CN110966051A - Turbine expansion machine - Google Patents
Turbine expansion machine Download PDFInfo
- Publication number
- CN110966051A CN110966051A CN201911156201.XA CN201911156201A CN110966051A CN 110966051 A CN110966051 A CN 110966051A CN 201911156201 A CN201911156201 A CN 201911156201A CN 110966051 A CN110966051 A CN 110966051A
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- bearing
- assembly
- magnetic suspension
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- turbine
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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
- F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
- F01D15/10—Adaptations for driving, or combinations with, electric generators
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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
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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
-
- 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
- F01D25/14—Casings modified therefor
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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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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Abstract
The invention provides a turboexpander, which comprises a turbine shell, a volute fixedly connected to one end of the turbine shell, a rotating shaft accommodated in the turbine shell and the volute, a turbine assembly fixedly connected to one end of the rotating shaft and accommodated in the volute, and a magnetic suspension bearing assembly and a generator assembly which are sleeved on one end of the rotating shaft, far away from the turbine assembly and fixedly connected to the turbine shell; the magnetic suspension bearing assembly comprises at least two radial magnetic suspension bearing assemblies and an axial magnetic suspension bearing assembly; the volute comprises a diffuser pipe and a nozzle assembly, the turbine assembly is contained at one end, close to the nozzle assembly, of the diffuser pipe, gas enters the turbine assembly through the nozzle assembly and is expanded to do work and cool, the rotating shaft is driven to rotate, and the generator assembly generates electric energy under the driving of the rotating shaft. The turboexpander provided by the invention is simple to manufacture, good in reliability and convenient to control.
Description
[ technical field ] A method for producing a semiconductor device
The invention relates to the field of refrigeration and low-temperature engineering, in particular to a turboexpander.
[ background of the invention ]
The turboexpander is a key unit necessary for obtaining cold energy of air separation equipment, natural gas (petroleum gas) liquefaction separation equipment, low-temperature crushing equipment and the like, and is a heart for ensuring the stable operation of the whole set of equipment.
The turboexpander is a rotating machine, and the support of a bearing is necessary. The existing turboexpander usually adopts a gas bearing, and the gas bearing is mainly divided into a static pressure gas bearing and a dynamic pressure gas bearing. When the static pressure gas bearing works, high-pressure hydrogen is required to be extracted from a system loop at any time to supply gas to the bearing, the suspension force is maintained, the complexity of the device is increased, the process gas loss of the whole large-scale liquefaction process is caused, the system efficiency is reduced, and the cost of the hydrogen liquefaction process is increased. For the dynamic pressure gas bearing, although extra gas supply is not needed, the working medium of the air bearing is hydrogen, the viscosity density is very low, the bearing capacity is limited, the stability is poor, and the air bearing is not suitable for shafting support with larger mass. Although the foil type dynamic pressure gas bearing can solve the problems of insufficient bearing capacity and poor stability, the problem of friction and abrasion between the inner foil and a shaft in the starting and speed reducing processes is solved, the processing is difficult, and the regular maintenance is needed for a period of time. Meanwhile, small molecular hydrogen is easy to leak under large pressure difference, a longer sealing section is required to be arranged on the air bearing to prevent working gas from leaking, and the sealing structure is a strong nonlinear vibration excitation source and has great influence on shafting design and whole machine structure layout.
In addition, the gas bearing has high requirements on processing and manufacturing precision, and the processing precision greatly influences the availability and stability of the air bearing system. In order to provide sufficient levitation force and stability for the hydrostatic gas bearing, the clearance between the rotor and the bearing is usually 20 μm or less, the diameter of the bearing air hole is about 100 μm, and the overall machining accuracy is preferably 1 μm or less. For the dynamic pressure gas bearing, the foil structure and the manufacturing process are very complex, the requirement of the surface wear-resistant coating is strict, and the accumulation of the related technology in China is weak at present. In addition, the gas bearing requires small fit clearance, the assembly precision is very high, the maintenance, assembly and maintenance are inconvenient, and once the unstable rotating shaft is easy to lock in the working stage, irretrievable loss is caused.
In view of the above, it is desirable to provide a new turboexpander to overcome the above-mentioned drawbacks.
[ summary of the invention ]
The invention aims to provide a turboexpander which is simple to manufacture, good in reliability and convenient to control.
In order to achieve the above object, the present invention provides a turboexpander, including a turbine housing, a volute fixedly connected to one end of the turbine housing, a rotating shaft accommodated in the turbine housing and the volute, a turbine assembly fixedly connected to one end of the rotating shaft and accommodated in the volute, and a magnetic suspension bearing assembly and a generator assembly simultaneously sleeved on one end of the rotating shaft away from the turbine assembly and fixedly connected to the turbine housing; the magnetic suspension bearing assembly comprises at least two radial magnetic suspension bearing assemblies and an axial magnetic suspension bearing assembly; the volute comprises a diffuser pipe and a nozzle assembly, the turbine assembly is contained at one end, close to the nozzle assembly, of the diffuser pipe, gas enters the turbine assembly through the nozzle assembly and expands to do work and cool, the rotating shaft is driven to rotate, and the generator assembly is driven by the rotating shaft to generate electric energy.
In a preferred embodiment, the number of the radial magnetic suspension bearing assemblies is two, and the two radial magnetic suspension bearing assemblies are respectively positioned at two ends of the rotating shaft; the turbine shell is internally provided with an accommodating cavity, an inner wall of the accommodating cavity is protruded to form an upper radial bearing fixing boss and a lower radial bearing fixing boss which are arranged at intervals, and the two radial magnetic suspension bearing assemblies are respectively fixed on the upper radial bearing fixing boss and the lower radial bearing fixing boss.
In a preferred embodiment, each radial magnetic suspension bearing assembly comprises a sensor rotor, a bearing rotor, a sensor stator, a radial bearing stator and a radial bearing bracket, wherein the sensor stator corresponds to and is sleeved on the sensor rotor and the bearing rotor respectively; the sensor rotor and the bearing rotor are respectively sleeved on the rotating shaft and are in interference fit with the rotating shaft, and the sensor stator and the radial bearing stator are respectively arranged at intervals with the corresponding sensor rotor and the corresponding bearing rotor; the radial bearing support is used for clamping and fixing the sensor stator and the radial bearing stator; and the radial bearing supports corresponding to the two radial magnetic suspension bearing assemblies are respectively abutted against the upper radial bearing fixing boss and the lower radial bearing fixing boss, and the radial bearing is fixedly connected with the corresponding upper radial bearing fixing boss and the lower radial bearing fixing boss through connecting pieces.
In a preferred embodiment, the axial magnetic bearing assembly is clamped between the two radial magnetic bearing assemblies, and the inner wall of the accommodating cavity is protruded to form an axial bearing fixing boss clamped between the upper radial bearing fixing boss and the lower radial bearing fixing boss; the axial magnetic suspension bearing assembly is fixed on the axial bearing fixing boss.
In a preferred embodiment, the axial magnetic suspension bearing assembly comprises two axial bearing stators which are oppositely arranged at intervals and an axial magnetic suspension bracket for fixing the two axial bearing stators; the rotating shaft comprises an integrally formed main shaft and a thrust disc fixed on the main shaft, and the thrust disc is clamped between the two axial bearing stators; and an axial bearing support of the axial magnetic suspension bearing assembly is abutted against the axial bearing fixing boss, and the axial bearing support is fixedly connected with the axial bearing fixing boss through a connecting piece.
In a preferred embodiment, the generator assembly includes a generator rotor and a generator stator sleeved on the generator rotor, and the generator stator is accommodated in the accommodating cavity and fixed with the turbine housing.
In a preferred embodiment, the turboexpander further comprises a thermally insulating material; the thermal insulation material is filled at one end of the volute close to the turbine shell; the rotating shaft penetrates through the heat insulation material, the turbine assembly is located on one side, close to the volute, of the heat insulation material, and the magnetic suspension bearing assembly and the generator assembly are located on one side, away from the turbine assembly, of the heat insulation material.
In a preferred embodiment, a surface of the main shaft at an end thereof adjacent the turbine assembly is provided with a helical raised formation which is in sealing engagement with the thermally insulating material.
In a preferred embodiment, a first sealing gas flow passage is provided in the heat insulating material, and a second sealing gas flow passage communicating with the first sealing gas flow passage is provided in the housing.
In a preferred embodiment, the turbine housing is cylindrical and is provided with a spiral cooling channel.
In a preferred embodiment, the main shaft is hollow.
According to the turboexpander, the magnetic suspension bearing assembly is used for replacing a traditional gas bearing, so that the processing and manufacturing difficulty of the bearing is reduced, the bearing capacity and rigidity of the bearing are increased, and the reliability of a rotor system is improved; in addition, the generator is adopted for braking, compared with the traditional fan wheel and booster wheel, the regulation response is quicker, the rotating speed is easier to control accurately, the braking mode omits the sealing of the braking end, the braking gas loop is reduced, the integral structure is simplified, the loss of process gas is reduced, the recovery of braking power is realized, the requirements of energy conservation and emission reduction are met, and particularly when the turbine power is larger, the value is more obvious. In addition, the main shaft is a hollow shaft, so that the axial heat conductivity coefficient is greatly reduced, and the cold loss and the thermal deformation of a low-temperature end are avoided.
[ description of the drawings ]
Fig. 1 is a perspective view of a turboexpander provided by the present invention.
Fig. 2 is a sectional view of the turboexpander shown in fig. 1.
Fig. 3 is a cross-sectional view of the shaft of the turboexpander shown in fig. 2 in cooperation with the sensor rotor, the bearing rotor, the generator rotor and the turbine assembly.
[ detailed description ] embodiments
In order to make the objects, technical solutions and advantageous effects of the present invention more clearly apparent, the present invention is further described in detail below with reference to the accompanying drawings and the detailed description. It should be understood that the detailed description and specific examples, while indicating the preferred embodiment of the invention, are intended for purposes of illustration only and are not intended to limit the scope of the invention.
Referring to fig. 1 and 2, the present invention provides a turbine expander 100, which includes a turbine housing 10, a volute 20 fixedly connected to one end of the turbine housing 10, a rotating shaft 30 accommodated in the turbine housing 10 and the volute 20, a turbine assembly 40 fixedly connected to one end of the rotating shaft 30 and accommodated in the volute 10, and a magnetic suspension bearing assembly 50 and a generator assembly 60 simultaneously sleeved on one end of the rotating shaft 30 far away from the turbine assembly 40 and fixedly connected to the turbine housing 10.
Wherein the magnetic levitation bearing assembly 50 comprises at least one radial magnetic levitation bearing assembly 51 and an axial magnetic levitation bearing assembly 52. The volute 20 comprises a diffuser pipe 21 and a nozzle assembly 22, the turbine assembly 40 is accommodated in one end, close to the nozzle assembly 22, of the diffuser pipe 21, the gas drives the turbine assembly 40 to rotate, the rotating shaft 30 is further driven to rotate, and the generator assembly 60 generates electric energy under the driving of the rotating shaft 30.
Referring to fig. 3, in this embodiment, the number of the radial magnetic suspension bearing assemblies 51 is two, and the two radial magnetic suspension bearing assemblies 51 are respectively located at two ends of the rotating shaft 30, so that the rotating shaft 30 can rotate smoothly, and the rotating shaft 30 is prevented from polarization. The turbine shell 10 is internally provided with a containing cavity 101, an inner wall of the containing cavity 101 protrudes to form an upper radial bearing fixing boss 1011 and a lower radial bearing fixing boss 1012 which are arranged at intervals, and the two radial magnetic suspension bearing assemblies 51 are respectively fixed on the upper radial bearing fixing boss 1011 and the lower radial bearing fixing boss 1012. The arrangement of the upper radial bearing fixing boss 1011 and the lower radial bearing fixing boss 1012 facilitates the fixed connection of the two radial magnetic suspension bearing assemblies 51 with the turbine housing 10.
Further, each radial magnetic suspension bearing assembly 51 comprises a sensor rotor 511, a bearing rotor 512, a sensor stator 513 corresponding to and sleeved on the sensor rotor 511 and the bearing rotor 512, a radial bearing stator 514 and a radial fixing bracket 515. The sensor rotor 511 and the bearing rotor 512 are respectively sleeved on the rotating shaft 30 and are in interference fit with the rotating shaft 30, and are used for preventing the sensor rotor 511 and the bearing rotor 512 from rotating relative to the rotating shaft 30. The sensor stator 513 and the radial bearing stator 514 are respectively arranged at intervals with the corresponding sensor rotor 511 and the corresponding bearing rotor 512, so that the sensor stator 513 and the radial bearing stator 514 are prevented from being contacted or rubbed with the corresponding sensor rotor 511 and the corresponding bearing rotor 512, and further the friction between the sensor stator 513 and the corresponding sensor rotor 511 and the friction between the bearing rotor 512 and the corresponding radial bearing stator 514 are reduced.
The radial fixing bracket 515 is used for clamping and fixing the sensor stator 513 and the radial bearing stator 514. The radial fixing supports 515 corresponding to the two radial magnetic suspension bearing assemblies 51 are respectively abutted to the upper radial bearing fixing boss 1011 and the lower radial bearing fixing boss 1012, and the radial fixing supports 515 and the corresponding upper radial bearing fixing boss 1011 and the lower radial bearing fixing boss 1012 are fixedly connected through connecting pieces.
Further, the radial fixing bracket 515 includes a radial magnetic bearing bracket 5151, a radial sensor bracket 5152 and an auxiliary bearing bracket 5153 stacked in sequence, the radial magnetic bearing bracket 5151 and the radial sensor bracket 5152 enclose a first fixing cavity 5154 for receiving and fixing the radial bearing stator 514, and the radial sensor bracket 5152 and the auxiliary bearing bracket 5153 enclose a second fixing cavity 5155 for receiving and fixing the sensor stator 513. The radial magnetic bearing bracket 5151, the radial sensor bracket 5152 and the auxiliary bearing bracket 5153 are fixed by a connecting member, such as a pin, and the connection between the radial fixing bracket 515 and the upper radial bearing fixing boss 1011 or the lower radial bearing fixing boss 1012 is also fixed by a connecting member, such as a pin, so as to achieve the fastening and fixing of the radial magnetic suspension bearing assembly 51 and the turbine housing 10.
Each of the auxiliary bearing brackets 5153 is provided with an auxiliary bearing 5156, and the rotating shaft 30 passes through the auxiliary bearing 5156. When the magnetic suspension bearing assembly 50 cannot provide the bearing force required by the rotating shaft 30, the auxiliary bearing 5156 supports and protects the magnetic suspension bearing assembly 50 and the turbine assembly 40 from being damaged.
In this embodiment, the axial magnetic suspension bearing assembly 52 is sandwiched between the two radial magnetic suspension bearing assemblies 51, and is used for providing an axial acting force to the rotating shaft 30, so that the rotating shaft 30 is balanced in the axial direction, and the interaction force between the rotating shaft 30 and the auxiliary bearing 5156 is reduced. The inner wall of the receiving cavity 101 protrudes to form an axial fixing boss 1013 sandwiched between the upper radial bearing fixing boss 1011 and the lower radial bearing fixing boss 1012, and the axial magnetic suspension bearing assembly 52 is fixed on the axial fixing boss 1013, so as to balance the overall stress of the rotating shaft 30 as much as possible.
Further, the axial magnetic suspension bearing assembly 52 includes two axial bearing stators 521 disposed opposite to each other at intervals, and an axial bearing bracket 522 for fixing the two axial bearing stators 521. The rotating shaft 30 includes a main shaft 31 formed integrally and a thrust disk 32 fixed on the main shaft 31, and the thrust disk 32 is sandwiched between the two axial bearing stators 521 and keeps balance under the action of the two axial bearing stators 521. The axial bearing bracket 522 of the axial magnetic suspension bearing assembly 52 abuts against the axial fixing boss 1013, and the axial bearing bracket 522 is fixedly connected with the axial fixing boss 1013 through a connecting member.
Furthermore, the radial fixing bracket 522 includes an annular cylinder 5221 and a clamping plate 5222 fixed on the cylinder 5221, two fixing rings 5223 are disposed on the inner wall of the cylinder 5221 at intervals and oppositely, and each axial bearing stator 521 is accommodated in one fixing ring 5223. The thrust disk 32 is sandwiched between the two fixing rings 5223. The catch plate 5222 abuts against the axial fixing boss 1013 and is fixedly connected to the turbine housing 10 by a connecting member such as a pin.
In this embodiment, the main shaft 31 is a hollow shaft, which greatly reduces the axial heat conductivity coefficient, effectively reduces the heat transfer from the normal temperature section to the cold end, and reduces the loss of cold energy.
In this embodiment, the generator assembly 60 includes a generator rotor 61 and a generator stator 62 sleeved on the generator rotor 61. The generator rotor 61 is sleeved on the rotating shaft 30 and is in interference fit with the rotating shaft 30, and the generator stator 62 is accommodated in the accommodating cavity 101 and is fixed with the turbine housing 10. The generator assembly 60 is sandwiched between the two radial magnetic bearing assemblies 51. In operation, the generator assembly 60 generates an electromagnetic braking torque to balance the torque of the main shaft 31, thereby converting shaft work into electrical energy and carrying away power generated by the turboexpander 100.
The turboexpander 100 also includes insulation 70. The thermal insulation material 70 is filled in an end of the volute 20 near the turbine housing 10 for insulating heat transfer between the turbine housing 10 and the volute 20. Specifically, the shaft 30 passes through the thermal insulation material 70, the turbine assembly 40 is located on a side of the thermal insulation material 70 close to the volute 20, and the magnetic suspension bearing assembly 50 and the generator assembly 60 are located on a side of the thermal insulation material 70 away from the turbine assembly 40.
A spiral protrusion structure (not shown) is disposed on a surface of the main shaft 31 near one end of the turbine assembly 40, and the protrusion structure is in sealing fit with the heat insulating material, so that the main shaft 31 and the heat insulating material 70 are fixed more firmly, and the main shaft 31 and the heat insulating material 70 are sealed better.
Furthermore, a first sealing gas flow passage 71 is provided in the heat insulating material 70, and a second sealing gas flow passage 102 communicating with the first sealing gas flow passage 71 is provided in the casing 10, so as to prevent the process gas from leaking into the turbine casing 10 from the volute 20 and losing the cooling capacity. When the turboexpander 100 works, the sealing process gas is introduced into the first sealing gas channel 71 and the 2 nd sealing gas channel 102, so that the cold leakage is reduced. And calculating the pressure and temperature of the sealed process gas according to the working medium parameters of the process gas.
In this embodiment, the turbine housing 10 is cylindrical, and the turbine housing 10 is provided with a spiral cooling water channel 103 for cooling heat generated by the magnetic suspension bearing assembly 50 and the generator assembly 60 during operation.
The nozzle assembly 22 includes a flow director 221 and a nozzle 222. An air inlet cavity 201 is arranged in the volute 20, the air inlet cavity 201 is communicated with the flow guide 221, and air is collected in the air inlet cavity 201 and enters the nozzle 222 under the flow guide effect of the flow guide 221, so that the flow speed and the direction of the air entering the nozzle 222 are kept relatively consistent.
The diffuser pipe 21 is in a circular funnel shape, and the diameter of the diffuser pipe is gradually increased from one end of the nozzle 222 to the other end, so that the pressure and the speed of the gas passing through the diffuser pipe 21 are increased and reduced. In the present embodiment, the diffuser pipe 21 is provided coaxially with the main shaft 31.
The turboexpander 100 further includes an upper end cover 80, and the upper end cover 80 is disposed at an end of the turbine housing 10 away from the volute 20. The upper end cover 80 and the volute casing 20 are respectively disposed at two ends of the turbine housing 10, and enclose the turbine housing 10 into a sealed space for accommodating the rotating shaft 30, the magnetic suspension bearing assembly 50 and the generator assembly 60.
The upper end cover 80 is also provided with a magnetic suspension bearing wiring port 81, a sensor wiring port 82 and a generator wiring port 83. The electric wires electrically connected with the radial bearing stator 514 and the axial bearing stator 521 pass through the magnetic suspension bearing wiring port 81 to be communicated with a power supply; the electric wire electrically connected to the sensor stator 513 is communicated with the power supply through the sensor wiring port 82; the electrical wires electrically connecting the generator assembly 60 pass through the generator connection port 83 to communicate with energy storage devices or electrical devices.
According to the turboexpander 100, the magnetic suspension bearing assembly 50 is used for replacing a traditional gas bearing, so that the processing and manufacturing difficulty of the bearing is reduced, the bearing capacity and rigidity of the bearing are increased, and the reliability of a rotor system is improved; in addition, the generator assembly 60 is adopted for braking, compared with the traditional fan wheel and booster wheel, the regulation response is quicker, the rotating speed is easier to control accurately, the braking mode omits the sealing of the braking end, reduces the braking gas loop, simplifies the whole structure, reduces the loss of process gas, realizes the recovery of braking power, meets the requirements of energy conservation and emission reduction, and has more obvious value particularly when the turbine power is larger. In addition, the main shaft 31 is a hollow shaft, so that the axial heat conductivity coefficient is greatly reduced, and the cold loss and the thermal deformation at a low temperature end are avoided.
The invention is not limited solely to that described in the specification and embodiments, and additional advantages and modifications will readily occur to those skilled in the art, so that the invention is not limited to the specific details, representative apparatus, and illustrative examples shown and described herein, without departing from the spirit and scope of the general concept as defined by the appended claims and their equivalents.
Claims (11)
1. A turboexpander characterized by: the magnetic suspension type turbine comprises a turbine shell, a volute fixedly connected to one end of the turbine shell, a rotating shaft accommodated in the turbine shell and the volute, a turbine assembly fixedly connected to one end of the rotating shaft and accommodated in the volute, and a magnetic suspension bearing assembly and a generator assembly which are sleeved on one end of the rotating shaft, far away from the turbine assembly, and fixedly connected to the turbine shell; the magnetic suspension bearing assembly comprises at least two radial magnetic suspension bearing assemblies and an axial magnetic suspension bearing assembly; the volute comprises a diffuser pipe and a nozzle assembly, the turbine assembly is contained at one end, close to the nozzle assembly, of the diffuser pipe, gas enters the turbine assembly through the nozzle assembly and expands to do work and cool, the rotating shaft is driven to rotate, and the generator assembly is driven by the rotating shaft to generate electric energy.
2. A turboexpander as claimed in claim 1 wherein: the number of the radial magnetic suspension bearing assemblies is two, and the two radial magnetic suspension bearing assemblies are respectively positioned at two ends of the rotating shaft; the turbine shell is internally provided with an accommodating cavity, an inner wall of the accommodating cavity is protruded to form an upper radial bearing fixing boss and a lower radial bearing fixing boss which are arranged at intervals, and the two radial magnetic suspension bearing assemblies are respectively fixed on the upper radial bearing fixing boss and the lower radial bearing fixing boss.
3. A turboexpander as claimed in claim 1 wherein: each radial magnetic suspension bearing assembly comprises a sensor rotor, a bearing rotor, a sensor stator, a radial bearing stator and a radial bearing bracket, wherein the sensor stator, the radial bearing stator and the radial bearing bracket are respectively corresponding to and sleeved on the sensor rotor and the bearing rotor; the sensor rotor and the bearing rotor are respectively sleeved on the rotating shaft and are in interference fit with the rotating shaft, and the sensor stator and the radial bearing stator are respectively arranged at intervals with the corresponding sensor rotor and the corresponding bearing rotor; the radial bearing support is used for clamping and fixing the sensor stator and the radial bearing stator; and the radial bearing supports corresponding to the two radial magnetic suspension bearing assemblies are respectively abutted against the upper radial bearing fixing boss and the lower radial bearing fixing boss, and the radial bearing supports and the corresponding upper radial bearing fixing boss and the corresponding lower radial bearing fixing boss are fixedly connected through connecting pieces.
4. A turboexpander as claimed in claim 3 wherein: the axial magnetic suspension bearing assembly is clamped between the two radial magnetic suspension bearing assemblies, and the inner wall of the containing cavity protrudes to form an axial bearing fixing boss clamped between the upper radial bearing fixing boss and the lower radial bearing fixing boss; the axial magnetic suspension bearing assembly is fixed on the axial bearing fixing boss.
5. A turboexpander as claimed in claim 4 wherein: the axial magnetic suspension bearing assembly comprises two axial bearing stators which are oppositely arranged at intervals and an axial bearing bracket used for fixing the axial bearing stators; the rotating shaft comprises an integrally formed main shaft and a thrust disc fixed on the main shaft, and the thrust disc is clamped between the two axial bearing stators; the axial magnetic suspension bearing assembly support is abutted against the axial bearing fixing boss, and the axial bearing support is fixedly connected with the axial bearing fixing boss through a connecting piece.
6. A turboexpander as claimed in claim 3 wherein: the generator assembly comprises a generator rotor and a generator stator sleeved on the generator rotor, and the generator stator is contained in the containing cavity and fixed with the turbine shell.
7. A turboexpander as claimed in claim 6 wherein: also comprises a heat insulating material; the thermal insulation material is filled at one end of the volute close to the turbine shell; the rotating shaft penetrates through the heat insulation material, the turbine assembly is located on one side, close to the volute, of the heat insulation material, and the magnetic suspension bearing assembly and the generator assembly are located on one side, away from the turbine assembly, of the heat insulation material.
8. A turboexpander as claimed in claim 7 wherein: the main shaft is close to the one end surface of turbine subassembly and is provided with heliciform protruding structure, protruding structure with the sealed cooperation of heat-insulating material.
9. A turboexpander as claimed in claim 7 wherein: a first sealed gas flow channel is arranged in the heat insulation material, and a second sealed gas flow channel communicated with the first sealed gas flow channel is arranged on the shell.
10. A turboexpander as claimed in claim 1 wherein: the turbine shell is cylindrical, and a spiral cooling water channel is arranged on the turbine shell.
11. A turboexpander as claimed in claim 5 wherein: the main shaft is arranged in a hollow mode.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911156201.XA CN110966051B (en) | 2019-11-22 | 2019-11-22 | Turbine expansion machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911156201.XA CN110966051B (en) | 2019-11-22 | 2019-11-22 | Turbine expansion machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110966051A true CN110966051A (en) | 2020-04-07 |
| CN110966051B CN110966051B (en) | 2022-04-26 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911156201.XA Active CN110966051B (en) | 2019-11-22 | 2019-11-22 | Turbine expansion machine |
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| Country | Link |
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| CN (1) | CN110966051B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114033504A (en) * | 2021-11-05 | 2022-02-11 | 重庆江增船舶重工有限公司 | Liquid working medium spray cooling system |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000120402A (en) * | 1998-10-15 | 2000-04-25 | Nippon Sanso Corp | Hybrid bearing type expansion turbine |
| CN103557036A (en) * | 2013-10-21 | 2014-02-05 | 陕西博尔能源科技有限公司 | Integrated turbine set based on permanent magnetic and magnetic suspension technologies |
| CN107476833A (en) * | 2017-06-14 | 2017-12-15 | 南京航空航天大学 | The self cooled magnetic suspension turbine expansion generator of zero leakage and System and method for |
| CN107503806A (en) * | 2017-08-25 | 2017-12-22 | 谢竞宁 | Turbine |
| CN110439634A (en) * | 2019-08-19 | 2019-11-12 | 哈尔滨电气股份有限公司 | One kind being used for direct connection natural gas radial-inflow turboexpaner generating equipment |
-
2019
- 2019-11-22 CN CN201911156201.XA patent/CN110966051B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000120402A (en) * | 1998-10-15 | 2000-04-25 | Nippon Sanso Corp | Hybrid bearing type expansion turbine |
| CN103557036A (en) * | 2013-10-21 | 2014-02-05 | 陕西博尔能源科技有限公司 | Integrated turbine set based on permanent magnetic and magnetic suspension technologies |
| CN107476833A (en) * | 2017-06-14 | 2017-12-15 | 南京航空航天大学 | The self cooled magnetic suspension turbine expansion generator of zero leakage and System and method for |
| CN107503806A (en) * | 2017-08-25 | 2017-12-22 | 谢竞宁 | Turbine |
| CN110439634A (en) * | 2019-08-19 | 2019-11-12 | 哈尔滨电气股份有限公司 | One kind being used for direct connection natural gas radial-inflow turboexpaner generating equipment |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114033504A (en) * | 2021-11-05 | 2022-02-11 | 重庆江增船舶重工有限公司 | Liquid working medium spray cooling system |
| CN114033504B (en) * | 2021-11-05 | 2024-05-03 | 重庆江增船舶重工有限公司 | Liquid working medium spray cooling system |
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| Publication number | Publication date |
|---|---|
| CN110966051B (en) | 2022-04-26 |
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