stacking rules such as circular arc, in addition, because vane thickness is very thick, in order to reduce the rotary inertia of runner, also blade interior can be emptied, only retaining the even of 5-10mm or non-uniform wall thickness.
Another energy conversion elements of the utility model turbo-expander is second level centrifugal turbine, mainly completes the transformation of energy of about 20%.This grade of turbine is deceleration runner, is also subsonic speed runner, main recovery speed energy and fraction pressure energy.
This grade of turbine wheel blade adopts the extremely thick design of thickness equally, but has obvious difference with the centripetal blade of the first order.Front side of vane, the back side and trailing edge are circular arc line.Leaf head is rounding, but this rounding radii is larger than first order turbine.
Second level runner the best is made up of 9 blades, and flowing medium flows to outer outlets from side-entrance in runner, and width of flow path increases, and in order to easy to process, leaf height direction adopts the stacking rule of straight line.
Blade number in turbine at the corresponding levels can choose other numerical value according to flow difference, and leaf height direction also can adopt other stacking rules such as circular arc.In addition, because vane thickness is very thick, in order to reduce the rotary inertia of runner, also blade interior can be emptied, only retaining the even of 5-10mm or non-uniform wall thickness.
In addition, second level turbine outlet has Diffuser, Diffuser adopt vaned diffuser or without blade to enlarge pressure, vaned diffuser blade is prismatic blade, is in tilted layout, number of blade the best is 46.
When adopting vaned diffuser, flow losses are little, and energy conversion efficiency is higher.
Accompanying drawing explanation
Fig. 1 is a kind of feature cross-section schematic diagram of the utility model turbo-expander;
Fig. 2 is the utility model turbo-expander structural blast schematic diagram;
Fig. 3 is the utility model turbo-expander first order stator and centripetal turbine structural upright schematic diagram;
Fig. 4 is the utility model turbo-expander first order stator and centripetal turbine structural plan schematic diagram;
Fig. 5 is the utility model turbo-expander first order stator schematic perspective view;
Fig. 6 is the utility model turbo-expander centripetal turbine structural upright schematic diagram;
Fig. 7 is the centripetal blade structure schematic diagram of the utility model turbo-expander;
Fig. 8 is the utility model turbo-expander centrifugal turbine and has straight sheet diffusion flow passage structure schematic perspective view;
Fig. 9 is the utility model turbo-expander centrifugal turbine and has straight sheet diffusion flow passage structure floor map;
Figure 10 is that the utility model turbo-expander has straight sheet diffusion flow passage structure schematic perspective view;
Figure 11 is the utility model turbo-expander centrifugal turbine structural upright schematic diagram;
Figure 12 is the utility model turbo-expander centrifugal turbine and without straight sheet diffusion flow passage structure floor map;
Figure 13 is the utility model turbo-expander centrifugal blade structural representation;
Figure 14 is the utility model turbo-expander second level guide vane structure schematic diagram;
Figure 15 is the utility model turbine expansion engine housing;
Figure 16 is the utility model turbo-expander centripetal leaf cross-section hollow-core construction schematic diagram;
Figure 17 is the utility model turbo-expander centrifugal blade cross section hollow-core construction schematic diagram;
Figure 18 is the utility model turbo-expander separating rotary shaft feature cross-section schematic diagram.
In figure, 1 is housing, 11 is working medium entrances, 12 is sender property outlets, 13 is first order ring runners, 14 is second level ring runners, 2 is first order stators, 2a is stator nozzle, 3 is centripetal turbines, 3a is centripetal turbine platform flow channel, 31 is centripetal leaf heads, 32 is centripetal front side of vanes, 33 is centripetal blade trailing edges, 34 is centripetal vacuum side of blades, 4 is rotating shafts, 5 is positioning blocks, 5a is second level stator, 6 is centrifugal turbines, 6a is centrifugal turbine platform flow channel, 61 is centrifugal blade heads, 62 is centrifugal blade working surfaces, 63 is centrifugal blade trailing edges, 64 is the centrifugal blade back side, 7 is diffusion runners, 7a is straight sheet, 8 is pedestals, 9 is second rotating shafts.
Embodiment
Below by embodiment, the utility model is specifically described; embodiment is only for being further detailed the utility model; can not be interpreted as the restriction to the utility model protection domain, some nonessential improvement that those skilled in the art makes according to above-mentioned content of the present utility model and adjustment also belong to the scope of the utility model protection.
Composition graphs 1 to Fig. 9.
A kind of small flow turbo-expander, at least comprise organic working medium entrance 11 and outlet 12 that housing 1 and housing 1 have, turbo-expander is made up of two-stage turbine structures in series, and first order turbine is made up of centripetal turbine 3, and second level turbine is made up of centrifugal turbine 6.
First order turbine comprises first order ring runner 13 that organic working medium entrance 11 connects, first order stator 2 inside first order ring runner 13 and centripetal turbine 3; Centripetal turbine 3 comprises symmetrically arranged multiple centripetal blade, and each centripetal front side of vane 32 and trailing edge 33 are circular arc line, and vacuum side of blade 34 is the camber lines be formed by connecting by spline curve, and leaf head 31 is circular arc chamfering; The centripetal turbine platform flow channel 3a width formed between adjacent centripetal blade is evenly reduced to outlet section by entrance.
Multiple stator nozzle 2a throat widths that first order stator 2 is formed are greater than exit width.
Second level turbine comprise be arranged at first order turbine outlet center second level stator 5a, second level stator 5a outside centrifugal turbine 6, centrifugal turbine 6 periphery diffusion runner 7 and export with organic working medium the second level ring runner 14 be connected; Centrifugal turbine 6 comprises symmetrically arranged multiple centrifugal blade, and each centrifugal blade working surface 62, the back side 64 and trailing edge 63 are circular arc line, and leaf head 61 is circular arc chamfering; The centrifugal turbine platform flow channel 6a width formed between adjacent centrifugal blade first reduces rear increase by entrance to outlet section, and throat width is greater than exit width.
Diffusion runner 7 has blade to enlarge pressure runner or without blade to enlarge pressure runner; Have blade to enlarge pressure runner to be arranged around annular diffusion runner 7 by the straight sheet 7a evenly arranged, each straight sheet 7a is arranged along diffusion runner radial skew.
As shown in Figure 1, Fig. 1 is the utility model turbo-expander feature cross-section schematic diagram, illustrates each Component composition configuration state of turbo-expander adopting the utility model structure in figure.
Fig. 2 to Figure 15 adopts the turbo-expander of the utility model structure each component partition status architecture schematic diagram.
Figure 16 and Figure 17 is the centripetal blade of the utility model and centrifugal blade sectional view, and each figure all illustrates the hollow structure of the utility model blade.
The utility model structure turbo-expander is utilized to provide following embodiment:
Embodiment 1
Suck spiral case inlet stagnation pressure 1.12MPa, stagnation temperature 370K, mass flow rate 0.6kg/s, specific enthalpy 474KJ/kg; Discharge volute outlet stagnation pressure 0.34MPa, stagnation temperature 364.7K; Working medium is R245fa; Wheel speed 8000r/min.This turbo-expander isentropic efficiency is about 77%, effective air horsepower 2.6kW.Two-stage turbine rotating speed size and Orientation is identical, drives same generator by the same axis.
Embodiment 2
In conjunction with Figure 18, as shown in the figure, spiral case inlet stagnation pressure 1.12MPa is sucked, stagnation temperature 370K, mass flow rate 0.6kg/s, specific enthalpy 474KJ/kg; Discharge volute outlet stagnation pressure 0.34MPa, stagnation temperature 364.7K; Working medium is R245fa; Both stage impellers rotating speed is 8000r/min.This turbo-expander is counter rotating turbine.Due to different in the intermediate guide blade of this example and embodiment 1, for on-bladed design, this place deflection angle that flows is less than embodiment 1, and flow losses are less; Meanwhile, contrary owing to turning to, secondary centrifugal turbine blade lays direction and embodiment 1 is contrary, and because flow losses reduce, isentropic efficiency is higher, is about 85%, effective air horsepower 2.9kW.But two-stage turbine disalignment, sense of rotation is contrary, drives respective generator respectively.
Claims (10)
1. a small flow turbo-expander, at least comprise the organic working medium entrance and exit that housing and housing have, it is characterized in that: turbo-expander is made up of two-stage turbine structures in series, first order turbine is made up of centripetal turbine, and second level turbine is made up of centrifugal turbine.
2. small flow turbo-expander according to claim 1, is characterized in that: described first order turbine comprises first order ring runner that organic working medium entrance connects, first order stator inside first order ring runner and centripetal turbine; Centripetal turbine comprises symmetrically arranged multiple centripetal blade, and each centripetal front side of vane and trailing edge are circular arc line, and vacuum side of blade is the camber line be formed by connecting by spline curve, and leaf head is circular arc chamfering; The centripetal turbine platform flow channel width formed between adjacent centripetal blade is evenly reduced to outlet section by entrance.
3. small flow turbo-expander according to claim 2, is characterized in that: multiple nozzle entrance width that described first order stator is formed are greater than exit width.
4. the small flow turbo-expander according to claim 1 or 2 or 3, is characterized in that: described second level turbine comprise be arranged at first order turbine outlet center second level stator, centrifugal turbine outside the stator of the second level, centrifugal turbine periphery diffusion runner and export with organic working medium the second level ring runner be connected; Centrifugal turbine comprises symmetrically arranged multiple centrifugal blade, and each centrifugal blade working surface, the back side and trailing edge are circular arc line, and centrifugal blade head is circular arc chamfering; The centrifugal turbine platform flow channel width formed between adjacent centrifugal blade first reduces rear increase by entrance to outlet section, and throat width is greater than exit width.
5. small flow turbo-expander according to claim 4, is characterized in that: described diffusion runner has blade to enlarge pressure runner or without blade to enlarge pressure runner; Have blade to enlarge pressure runner to be arranged around annular diffusion runner by the straight sheet evenly arranged, each straight sheet is arranged along diffusion runner radial skew.
6. small flow turbo-expander according to claim 5, is characterized in that: described centripetal blade and centrifugal blade are hollow-core construction or solid construction.
7. small flow turbo-expander according to claim 5, is characterized in that: described centripetal blade adopts the extremely thick design of thickness, and blade thickness reaches 40mm.
8. small flow turbo-expander according to claim 5, is characterized in that: described centrifugal blade adopts the extremely thick design of thickness, and blade thickness reaches 35mm.
9. small flow turbo-expander according to claim 5, is characterized in that: described centripetal blade and centrifugal blade height are straight line at the Changing Pattern in leaf height direction.
10. small flow turbo-expander according to claim 5, is characterized in that: described two-stage turbine is two axle construction of coaxial configuration or separation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520402959.8U CN204783121U (en) | 2015-06-12 | 2015-06-12 | Low discharge turbo -expander |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520402959.8U CN204783121U (en) | 2015-06-12 | 2015-06-12 | Low discharge turbo -expander |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204783121U true CN204783121U (en) | 2015-11-18 |
Family
ID=54523189
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520402959.8U Withdrawn - After Issue CN204783121U (en) | 2015-06-12 | 2015-06-12 | Low discharge turbo -expander |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204783121U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104863642A (en) * | 2015-06-12 | 2015-08-26 | 西华大学 | Small flow turbine expansion machine |
| CN105937415A (en) * | 2016-06-08 | 2016-09-14 | 西安交通大学 | Supercritical carbon dioxide turbine device capable of adapting to large-range back pressure and flow |
| CN106930786A (en) * | 2017-04-27 | 2017-07-07 | 西安交通大学 | A kind of multistage radial-flow type counter rotating turbine structure |
-
2015
- 2015-06-12 CN CN201520402959.8U patent/CN204783121U/en not_active Withdrawn - After Issue
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104863642A (en) * | 2015-06-12 | 2015-08-26 | 西华大学 | Small flow turbine expansion machine |
| CN104863642B (en) * | 2015-06-12 | 2016-06-15 | 西华大学 | A kind of low discharge turbo-expander |
| CN105937415A (en) * | 2016-06-08 | 2016-09-14 | 西安交通大学 | Supercritical carbon dioxide turbine device capable of adapting to large-range back pressure and flow |
| CN106930786A (en) * | 2017-04-27 | 2017-07-07 | 西安交通大学 | A kind of multistage radial-flow type counter rotating turbine structure |
| CN106930786B (en) * | 2017-04-27 | 2020-07-28 | 西安交通大学 | Multistage radial-flow type counter-rotating turbine structure |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN204783121U (en) | Low discharge turbo -expander | |
| CN101915196A (en) | Double-runner ultra-low specific speed axial flow hydraulic turbine for driving cooling tower fan | |
| CN110043323A (en) | A kind of supersonic speed radial-inward-flow turbine | |
| CN106415154B (en) | Device and method for converting thermal energy | |
| CN104863642B (en) | A kind of low discharge turbo-expander | |
| US20150082793A1 (en) | Device for power generation according to a rankine cycle | |
| CN110836131A (en) | Supercritical carbon dioxide recompression circulating turbine mechanical system | |
| CN209308988U (en) | A kind of ventilation equipment | |
| CN104100301A (en) | Multi-stage differential pressure radial flow turbine capable of adjusting nozzle ring opening | |
| CN208934745U (en) | A kind of parallel connection double end difference exhaust centripetal turbine device | |
| CN100337013C (en) | Radial-flow steam turbine | |
| CN102667063A (en) | Radial turbine | |
| CN205779035U (en) | A kind of turbo-expander being applicable to organic rankine cycle system | |
| EP3119991B1 (en) | Centrifugal radial turbine | |
| CN107725481B (en) | Structure and method for improving compression ratio of centrifugal vapor compressor | |
| CN208040454U (en) | Rotor, steam turbine and prime mover equipment of steam turbine | |
| CN110469369A (en) | A kind of kW grade supercritical carbon dioxide radial turbine structure with splitterr vanes | |
| CN114396314B (en) | Supersonic axial flow composite bladeless turbine | |
| CN110159353B (en) | Megawatt-level supercritical carbon dioxide centripetal turbine device | |
| CN114382551B (en) | Energy-saving method for steam turbine, steam turbine blade and energy-saving steam turbine structure | |
| CN109538513A (en) | A kind of ventilation equipment | |
| CN204458540U (en) | The flow guide device of bidirectional reversible propeller fan | |
| CN210715175U (en) | Axial flow compressor of small and medium-sized gas turbine | |
| CN203847174U (en) | Stator steam inlet structure of radial-flow turbine | |
| CN109844265A (en) | It is suitable for the multiatage axial flow turbine run under low vapor (steam) temperature |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20151118 Effective date of abandoning: 20160615 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |