CN114483303A - High-speed permanent magnet motor applied to micro gas turbine - Google Patents
High-speed permanent magnet motor applied to micro gas turbine Download PDFInfo
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- CN114483303A CN114483303A CN202111648818.0A CN202111648818A CN114483303A CN 114483303 A CN114483303 A CN 114483303A CN 202111648818 A CN202111648818 A CN 202111648818A CN 114483303 A CN114483303 A CN 114483303A
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- 239000003921 oil Substances 0.000 claims abstract description 67
- 238000007667 floating Methods 0.000 claims abstract description 43
- 238000002347 injection Methods 0.000 claims abstract description 15
- 239000007924 injection Substances 0.000 claims abstract description 15
- 229910000976 Electrical steel Inorganic materials 0.000 claims abstract description 13
- 238000005461 lubrication Methods 0.000 claims abstract description 13
- 238000001816 cooling Methods 0.000 claims abstract description 12
- 238000004804 winding Methods 0.000 claims abstract description 10
- 229920000049 Carbon (fiber) Polymers 0.000 claims abstract description 8
- 239000004917 carbon fiber Substances 0.000 claims abstract description 8
- 238000005096 rolling process Methods 0.000 claims abstract description 6
- 229910000746 Structural steel Inorganic materials 0.000 claims abstract description 5
- KPLQYGBQNPPQGA-UHFFFAOYSA-N cobalt samarium Chemical compound [Co].[Sm] KPLQYGBQNPPQGA-UHFFFAOYSA-N 0.000 claims abstract description 5
- 229910000938 samarium–cobalt magnet Inorganic materials 0.000 claims abstract description 5
- 238000009423 ventilation Methods 0.000 claims abstract description 4
- 238000007789 sealing Methods 0.000 claims description 9
- 238000013016 damping Methods 0.000 claims description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 4
- 230000007704 transition Effects 0.000 claims description 2
- 239000000498 cooling water Substances 0.000 claims 2
- 230000036316 preload Effects 0.000 claims 1
- 230000001050 lubricating effect Effects 0.000 description 7
- 239000010687 lubricating oil Substances 0.000 description 7
- 230000009467 reduction Effects 0.000 description 6
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 5
- 239000000725 suspension Substances 0.000 description 5
- 239000004519 grease Substances 0.000 description 4
- 238000010248 power generation Methods 0.000 description 4
- 230000007547 defect Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 239000000446 fuel Substances 0.000 description 3
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 3
- 229920001967 Metal rubber Polymers 0.000 description 2
- 230000009471 action Effects 0.000 description 2
- 239000000919 ceramic Substances 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 238000005008 domestic process Methods 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000010030 laminating Methods 0.000 description 1
- 238000011031 large-scale manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000013017 mechanical damping Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000001172 regenerating effect Effects 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
- F02C3/04—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/06—Arrangements of bearings; Lubricating
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Motor Or Generator Frames (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
The invention relates to a power machine of a small thermal power generator, in particular to a high-speed permanent magnet motor applied to a micro gas turbine. A high-speed permanent magnet motor applied to a micro gas turbine is mounted in a horizontal flange mode, a stator is of a pear-shaped groove winding structure, and a ventilation channel is reserved at a groove opening; the stator core adopts a high-frequency low-loss non-oriented silicon steel sheet; the rotor is made of magnetic conduction structural steel without silicon steel sheets, the permanent magnet is made of high-temperature-resistant samarium cobalt, and the rotor is solidified by adopting a surface-mounted mode and externally winding carbon fibers; the bearing adopts an ultra-precise high-speed rolling bearing: namely, two angular contact ball bearings at the fixed end and the floating end are installed in a face-to-face mode, and the floating end is axially pre-tightened through a disc spring; and an embedded oil injection lubrication structure is adopted for bearing lubrication and cooling.
Description
Technical Field
The invention relates to a power machine of a small thermal power generator, in particular to a high-speed permanent magnet motor applied to a micro gas turbine.
Background
The micro gas turbine is a newly developed small thermal power generator power machine, the single machine power range of the micro gas turbine is 100-500 kW, and the micro gas turbine is basically technically characterized in that a radial-flow impeller machine (a centripetal turbine and a centrifugal compressor) and a regenerative cycle are adopted, a rotary thermal engine using fuel and air as media is adopted, and an impeller is pushed by high-temperature and high-pressure gas to do work to drive a generator to generate electric energy. The micro gas turbine has a series of advanced technical characteristics of multi-station integrated capacity expansion, multi-fuel, low noise, low emission, low vibration, low maintenance rate and the like, can be used for a standby power station, cogeneration, grid-connected power generation, peak load power generation and the like besides distributed power generation, and is an optimal mode for providing clean, reliable, high-quality, multipurpose, small-sized distributed power generation and cogeneration.
In the micro gas turbine system, three key components of the gas turbine, the air inlet compressor and the permanent magnet generator are coaxially connected and have the same rotating speed. Because the fuel and the air entering the micro gas turbine system are accurately controllable, when the micro gas turbine is successfully started and reaches a stable operation state, the output electric power is stable, and the impact on a power grid can not be caused during grid connection operation. Under the normal operation condition, the generator adopted by the micro gas turbine generator set is mainly a high-rotation-speed permanent magnet generator (the rotation speed range is 10000-60000 r/min), and outputs high-frequency alternating current.
The high-speed permanent magnet motor has the advantages of small volume, direct connection with a load and high efficiency, and has wide application space in the field of micro gas turbines. At present, foreign high-speed motors account for 20% of the motor market, are mainly applied to the fields of high-speed compressors, high-speed blowers, high-speed water pumps and the like, and are in a rapidly increasing trend. The main domestic process is mainly focused on a prototype stage and a theoretical stage, only a few enterprises are still developing and trying to produce, and large-scale production and serialized products are not formed.
1) The technical scheme of the prior art I is as follows: the totally-enclosed water-cooling high-speed permanent magnet motor is supported by a deep groove ball bearing or a roller bearing, and grease lubrication and non-contact rotating labyrinth sealing are adopted to prevent grease from escaping outwards and impurities from entering the inside of the bearing. As shown in fig. 8.
The first prior art has the following defects: the deep groove ball bearing and the roller bearing have low limit rotating speed and can be used in the occasions with lower rotating speed and heavy load, the rotating DN value (the product of the bearing inner diameter D and the rotating speed n) of the rolling body generally does not exceed 50 ten thousand, and a high-speed motor usually requires the DN number to be more than 100 ten thousand, so the conventional bearing support structure can not be used at high speed generally; the lubricating grease filled in the bearing is likely to splash and escape from the labyrinth at a high rotating speed, poor lubrication of the bearing is caused, and the temperature rise of the bearing is easy to exceed the standard when the rolling element stirs the lubricating grease at a high speed.
2) Prior art relating to the invention
The second technical scheme in the prior art: the stator iron core and the rotor iron core are formed by laminating silicon steel sheets, so that eddy current loss is reduced, the armature winding is embedded in the stator iron core, the permanent magnet is installed in the slot of the rotor silicon steel sheet, and the rotor structure is as shown in figure 9.
The second prior art has the following defects: the permanent magnet of this scheme structure can provide great per-pole magnetic flux, but when rotor surface rotational speed linear velocity exceeded 100m/s, the silicon steel sheet was cracked certainly from separating magnetic bridge position, and the rotor structure can't satisfy high rotational speed requirement, the power and the volume of the motor of the mechanical strength restriction of rotor.
3) Prior art three related to the invention
The third technical scheme in the prior art: the high-speed motor rotor has high rotation speed which can reach tens of thousands of revolutions per minute or even hundreds of thousands of revolutions per minute, so that the motor rotor always works above the critical rotation speed or passes through the critical rotation speed back and forth, vibration reduction measures are necessarily adopted when the critical rotation speed is crossed, otherwise the motor vibration is high to cause the friction between the stator and the rotor, and the high-speed motor supported by the magnetic suspension bearing can realize the crossing of the critical rotation speed because of the accurate real-time position adjustment of the magnetic suspension technology and the lower support rigidity, as shown in figure 10.
The third prior art has the following defects: the magnetic suspension bearing has the advantages of high manufacturing cost, long debugging period and large installation size, and a set of control system needs to be matched simultaneously and independently, so that the manufacturing cost is increased.
Disclosure of Invention
The invention aims to solve the following technical problems:
1) the common bearing can not reliably run at a high speed, and a high-rotating-speed (namely a high DN value) bearing is required to be adopted, and a matched lubricating system is designed;
2) the high-speed permanent magnet motor is mainly characterized in that the rotor has high rotating speed, and the conventional laminated rotor is difficult to bear huge centrifugal force at high rotating speed, so that the condition of high rotating speed can be met only by adopting different structures;
3) the high-speed motor rotor system has very high possibility of approaching and crossing critical rotating speed, and the critical rotating speed of the rotor system must be accurately predicted to avoid bending resonance and a vibration reduction design is added;
4) the sintered permanent magnet material cannot withstand the tensile stress generated by the high-speed rotation of the rotor, so that protection measures must be taken.
The invention is realized by adopting the following technical scheme: a high-speed permanent magnet motor applied to a micro gas turbine is mounted in a horizontal flange mode, a stator is of a pear-shaped groove winding structure, and a ventilation channel is reserved at a groove opening; the stator iron core adopts a high-frequency low-loss non-oriented silicon steel sheet; the rotor is made of magnetic conduction structural steel without silicon steel sheets, the permanent magnet is made of high-temperature-resistant samarium cobalt, and the rotor is solidified by adopting a surface-mounted mode and externally winding carbon fibers; the bearing adopts an ultra-precise high-speed rolling bearing: namely, two angular contact ball bearings at the fixed end and the floating end are installed in a face-to-face mode, and the floating end is axially pre-tightened through a disc spring; and an embedded oil injection lubrication structure is adopted for bearing lubrication and cooling.
The invention adopts the angular contact ball bearing, which meets the requirement of high rotating speed; the embedded oil injection lubricating structure can effectively realize the lubrication and cooling of the bearing; the rotor is made of magnetic conduction structural steel without silicon steel sheets, and can bear huge centrifugal force caused by high-speed rotation; the permanent magnet is high temperature resistant samarium cobalt, and adopts the table to paste the form and add outside winding carbon fiber and solidify, can bear the tensile stress that the high-speed rotation of rotor produced.
Furthermore, elastic supports and squeeze film dampers are assembled at two ends of the rotating shaft and are used for damping vibration, the elastic supports and the squeeze film dampers are of an integrated structure, the elastic supports are installed in central holes of the fixed end cover and the floating end cover, the squeeze film dampers are positioned on the circumferential outer ring of the bearing and serve as bearing chambers of the bearing, and the squeeze film dampers at the floating end are in transition fit with the outer ring of the bearing; the disc spring of the floating end is arranged on one side of the floating end bearing, which faces the elastic support, and tightly props against the floating end bearing; an O-shaped ring is arranged on the surface of the outer circle of the floating end bearing; the fixed end is also provided with a bearing cover on the inner side of the end cover, the bearing cover is arranged in the engine base, and a central hole of the bearing cover is sleeved on the outer side of the squeeze film damper of the fixed end.
By adopting the damping structure integrating the elastic support and the squeeze film damper and combining the design of the disc spring, the vibration caused by high-speed rotation can be effectively reduced. In order to prevent the bearing from excessive displacement and vibration in the bearing chamber, the O-shaped ring is sleeved on the outer ring of the floating end bearing, the O-shaped ring can be made of metal rubber, and certain elastic coefficient is ensured, so that the rotor can displace in a controllable range under the action of unilateral magnetic tension and gravity.
Furthermore, a grate tooth sealing structure is arranged between the rotating shaft and the bearing cover as well as between the rotating shaft and the floating end cover, so that the conditions of overhigh rotating speed and lack of heat dissipation conditions of the high-speed permanent magnet motor are met.
Because motor stiff end and floating end structure are different, consequently designed the initiative oil spout formula lubricating system that the structure is different respectively at both ends: the fixed end cover and the bearing cover enclose a cavity; a first oil return cavity for connecting the cavity and the grate tooth sealing structure is formed in the bearing cover; a first oil filling hole is formed in the upper portion of the bearing cover on the base, an annular groove is formed in the position, corresponding to the first oil filling hole, of the bearing cover, an oil way communicated with the position of a bearing ball is formed in the bottom of the annular groove, and an oil nozzle is arranged at an oil way outlet; the cavity and the first oil filling hole are communicated through a pump.
A second oil hole is arranged on the squeeze film damper at the floating end, and an oil film cavity communicated with the second oil hole, the floating end bearing ball part and the oil film cavity is formed in the squeeze film damper; and the elastic support at the floating end and the squeeze film damper are provided with a cavity, and the grate tooth sealing structure at the floating end is communicated with the cavity through a second oil return cavity.
According to the active oil injection type lubricating system, the oil way is arranged in the circumferential direction in the form of the annular groove and the oil injection hole and is embedded in the bearing chamber and the engine base, the oil of the squeeze film damper and the bearing lubricating oil are input by the same oil pump, the oil way is also embedded in the bearing chamber, and a nozzle and an oil pipe are not additionally arranged.
The invention has the technical characteristics that:
1) the motor vibration reduction design: the invention adopts the scheme of externally adding damping, namely adding an integrated elastic support and an extrusion oil film damper to reduce the vibration amplitude of the rotor. The damper vibration reduction technology has good vibration reduction performance, and is simple in structure, high in reliability and low in cost.
2) Bearing arrangement, lubrication and sealing structure: the rotor structure comprises a single bearing configuration scheme with disc spring pre-tightening, tolerance design of a floating end bearing, oil injection oil way design and a carbon fiber protection integrated rotor structure.
Drawings
FIG. 1 is a schematic diagram of the motor structure with elastic support and squeeze film damper of the present invention.
FIG. 2 is a schematic view of a bearing with an o-ring.
FIG. 3 shows a schematic oil injection scheme (floating end) for squeeze film dampers.
Fig. 4 shows a schematic view of the assembly of an angular contact bearing with spring pretensioning.
FIG. 5 schematic view of an active oil-jet lubrication system (fixed end).
FIG. 6 shows a centrifugal + grate seal.
FIG. 7 is a schematic diagram of a water cooling structure of a spiral groove.
Fig. 8 is a schematic view of a supporting and sealing structure of a permanent magnet motor in common use at present.
Fig. 9 is a schematic view of a rotor structure of a second prior art.
FIG. 10 is a schematic diagram of a high speed motor supported by magnetic bearings.
1-rotating shaft, 2-stator, 3-floating end cover, 4-fixed end cover, 5-bearing cover, 6-ceramic angular contact bearing, 7-elastic support, 8-squeeze film damper, 9-permanent magnet, 10-carbon fiber, 11-disc spring, 12-first oil injection hole, 13-annular groove, 14-oil nozzle, 15-first oil return cavity, 16-centrifugal seal, 17-labyrinth seal structure, 18-second oil injection hole, 19-oil film cavity, 20-O ring, 21-second oil return cavity, 22-rotor, 23-roller bearing, 24-labyrinth oil seal, 25-rotor core, 26-radial bearing, 27-thrust bearing and 28-water cooling spiral groove structure.
Detailed Description
The high-speed motor is installed by a horizontal flange, the stator is basically similar to the stator structure of an alternating current motor, a pear-shaped slot winding structure is adopted, a certain ventilation channel is reserved at the position of a slot opening, and a stator iron core is made of a high-frequency low-loss non-oriented silicon steel sheet with the thickness of 0.2 mm; the rotor is made of magnetic conduction structural steel without silicon steel sheets, the permanent magnet is made of high-temperature-resistant samarium cobalt, and the rotor is solidified by adopting a surface-mounted mode and externally winding carbon fibers; the bearing adopts an ultra-precise high-speed rolling bearing: namely, two angular contact ball bearings are installed in a back-to-back mode, the floating end is pre-tightened by an axial disc spring, and an embedded oil injection lubrication structure is adopted for bearing lubrication and cooling; the whole machine adopts a stator spiral groove water-cooling structure (shown in figure 7).
Specific embodiment (structure is shown in figure 1)
1) The invention adopts the angular contact ceramic bearing support pre-tightened by the disc spring, and the bearing is realized by a pair of (spring) pre-tightened angular contact ball bearings: one end of the shaft is a fixed bearing and the other end is a floating bearing (the minimum clearance between the floating end bearing and the bearing chamber is 20μm). In order to prevent the bearing from excessive displacement and vibration in the bearing chamber, the O-shaped ring is sleeved on the outer ring of the floating end bearing, the O-shaped ring can be made of metal rubber, and certain elastic coefficient is ensured, so that the rotor can displace in a controllable range under the action of unilateral magnetic tension and gravity. As shown in fig. 2.
At the floating bearing end, the pre-tightening spring needs to be capable of maintaining constant pre-tightening force under all working conditions. In all operating modes (maximum rotating speed + maximum radial load), the requirement of disc spring pretightening force is as follows: 350N. The price of the angular contact bearing is far lower than that of a magnetic suspension bearing, the angular contact bearing is used as a standardized product, the later maintenance and replacement are very convenient, the magnetic suspension bearing generally needs to be designed one to one according to a mechanical structure, once a fault occurs, the structure and a control system possibly need to be designed or set and adjusted at the same time, the special property is strong, and the operability is low. The design structure is shown in fig. 4.
2) Initiative oil spout formula lubricating system: the oil circuit is arranged in the circumferential direction in the form of an annular groove and an oil filling hole and is embedded in the bearing chamber and the machine base, the squeeze film damper oil and the bearing lubricating oil are input by the same oil pump, and the oil circuit is also embedded in the bearing chamber without additionally adding a nozzle and an oil pipe. As shown in fig. 3 and 5, the oil injection structure of the fixed end and the floating end is respectively.
With reference to fig. 1, 3 and 4, the floating end labyrinth seal structure includes a plurality of labyrinth teeth arranged inside the center hole of the floating end cover and an annular chute formed on the rotating shaft, the chute being used as a centrifugal oil slinger; two sides of the grate teeth form annular grooves which correspond to the inclined grooves one by one; the second oil return cavity is communicated with the annular groove and the cavity.
With reference to fig. 5 and 6, the labyrinth seal structure at the fixed end comprises a plurality of labyrinth teeth arranged inside the central hole of the bearing cap and an annular chute opening on the rotating shaft, the chute being a centrifugal oil slinger; two sides of the grate teeth form annular grooves which correspond to the inclined grooves one by one; the first oil return cavity is communicated with the annular groove and the cavity.
3) Centrifugal + grate seal (as shown in fig. 6): because of the over-high rotating speed and lack of heat dissipation conditions, a grate tooth type sealing structure with an oil return hole is adopted instead of a contact type mechanical seal, and a rotating shaft is provided with a centrifugal oil slinger. The motor outer part of the lubricating oil injection pressurization and recovery cooling oil path is provided by an oil pump and a cooling tower, the viscosity grade of the lubricating oil is VG32, the lubricating oil is injected into the middle of the bearing inner ring and the retainer at the speed of 10m/s so as to pass through an air curtain caused by high-speed rotation, the lubricating oil amount is 0.3-0.8L/min, and the minimum lubricating oil amount is determined through a motor test.
4) The scheme of the integral rotor with the carbon fiber sheath is provided with the elastic support and the squeeze film damper for vibration reduction, the vibration of the motor can be greatly reduced through the mechanical damping characteristic and the matching design scheme of the squeeze film, the motor can successfully operate above the critical rotating speed, the motor can successfully work in a high rotating speed area and can stably pass through between the critical rotating speeds, a special control system is not required, and manual intervention is not required in the operation process.
Claims (10)
1. A high-speed permanent magnet motor applied to a micro gas turbine is mounted in a horizontal flange mode, a stator is of a pear-shaped groove winding structure, and a ventilation channel is reserved at a groove opening; the stator core is made of high-frequency low-loss non-oriented silicon steel sheets; the rotor is made of magnetic conduction structural steel without silicon steel sheets, the permanent magnet is made of high-temperature-resistant samarium cobalt, and the rotor is solidified by adopting a surface-mounted mode and externally winding carbon fibers; the bearing adopts an ultra-precise high-speed rolling bearing: namely, two angular contact ball bearings at the fixed end and the floating end are installed in a face-to-face mode, and the floating end is axially pre-tightened through a disc spring; and an embedded oil injection lubrication structure is adopted for bearing lubrication and cooling.
2. The high-speed permanent magnet motor applied to the micro gas turbine as claimed in claim 1, wherein the two ends of the rotating shaft are respectively provided with an elastic support and a squeeze film damper for damping vibration, the elastic support and the squeeze film damper are integrated into a whole structure, the elastic support is installed in the central holes of the fixed end cover and the floating end cover, the squeeze film damper is located on the circumferential outer ring of the bearing and serves as a bearing chamber of the bearing, and the squeeze film damper at the floating end is in transition fit with the outer ring of the bearing; the disc spring of the floating end is arranged on one side of the floating end bearing, which faces the elastic support, and tightly props against the floating end bearing; an O-shaped ring is arranged on the surface of the outer circle of the floating end bearing; the fixed end is also provided with a bearing cover on the inner side of the end cover, the bearing cover is arranged in the engine base, and a central hole of the bearing cover is sleeved on the outer side of the squeeze film damper of the fixed end.
3. A high speed permanent magnet motor for a micro gas turbine as claimed in claim 2, wherein a labyrinth seal structure is provided between the rotating shaft and the bearing cap and between the rotating shaft and the floating end cap.
4. A high speed permanent magnet motor for a micro gas turbine as claimed in claim 3, wherein the fixed end cap and the bearing cap define a cavity; a first oil return cavity for connecting the cavity and the grate tooth sealing structure is formed in the bearing cover; a first oil injection hole is formed above the bearing cover on the engine base, an annular groove is formed in the position, corresponding to the first oil injection hole, on the bearing cover, an oil way communicated with the position of a bearing ball is formed in the bottom of the annular groove, and an oil nozzle is arranged at an outlet of the oil way; the cavity and the first oil filling hole are communicated through a pump.
5. The high-speed permanent magnet motor applied to the micro gas turbine as claimed in claim 3, wherein the squeeze film damper at the floating end is provided with a second oil hole, and an oil film cavity communicated with the second oil hole and the ball part of the bearing at the floating end is formed in the squeeze film damper; and the elastic support at the floating end and the squeeze film damper are provided with a cavity, and the grate tooth sealing structure at the floating end is communicated with the cavity through a second oil return cavity.
6. A high-speed permanent magnet motor applied to a micro gas turbine according to claim 4, wherein the labyrinth seal structure comprises a plurality of labyrinth teeth arranged inside the central hole of the bearing cover and an annular inclined groove formed on the rotating shaft, and the inclined groove is used as a centrifugal oil slinger; two sides of the grate teeth form annular grooves which correspond to the inclined grooves one by one; the first oil return cavity is communicated with the annular groove and the cavity.
7. A high-speed permanent magnet motor applied to a micro gas turbine as claimed in claim 5, wherein the labyrinth seal structure comprises a plurality of castellations arranged inside the center hole of the floating end cover and an annular chute arranged on the rotating shaft and used as a centrifugal oil slinger; two sides of the grate teeth form annular grooves which correspond to the inclined grooves one by one; the second oil return cavity is communicated with the annular groove and the cavity.
8. A high-speed permanent magnet motor for a micro gas turbine according to any one of claims 1 to 7, wherein the stator core is made of a high-frequency low-loss non-oriented silicon steel sheet with a thickness of 0.2 mm.
9. The high-speed permanent magnet motor applied to the micro gas turbine as claimed in any one of claims 1 to 7, wherein the disk spring pre-load requirement is as follows: 350N; the minimum value of the clearance between the floating end bearing and the bearing chamber is 20 mu m.
10. The high-speed permanent magnet motor applied to the micro gas turbine as claimed in any one of claims 1 to 7, wherein a cooling water jacket is sleeved outside the stator, and the cooling water jacket adopts a spiral groove water cooling structure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111648818.0A CN114483303B (en) | 2021-12-30 | 2021-12-30 | High-speed permanent magnet motor applied to micro gas turbine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111648818.0A CN114483303B (en) | 2021-12-30 | 2021-12-30 | High-speed permanent magnet motor applied to micro gas turbine |
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| CN114483303A true CN114483303A (en) | 2022-05-13 |
| CN114483303B CN114483303B (en) | 2023-04-07 |
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08334117A (en) * | 1995-05-12 | 1996-12-17 | Capstone Turbine Corp | Composite shaft |
| CN101413440A (en) * | 2008-11-26 | 2009-04-22 | 沈阳黎明航空发动机(集团)有限责任公司 | Minitype gas turbine electric generating set |
| CN102506006A (en) * | 2011-11-21 | 2012-06-20 | 哈尔滨电机厂有限责任公司 | Shaft system structure for marine tidal current generator |
| CN109026397A (en) * | 2018-10-21 | 2018-12-18 | 至玥腾风科技投资集团有限公司 | Bearing lubrication system and miniature gas turbine generating set |
| CN208890609U (en) * | 2018-03-09 | 2019-05-21 | 沈阳工业大学 | Rotor uses the high-speed permanent magnetic generator of hybrid permanent magnet annular structure |
| CN110645097A (en) * | 2019-08-23 | 2020-01-03 | 湖南航翔燃气轮机有限公司 | Gas turbine generating set rotor subassembly and gas turbine generating set |
| CN110966096A (en) * | 2019-12-04 | 2020-04-07 | 扬州大学 | High-temperature magnetic suspension bearing cooling system for gas turbine |
| CN112242778A (en) * | 2020-09-25 | 2021-01-19 | 中车永济电机有限公司 | High-power high-speed magnetic suspension permanent magnet motor |
-
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- 2021-12-30 CN CN202111648818.0A patent/CN114483303B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08334117A (en) * | 1995-05-12 | 1996-12-17 | Capstone Turbine Corp | Composite shaft |
| CN101413440A (en) * | 2008-11-26 | 2009-04-22 | 沈阳黎明航空发动机(集团)有限责任公司 | Minitype gas turbine electric generating set |
| CN102506006A (en) * | 2011-11-21 | 2012-06-20 | 哈尔滨电机厂有限责任公司 | Shaft system structure for marine tidal current generator |
| CN208890609U (en) * | 2018-03-09 | 2019-05-21 | 沈阳工业大学 | Rotor uses the high-speed permanent magnetic generator of hybrid permanent magnet annular structure |
| CN109026397A (en) * | 2018-10-21 | 2018-12-18 | 至玥腾风科技投资集团有限公司 | Bearing lubrication system and miniature gas turbine generating set |
| CN110645097A (en) * | 2019-08-23 | 2020-01-03 | 湖南航翔燃气轮机有限公司 | Gas turbine generating set rotor subassembly and gas turbine generating set |
| CN110966096A (en) * | 2019-12-04 | 2020-04-07 | 扬州大学 | High-temperature magnetic suspension bearing cooling system for gas turbine |
| CN112242778A (en) * | 2020-09-25 | 2021-01-19 | 中车永济电机有限公司 | High-power high-speed magnetic suspension permanent magnet motor |
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| CN114483303B (en) | 2023-04-07 |
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