CN117052492A - Turbine expander capable of adjusting gas-liquid two-phase deposition liquid drop sweeping gas - Google Patents
Turbine expander capable of adjusting gas-liquid two-phase deposition liquid drop sweeping gas Download PDFInfo
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- CN117052492A CN117052492A CN202311216310.2A CN202311216310A CN117052492A CN 117052492 A CN117052492 A CN 117052492A CN 202311216310 A CN202311216310 A CN 202311216310A CN 117052492 A CN117052492 A CN 117052492A
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- 239000007788 liquid Substances 0.000 title claims abstract description 59
- 230000008021 deposition Effects 0.000 title claims abstract description 17
- 238000010408 sweeping Methods 0.000 title claims abstract description 12
- 238000007789 sealing Methods 0.000 claims abstract description 38
- 230000000149 penetrating effect Effects 0.000 claims abstract description 4
- 238000010926 purge Methods 0.000 claims description 9
- 230000001105 regulatory effect Effects 0.000 claims description 5
- 239000007789 gas Substances 0.000 description 43
- 238000000034 method Methods 0.000 description 9
- 238000009833 condensation Methods 0.000 description 8
- 230000005494 condensation Effects 0.000 description 8
- 230000008569 process Effects 0.000 description 7
- 238000013461 design Methods 0.000 description 5
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 4
- 238000011160 research Methods 0.000 description 3
- 238000004781 supercooling Methods 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 150000001335 aliphatic alkanes Chemical class 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000002706 hydrostatic effect Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000005514 two-phase flow Effects 0.000 description 2
- 229910001069 Ti alloy Inorganic materials 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 238000007792 addition Methods 0.000 description 1
- 239000003570 air Substances 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 230000003628 erosive effect Effects 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 230000006911 nucleation Effects 0.000 description 1
- 238000010899 nucleation Methods 0.000 description 1
- 238000013021 overheating Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000008823 permeabilization Effects 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 230000002269 spontaneous effect Effects 0.000 description 1
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Classifications
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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
- F01D25/32—Collecting of condensation water; Drainage ; Removing solid particles
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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
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/003—Preventing or minimising internal leakage of working-fluid, e.g. between stages by packing rings; Mechanical seals
-
- 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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/14—Form or construction
- F01D5/147—Construction, i.e. structural features, e.g. of weight-saving hollow blades
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Architecture (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention discloses a turbine expander capable of adjusting gas-liquid two-phase deposition liquid drop sweeping gas, which comprises an expander shell and a rotor motor arranged in the expander shell, wherein the rotor motor is arranged on the inner side of the expander shell; the rotating shaft of the rotor motor is rotatably fixed with bearings arranged at two ends of the shell of the expander; one end of the rotating shaft extends out of the expansion end of the expander shell and then is fixed with the two-phase expansion impeller, and the other end extends out of the brake end of the expander shell and then is fixed with the brake impeller; a through hole penetrating to the back of the impeller wheel is arranged in each impeller flow passage of the two-phase expansion impeller; the inlet of the through hole is positioned at the inner slope surface of the impeller wheel back, and the outlet of the through hole is positioned at a position on the hub surface of the impeller flow channel, which is close to the outlet of the expansion impeller; a movable sealing disc is arranged at the impeller back of the two-phase expansion impeller; the back clearance between the movable sealing disc and the two-phase expansion impeller is adjusted, so that the air inflow of the through hole is adjusted. The invention can reduce the flow loss to improve the liquid carrying rate and the operation stability of the two-phase turboexpander.
Description
Technical Field
The invention relates to the technical field of two-phase turboexpanders, in particular to a turboexpander capable of adjusting gas-liquid two-phase deposition liquid drop sweeping gas.
Background
The working principle of the centripetal turbine expander is that high-temperature and high-pressure gas working medium is expanded in an impeller flow channel to generate momentum moment to drive an impeller to rotate for doing work, and the pressure and the temperature of the working medium are reduced after the working medium is expanded by the centripetal turbine. The actual thermodynamic process is similar to an isentropic expansion process, and the thermodynamic enthalpy value of the working medium is reduced after expansion, so that a part of internal energy is converted into mechanical energy. Therefore, the centripetal turbine expander not only can be used for low-temperature refrigeration (gas liquefaction and space environment simulation), but also can be widely used for various power cycles (organic Rankine cycle and kalina cycle), and the aim of energy conservation and emission reduction can be achieved by recycling the low-grade heat source.
In order to safely and stably operate, the working medium in the whole expansion process is kept in a single-phase overheat state under the operation working condition of the conventional centripetal turbine expander in the industry. However, in order to further improve the thermal efficiency and economy of the system, the design application of the centripetal turbine expander is gradually expanding from a pure single-phase region to a two-phase region. Based on theoretical analysis, when the expansion gas enters the two-phase region more deeply, the larger the specific enthalpy drop generated in the expansion process is, and the more cold energy or output work is produced. This means that the two-phase turboexpander has a larger expansion ratio and higher isentropic efficiency than the single-phase turboexpander under the same inlet conditions. However, when the gas expands from the superheating area to the two-phase area, the gas generates two-phase unbalanced condensation to form droplets with extremely small diameters which are uniformly distributed in a mist form or do not condense when the supercooling degree is small. Under the condition, the operation stability of the centripetal turbine is not affected basically, and the current centripetal turbine expander for the air separation equipment can easily realize the liquid carrying rate of 6-8%. However, when the supercooling degree is further increased, the rate of two-phase condensation is increased, and the particle size of the liquid drops is increased, liquid drops deposit on the surface of the impeller, and under the action of centrifugal force of the impeller, the deposited liquid is prevented from falling off and colliding with the impeller to form secondary liquid drops. The secondary droplets have a relatively large radius, which is the main cause of blade damage and rotor instability. If the problem of non-equilibrium condensation droplet deposition of a centripetal turbine can be improved to increase the liquid carrying rate of a two-phase permeabilization, a larger enthalpy drop can be achieved.
At present, two-phase flow research in a turboexpander is mainly focused on the field of theoretical research, and relevant scholars of national western security traffic universities perform numerical calculation on a nucleation model and a droplet growth model in the air two-phase flow process in a low-temperature turboexpander and analyze the loss of fluid. The theoretical research on the two-phase turboexpander internationally is almost blank.
In terms of practical application, domestic reports on the practical operation of the two-phase turboexpander are almost blank. In order to avoid potential hazards from droplet deposition during two-phase operation, enterprises are strictly demanding expander designs and gas overheating throughout the operation. In addition, to reduce erosion of two-phase fluids, materials such as high strength titanium alloys, 7075 aviation aluminum, and the like are often used or special material coatings are plated on the surfaces of the impellers to improve the life cycle of the two-phase turboexpander impellers and reduce flow losses. There are no other solutions to reduce the flow losses and unbalanced condensation droplet deposition of a two-phase turboexpander.
Disclosure of Invention
In order to solve the problem of unbalanced condensation droplet deposition of a centripetal turbine expander, the invention provides the turbine expander with adjustable gas-liquid two-phase deposition droplet sweeping gas, which can reduce flow loss so as to improve the liquid carrying rate and the operation stability of the two-phase turbine expander.
A turbine expander capable of adjusting gas-liquid two-phase deposition liquid drop sweeping gas comprises an expander shell and a rotor motor arranged in the expander shell; the rotating shaft of the rotor motor is rotatably fixed with bearings arranged at two ends of the shell of the expander;
one end of the rotating shaft extends out of the expansion end of the expander shell and then is fixed with the two-phase expansion impeller, and the other end extends out of the brake end of the expander shell and then is fixed with the brake impeller;
a through hole penetrating to the back of the impeller wheel is arranged in each impeller flow passage of the two-phase expansion impeller; the inlet of the through hole is positioned at the inner slope surface of the impeller wheel back, and the outlet of the through hole is positioned at a position on the hub surface of the impeller flow channel, which is close to the outlet of the expansion impeller;
a movable sealing disc is arranged at the impeller back of the two-phase expansion impeller; the periphery of the movable sealing disc is provided with a gear disc meshed with a pinion, and the pinion is connected with an output shaft of the gear adjusting motor; the pinion is driven to rotate by the gear adjusting motor, so that the back clearance between the movable sealing disc and the two-phase expansion impeller is adjusted, and the air inflow of the through hole is adjusted.
The turbine expander is suitable for air, methane and other alkane working medium gases, overheated gas enters from the volute inlet at the expansion end of the turbine expander, is guided by the volute and uniformly enters along the circumferential direction, completes the first expansion process in the stationary blade nozzle, reduces the temperature and the pressure, converts the internal energy of the gas into kinetic energy and increases the flow velocity. The high-speed gas continuously enters a two-phase expansion impeller rotating at a high speed for secondary expansion, the low-temperature gas is further cooled and possibly enters a two-phase region across a saturation line, when the supercooling degree is further increased, unbalanced spontaneous condensation of the gas can occur in a flow channel to form small liquid drops, and the condensed liquid drops can be attached to the surface of a blade or gather on the hub surface of the impeller flow channel along with the reduction of the temperature and the growth of the liquid drops. The hub surface in the impeller runner is communicated with the impeller back, and the working medium gas enters the back of the impeller through the dynamic and static gaps of the expansion impeller, so that the pressure of the back space is the same as the pressure of the impeller inlet. The pressure of the gas at the outlet of the impeller runner is lower after the gas is fully expanded, so that the pressure difference exists between the pressure of the back space of the impeller and the pressure of the outlet of the impeller, the back gas rapidly flows to the outlet of the impeller through the small holes, deposited liquid drops in the two-phase impeller runner can be blown off, and the large-range deposition of the two-phase unbalanced condensation liquid drops in the runner is avoided.
The gap between the impeller wheel back and the movable sealing disc can be flexibly adjusted, and the air inflow of the impeller wheel back is controlled by adjusting the size of the gap, so that the amount of sweeping air through the impeller through hole is controlled. The movable sealing disk is meshed with the pinion at the same time and driven by the gear motor, so that the relative position of the movable sealing disk and the expansion impeller can be adjusted.
Alternatively, the through hole may be an equal-diameter through hole, a tapered through hole or a tapered through hole. In order to achieve the purpose of reducing and increasing the pressure, when the flow speed Mach number of the back gas of the expansion impeller wheel is smaller than 1, the through hole adopts a convergent nozzle type, when the flow speed Mach number of the back gas of the expansion impeller wheel is larger than 1, the through hole adopts a divergent nozzle type, and when the flow speed Mach number of the gas is smaller than 1, the gas is required to realize Mach number larger than 1 through expansion, the convergent divergent nozzle type can be considered.
Alternatively, the number of through holes in each impeller runner can be 1 or more, and the number of through holes and the aperture size can be arranged and designed according to the flow rate of actual requirements.
Further, the impeller wheel back is integrally designed by adopting a groove structure.
Alternatively, the two-phase expansion impeller may be of the type employing a semi-open impeller, a closed impeller, an impeller with separating blades, or an impeller without separating blades.
The periphery of the two-phase expansion impeller is sleeved with a nozzle ring, a gap exists between an inlet of the expansion impeller of the two-phase expansion impeller and an inner ring of the nozzle ring, an expansion end volute fixed with the shell of the expander is arranged on the periphery of the nozzle ring, and the expansion end volute is used for circumferentially feeding air and sealing an expansion end.
The bearing of the expansion end is fixed on the shell of the expander through a radial bearing seat, and the movable sealing disc is respectively connected with the nozzle ring and the radial bearing seat through threads.
The movable sealing disc adopts a labyrinth sealing mode to add dry gas for sealing, and is used for ensuring that gas at the expansion end cannot leak through a gap between the rotating shafts.
When no liquid drops are deposited on the hub surface of the impeller flow channel of the two-phase expansion impeller, the back clearance between the movable sealing disc and the two-phase expansion impeller is regulated and reduced, so that the gas quantity passing through the back of the impeller is reduced, and the working efficiency of the expander is improved; when more liquid drops are deposited on the hub surface of the impeller flow channel of the two-phase expansion impeller, the back clearance between the movable sealing disc and the two-phase expansion impeller is regulated and increased, the air inflow of the back sweeping air of the impeller is improved, and the running stability of the expander is improved.
Compared with the prior art, the invention has the following beneficial effects:
1. aiming at the problem of deposition of two-phase unbalanced condensed liquid drops in a turbine expander in a refrigerating system, the invention carries out special design and transformation on the two-phase expansion impeller, achieves the purpose of automatic purging of the deposited liquid drops by utilizing the pressure difference between the impeller back and the impeller outlet, and further improves the liquid carrying rate of the two-phase turbine expander.
2. The turbine expander and the impeller structure form thereof provided by the invention can timely discharge deposited liquid drops in the impeller, effectively prevent a large amount of liquid drops from being gathered and impacted with the blades, and can improve the running stability of the two-phase turbine rotor.
3. According to the invention, the movable sealing disk is driven and regulated by the gear motor, so that the gap between the back of the expansion impeller and the movable sealing disk is changed, the air inflow can be regulated according to the operation condition, and the efficient purging of deposited liquid drops on the surface of the impeller is realized.
4. According to the two-phase impeller structure provided by the invention, gas reaches the hub surface through the small holes of the impeller, and a gas protection layer is formed on the bottom surface of the impeller runner, so that the impact loss can be reduced to a certain extent.
5. The two-phase expansion impeller provided by the invention can design the size and shape of a specific through hole according to actual requirements, and has a simple and compact structure, and the punching operation is easy to realize.
Drawings
FIG. 1 is a schematic illustration of a turbo expander of the present invention with an adjustable gas-liquid two-phase deposited droplet sweep gas;
FIG. 2 is a schematic diagram of a two-phase expansion impeller according to the present invention;
FIG. 3 is a schematic cross-sectional view of a phase expansion impeller of the present invention corresponding to different through holes;
FIG. 4 is a schematic view of a different version of an expander impeller of the present invention;
FIG. 5 is a schematic diagram of the adjustment mechanism of the movable sealing disk of the present invention;
FIG. 6 is a schematic view of two different states of the movable sealing disk in the present invention.
In the figure: 1-two-phase expansion impeller, 2-nozzle ring, 3-pinion, 4-gear adjusting motor, 5-rotating shaft, 6-rotor motor, 7-expander shell, 8-brake impeller, 9-expansion end volute, 10-movable sealing disk, 11-radial bearing seat, 12-bearing, 13-brake end guide vane ring, 14-brake end volute, 15-through hole, 16-impeller wheel back, 17-expansion impeller inlet, 18-expansion impeller outlet, 19-impeller runner hub surface, 20-closed impeller wheel cover.
Detailed Description
The invention will be described in further detail with reference to the drawings and examples, it being noted that the examples described below are intended to facilitate the understanding of the invention and are not intended to limit the invention in any way.
As shown in fig. 1, a turbo expander for an adjustable gas-liquid two-phase deposited droplet sweep gas comprises the following components: the two-phase expansion impeller 1, the nozzle ring 2, the pinion 3, the gear adjusting motor 4, the rotating shaft 5, the rotor motor 6, the expander housing 7, the brake impeller 8, the expansion end volute 9, the movable sealing disk 10, the radial bearing seat 11, the bearing 12, the brake end guide vane ring 13 and the brake end volute 14.
The two ends of the expander housing 7 are respectively provided with an expansion end volute 9 and a brake end volute 14. The rotor motor 6 is arranged in the expander shell 7, and the rotating shaft 5 of the rotor motor 6 is rotatably fixed with bearings 12 arranged at two ends of the expander shell 7. One end of the rotating shaft 5 extends out of the expansion end of the expander shell 7 and then is fixed with the two-phase expansion impeller 1, and the other end extends out of the braking end of the expander shell 7 and then is fixed with the braking impeller 8.
A through hole 15 penetrating to an impeller back 16 is arranged in each impeller flow passage of the two-phase expansion impeller 1; the inlet of the through hole 15 is positioned at the inner slope surface of the impeller back 16, and the outlet of the through hole 15 is positioned at a position on the impeller runner hub surface 19 close to the expansion impeller outlet 18.
In one embodiment, the shaft diameters of the two-phase expansion impeller 1 and the rotating shaft 5 are connected through bolts, a movable sealing disc 10 is arranged at the impeller back 16 of the two-phase expansion impeller 1, the movable sealing disc 10 is sealed by dry gas in a labyrinth seal mode, and the gas at the expansion end can be ensured not to leak through a gap between the rotating shafts.
The periphery of the two-phase expansion impeller 1 is sleeved with a nozzle ring 2, a certain gap is reserved between an inlet 17 of the expansion impeller and the inner ring of the nozzle ring 2, and the periphery of the nozzle ring 2 is provided with an expansion end volute 9 which is used for circumferentially feeding air and sealing an expansion end.
In the embodiment of the invention, the radial and axial bearings of the rotating shaft are hydrostatic gas bearings, and besides the hydrostatic gas bearings, the bearings can be in various bearing forms including but not limited to ball bearings, magnetic bearings and the like, and can be matched according to specific conditions. The other end of the rotating shaft is connected with a brake impeller 8, and a brake end is sealed by a brake end volute 14 and is communicated with an external pipeline.
As shown in fig. 2 (a) and (b), in the embodiment, the two-phase expansion impeller 1 is a semi-open impeller, the number of blades is 13, the number of impeller channels is 13, a through hole 15 is obliquely penetrated in each channel and is communicated with the impeller back 16, and the through hole 15 is an equal-diameter small hole. The high-pressure gas flowing out of the nozzle enters the impeller back 16 through the dynamic and static blade gaps, and the pressure of the impeller back 16 is higher than that of the impeller outlet, so that the gas driven by the pressure can quickly flow to the impeller runner hub surface 19 at the position of the impeller runner outlet from the through hole 15. When the gas is subjected to two-phase unbalanced condensation in the impeller flow channel due to nearly isentropic expansion and cooling, liquid drops are extremely easy to deposit in the flow channel, deposited liquid can be carried away from the impeller by through hole airflow, so that the possibility of forming large-scale liquid clusters is reduced, the impeller and the liquid clusters are prevented from being impacted and damaging the impeller, and the liquid carrying rate of the two-phase expander is improved.
In the embodiments of the present invention, suitable gases for the expander include, but are not limited to, air, nitrogen, carbon dioxide, methane and other alkane gases, and the number of blades and small holes of the expansion wheel are merely illustrative, and do not limit the present invention.
The adjusting mechanism of the movable sealing disc 10 is shown in fig. 5, one side, close to the impeller back 16, of the movable sealing disc 10 positioned behind the two-phase expansion impeller 1 is designed into a structure matched with the impeller back 16, two sides of the movable sealing disc 10 are respectively connected with the nozzle ring 2 and the radial bearing seat 11 in a threaded mode, the outer circle of the movable sealing disc 10 is meshed with the pinion 3 through a gear, and the rotation is controlled through the gear adjusting motor 4. Thus, the movable sealing disk 10 can be moved in the axial direction by the driving of the gear adjusting motor 4, by which the clearance between the two-phase expansion impeller 1 and the movable sealing disk 10 can be adjusted, thereby controlling the intake air amount of the purge gas.
Two different wheel back clearance states are shown in fig. 6, when no liquid drops are deposited on the hub surface of the expansion impeller, the small clearance adjustment method in fig. 6 (a) can be adopted, so that the gas quantity passing through the wheel back is reduced, the working efficiency of the expander is improved, when more liquid drops are deposited on the hub surface of the expansion impeller, the large clearance adjustment method in fig. 6 (b) can be adopted, the air inflow of the wheel back purge gas is improved, and a part of efficiency is sacrificed, so that the operation stability of the two-phase expander is improved.
In a specific application process, the shape of the through hole 15 on the two-phase expansion impeller 1 may have various forms, and referring to (a), (b), (c) and (d) in fig. 3, besides the equal-diameter through holes, the tapered, gradually-expanding and gradually-expanding through holes may be selected according to actual requirements. The inlet of the through hole 15 is positioned at the edge position of the impeller wheel back, the outlet of the through hole is positioned at the position of the impeller flow passage hub surface 19 close to the expansion impeller outlet 18, and the impeller wheel back 16 is integrally in a wedge-shaped design. The number of through holes in a single flow channel of the expansion impeller comprises but is not limited to 1.
The two-phase expansion impeller 1 may be a semi-open impeller, a closed impeller, an impeller with and without separating blades, or the like, as shown in fig. 4 (a) and (b).
The foregoing embodiments have described in detail the technical solution and the advantages of the present invention, it should be understood that the foregoing embodiments are merely illustrative of the present invention and are not intended to limit the invention, and any modifications, additions and equivalents made within the scope of the principles of the present invention should be included in the scope of the invention.
Claims (8)
1. The turbine expander capable of adjusting the gas-liquid two-phase deposition liquid drop sweeping gas is characterized by comprising an expander shell (7) and a rotor motor (6) arranged in the expander shell (7); the rotating shaft (5) of the rotor motor (6) and bearings (12) arranged at two ends of the expander shell (7) can be rotationally fixed;
one end of the rotating shaft (5) extends out of the expansion end of the expander shell (7) and then is fixed with the two-phase expansion impeller (1), and the other end extends out of the brake end of the expander shell (7) and then is fixed with the brake impeller (8);
a through hole (15) penetrating to the back of the impeller wheel is arranged in each impeller flow passage of the two-phase expansion impeller (1); the inlet of the through hole (15) is positioned at the inner slope surface of the impeller wheel back, and the outlet of the through hole (15) is positioned at a position close to the expansion impeller outlet (18) on the impeller runner hub surface;
a movable sealing disc (10) is arranged at the back of the impeller of the two-phase expansion impeller (1); the periphery of the movable sealing disc (10) is provided with a gear disc meshed with a pinion (3), and the pinion (3) is connected with an output shaft of a gear adjusting motor (4); the pinion (3) is driven to rotate by the gear adjusting motor (4), so that the back clearance between the movable sealing disc (10) and the two-phase expansion impeller (1) is adjusted, and the air inflow of the through hole (15) is adjusted.
2. The turbine expander with the adjustable gas-liquid two-phase deposition liquid drop sweeping gas according to claim 1, wherein the through holes (15) can be selected from different types such as equal-diameter through holes, convergent through holes, divergent through holes or convergent divergent through holes according to different working condition requirements, and the number of the through holes in each impeller runner is 1 or more.
3. The turbine expander for the adjustable gas-liquid two-phase deposition liquid drop purge gas of claim 1, wherein the impeller wheel back is integrally designed with a groove structure.
4. The turbine expander of the adjustable gas-liquid two-phase deposited liquid drop purge gas according to claim 1, wherein the two-phase expansion impeller (1) is selected from a plurality of different types such as a semi-open impeller, a closed impeller, an impeller with separating blades or an impeller without separating blades.
5. The turbine expander for the adjustable gas-liquid two-phase deposited liquid drop purge gas according to claim 1, wherein a nozzle ring (2) is sleeved on the periphery of the two-phase expansion impeller (1), a gap exists between an expansion impeller inlet (17) of the two-phase expansion impeller (1) and an inner ring of the nozzle ring (2), an expansion end volute (9) fixed with an expander shell (7) is arranged on the periphery of the nozzle ring (2), and the expansion end volute (9) is used for circumferential air inlet and sealing expansion ends.
6. The turbine expander with adjustable gas-liquid two-phase deposition liquid drop purge gas according to claim 5, wherein the bearing (12) at the expansion end is fixed on the expander housing (7) through a radial bearing seat (11), and the movable sealing disc (10) is respectively connected with the nozzle ring (2) and the radial bearing seat (11) through threads.
7. The turbine expander of the adjustable gas-liquid two-phase deposited liquid droplet purge gas of claim 1, wherein the movable sealing disk (10) is sealed with dry gas in the form of a labyrinth seal for ensuring that gas at the expansion end does not leak through the gap between the rotating shafts (5).
8. The turbine expander with the adjustable gas-liquid two-phase deposition liquid drop sweeping gas as claimed in claim 1, wherein when no liquid drop is deposited on the hub surface of the impeller flow channel of the two-phase expansion impeller (1), the back clearance between the movable sealing disc (10) and the two-phase expansion impeller (1) is adjusted and reduced, so that the amount of gas passing through the back of the impeller wheel is reduced, and the working efficiency of the expander is improved; when more liquid drops are deposited on the hub surface of the impeller flow channel of the two-phase expansion impeller (1), the back clearance between the movable sealing disc (10) and the two-phase expansion impeller (1) is regulated and increased, the air inflow of the back sweeping air of the impeller is improved, and the running stability of the expander is improved.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311216310.2A CN117052492A (en) | 2023-09-20 | 2023-09-20 | Turbine expander capable of adjusting gas-liquid two-phase deposition liquid drop sweeping gas |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311216310.2A CN117052492A (en) | 2023-09-20 | 2023-09-20 | Turbine expander capable of adjusting gas-liquid two-phase deposition liquid drop sweeping gas |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN117052492A true CN117052492A (en) | 2023-11-14 |
Family
ID=88666476
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311216310.2A Pending CN117052492A (en) | 2023-09-20 | 2023-09-20 | Turbine expander capable of adjusting gas-liquid two-phase deposition liquid drop sweeping gas |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117052492A (en) |
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2023
- 2023-09-20 CN CN202311216310.2A patent/CN117052492A/en active Pending
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