WO2016184404A1 - Soufflante à très haute vitesse - Google Patents

Soufflante à très haute vitesse Download PDF

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Publication number
WO2016184404A1
WO2016184404A1 PCT/CN2016/082676 CN2016082676W WO2016184404A1 WO 2016184404 A1 WO2016184404 A1 WO 2016184404A1 CN 2016082676 W CN2016082676 W CN 2016082676W WO 2016184404 A1 WO2016184404 A1 WO 2016184404A1
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WO
WIPO (PCT)
Prior art keywords
groove pattern
foil
bearing
dynamic pressure
pressure gas
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2016/082676
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English (en)
Chinese (zh)
Inventor
罗立峰
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Individual
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Individual
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Publication date
Priority claimed from PCT/CN2015/079233 external-priority patent/WO2016183787A1/fr
Priority claimed from PCT/CN2015/079234 external-priority patent/WO2016183788A1/fr
Application filed by Individual filed Critical Individual
Publication of WO2016184404A1 publication Critical patent/WO2016184404A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/18—Structural association of electric generators with mechanical driving motors, e.g. with turbines
    • H02K7/1807—Rotary generators
    • H02K7/1823—Rotary generators structurally associated with turbines or similar engines
    • H02K7/183—Rotary generators structurally associated with turbines or similar engines wherein the turbine is a wind turbine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
    • F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/042—Sliding-contact bearings for exclusively rotary movement for axial load only with flexible leaves to create hydrodynamic wedge, e.g. axial foil bearings
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
    • F02B41/02—Engines with prolonged expansion
    • F02B41/10—Engines with prolonged expansion in exhaust turbines
    • 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
    • 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
    • F02C7/12—Cooling of plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/52—Casings; Connections of working fluid for axial pumps
    • F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/08—Sliding-contact bearings for exclusively rotary movement for axial load only for supporting the end face of a shaft or other member, e.g. footstep bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
    • F16C17/107—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one surface for radial load and at least one surface for axial load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/26—Systems consisting of a plurality of sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1005—Construction relative to lubrication with gas, e.g. air, as lubricant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/002—Cooling of bearings of fluid bearings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/161—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields radially supporting the rotary shaft at both ends of the rotor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/163—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields radially supporting the rotary shaft at only one end of the rotor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/18—Structural association of electric generators with mechanical driving motors, e.g. with turbines
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/02—Arrangements for cooling or ventilating by ambient air flowing through the machine
    • H02K9/04—Arrangements for cooling or ventilating by ambient air flowing through the machine having means for generating a flow of cooling medium
    • H02K9/06—Arrangements for cooling or ventilating by ambient air flowing through the machine having means for generating a flow of cooling medium with fans or impellers driven by the machine shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/028—Sliding-contact bearings for exclusively rotary movement for radial load only with fixed wedges to generate hydrodynamic pressure, e.g. multi-lobe bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines

Definitions

  • the invention relates to an ultra-high speed blower and belongs to the technical field of high precision machinery.
  • the air blower is mainly used in a part of an office automation equipment that requires a large amount of air, and the hot air generated inside the device is discharged outward by the wind generated by rotating the impeller, and the device is internally cooled and cooled.
  • the traditional blower usually uses the speed increasing system to drive the compressor impeller to rotate after the speed increase of the ordinary power frequency motor.
  • the main defects are as follows: 1 The speed increasing system is very complicated, the weight is large, the floor space is large, and the cost is expensive; Specially equipped oil system, and easy to leak oil problem, limited application range; 3 gear transmission noise is large, there is a certain mechanical loss, and ordinary power frequency motor has low power density, large volume and weight, high noise; Both the speed system and the ordinary power frequency motor need to apply the bearing.
  • Chinese Patent Publication No. CN102200136B discloses an air suspension gas supply adjustable high speed motor direct drive blower, which comprises a compressor impeller, a permanent magnet synchronous motor rotor, a motor stator, and a front Radial air bearing, rear radial air bearing, axial thrust air bearing, volute and motor housing; one end of the permanent magnet synchronous motor rotor is connected to the compressor impeller, and the motor stator drives the permanent magnet synchronous motor rotor to rotate, the front diameter
  • the air bearing, the rear radial air bearing and the axial thrust air bearing are suspended to support the permanent magnet synchronous motor rotor, and the scroll is disposed at the periphery of the compressor impeller, and the motor housing is located at the motor stator, the front radial air bearing, and the rear radial Air bearing, axial thrust air bearing and the periphery of the permanent magnet synchronous motor rotor.
  • the patented technology directly drives the compressor impeller through the permanent magnet synchronous motor rotor of the high-speed motor
  • the utility model has the advantages of high efficiency, low loss, environmental protection, wide applicable range, and the like, but the patent technology still has the following problems: 1.
  • the rotational speed is still limited. At present, it can only achieve a speed of up to 100,000 rpm; 2. It can not be operated for a long time: the heat generated by high-speed operation cannot be effectively exported, so that the continuous working time cannot be very long; 3.
  • the stability of high-speed operation is not good, so that the actual operating efficiency is up to Not ideal goals; 4, the structure is still relatively complex, large size, can not meet the requirements of today's miniaturization development.
  • an object of the present invention is to provide an ultrahigh speed blower which has high operation efficiency, high speed operation stability, and can work for a long time.
  • An ultra-high-speed air blower comprising an impeller and a motor, the motor comprising a rotor, a stator, a rotating shaft, an end cover and a casing; and further comprising: a rotary connecting member and a slot type dynamic pressure gas radial bearing, and
  • the housing is an annular cylindrical structure formed by two inner and outer cylinders, the rotary connecting member is a cylindrical structure having a cavity, and the rotating connecting member is sleeved on a rotating shaft close to the impeller Up, and respectively coupled with the impeller and the end of the rotating shaft, the side of the rotating connecting member is located in a cavity formed by the outer cylinder and the inner cylinder of the casing; the slot type dynamic pressure gas radial bearing and The rotating shaft is located in the inner cylinder cavity of the casing, and the slot type dynamic pressure gas radial bearing is sleeved on the rotating shaft; the stator is fixed on the outer cylinder outer wall of the casing, and the rotor is fixed on the rotating connecting
  • a plurality of air guide vanes are provided at a side of the rotary joint located above the air flow passage formed at the end of the rotary shaft and the slotted dynamic gas radial bearing.
  • a plurality of air inlet holes and a plurality of heat dissipation vent holes are formed on the outer circumference side of the outer casing of the casing.
  • the impeller is fixedly connected to the rotating connecting member and the rotating shaft by a locking bolt.
  • the rotating shaft and the locking bolt are both provided with a cavity to reduce the weight of the blower.
  • the ultra high speed blower further comprises an impeller casing, the impeller casing being fixedly connected to the outer cylinder of the casing by bolts.
  • the trough dynamic pressure gas radial bearing comprises a bearing outer casing and a bearing inner sleeve, and the outer circumferential surface and the opposite end surfaces of the inner bearing sleeve have regular groove patterns.
  • the groove pattern of one end surface of the bearing inner sleeve is mirror-symmetrical with the groove pattern of the other end surface, and the axial contour line of the groove pattern of the outer circumferential surface and the groove pattern of the both end surfaces
  • the radial contour lines form a one-to-one correspondence and intersect each other.
  • the axial high line in the groove pattern of the outer circumferential surface of the bearing inner sleeve corresponds to the radial high line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered.
  • the axial median line in the groove pattern of the outer circumferential surface corresponds to the radial median line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered;
  • the axial lower line in the middle corresponds to the radially lower line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered.
  • the matching gap between the bearing inner sleeve and the bearing outer sleeve is 0.003 to 0.008 mm.
  • a stop ring is provided at both ends of the bearing housing.
  • the ultra high speed blower further includes a hybrid dynamic pressure gas thrust bearing
  • the hybrid dynamic pressure gas thrust bearing includes two side plates and is sandwiched between the two side plates a middle plate, a foil-type elastic member is disposed between each of the side plates and the middle plate, and the hybrid dynamic pressure gas thrust bearing is formed at the housing and the end cover Inside the cavity, and sleeved on the shaft.
  • the end cap is fixedly connected to the middle disc adjusting ring of the hybrid dynamic pressure gas thrust bearing and the tail of the housing by bolts.
  • both end faces of the middle plate are provided with a regular pattern of groove patterns, and the groove pattern of one end face is mirror-symmetrical with the groove pattern of the other end face.
  • the outer circumferential surface of the intermediate disk is also provided with a groove pattern, and the shape of the groove pattern of the outer circumferential surface is the same as the shape of the groove pattern on both end faces, and the groove pattern of the outer circumferential surface
  • the axial contour line forms a one-to-one correspondence with the radial contour lines of the groove patterns on both end faces and intersects each other.
  • the axial high line in the groove pattern of the outer circumferential surface of the middle disk corresponds to the radial high line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered;
  • the outer circumference The axial median line in the groove pattern corresponds to the radial median line in the groove pattern on both end faces, and crosses each other before the end face is chamfered;
  • the axis in the groove pattern of the outer circumferential surface The low-order line corresponds to the radially lower line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered.
  • a wear-resistant coating is provided on the mating surface of the foil-type elastic member that is fitted to the intermediate disk.
  • the fitting gap between the foil-type elastic member and the middle plate is 0.003 to 0.008 mm.
  • At least one end of the foil-type elastic member is fixed to an inner end surface of the corresponding side disk.
  • the foil-type elastic members on each of the side plates are plural and evenly distributed along the inner end faces of the side plates.
  • the foil-type elastic member fixed to one side disk is mirror-symmetrical to the foil-shaped elastic member fixed to the other side disk.
  • a card slot for fixing the foil-type elastic member is provided on the inner end surface of the side disk.
  • the foil-type elastic member is composed of a wave foil and a flat foil, and the curved convex top end of the wave foil is attached to the flat foil.
  • the foil-type elastic member is composed of a wave foil and a flat foil, and the inter-wave arch transition bottom edge of the wave foil is in contact with the flat foil.
  • the foil-type elastic member is composed of two flat foils, wherein the flat foil near the end surface of the side disk has a plurality of bubbles, and the curved convex top end of the bubble is in phase with the other flat foil. fit.
  • the above-mentioned groove patterns are all impeller shapes.
  • the above-mentioned foil-type elastic member is preferably subjected to surface heat treatment.
  • the present invention has the following beneficial effects:
  • the blower provided by the present invention uses gas as a lubricant for the bearing, so that it has not only pollution-free, friction Low loss, long use time, wide application range, energy saving and environmental protection, etc., and adopting the structure, the heat dissipation effect is good, and the stable operation can be ensured for a long time; in particular, the air bearing of the structure can be realized in an air floating state. Under the ultra-high speed operation (tested, the limit speed can reach 100,000 ⁇ 450,000 rpm), so for the same power requirements, the present invention can significantly reduce the volume of the blower to achieve miniaturization, has the advantages of small footprint, convenient use, and the like. It is of great value to promote the development of miniaturized high-tech, and has significant progress compared to the prior art.
  • Embodiment 1 is a front perspective view of a super high speed blower provided in Embodiment 1;
  • Figure 2 is a front elevational view showing the structure of the super high speed blower provided in the first embodiment
  • Figure 3 is a view taken along line A-A of Figure 2;
  • FIG. 4 is a schematic perspective structural view of a rotary joint provided in Embodiment 1;
  • FIG. 6 is a partially divided left perspective view of the trough type dynamic pressure gas radial bearing provided in Embodiment 1;
  • Figure 7 is a partial enlarged view of B in Figure 6;
  • Figure 8 is a partially exploded right perspective view showing the slot type dynamic pressure gas radial bearing provided in Embodiment 1;
  • Figure 9 is a partial enlarged view of C in Figure 8.
  • Embodiment 10 is a schematic cross-sectional structural view of a hybrid dynamic pressure gas thrust bearing provided in Embodiment 1;
  • Figure 11a is a left side view of the center disk described in Embodiment 1;
  • Figure 11b is a right side view of the center disk described in Embodiment 1;
  • Figure 12a is a right side view of the left side disk to which the foil-type elastic member is fixed as described in Embodiment 1;
  • Figure 12b is a left side view of the right side disk with the foil-type elastic member fixed in Embodiment 1;
  • Figure 13 is a schematic cross-sectional view showing the foil-type elastic member provided in Embodiment 1;
  • Figure 14 is a perspective view showing the structure of the foil-type elastic member provided in Embodiment 1;
  • Figure 15a is a left side perspective structural view of a hybrid dynamic pressure gas thrust bearing provided in Embodiment 2;
  • Figure 16 is a partially sectional perspective structural view of the hybrid dynamic pressure gas thrust bearing provided in the second embodiment
  • Figure 17 is a left perspective view showing the middle plate of the second embodiment
  • Figure 18 is a partial enlarged view of D in Figure 17;
  • Figure 19 is a right perspective view showing the center disk of the second embodiment
  • Figure 20 is a partial enlarged view of E in Figure 19.
  • an ultrahigh speed blower provided by the embodiment includes an impeller 1 and a motor 2, the motor 2 including a rotor 21, a stator 22, a rotating shaft 23, an end cover 24 and a casing 25, It is characterized in that it further comprises a rotary joint 3, a trough dynamic pressure gas radial bearing 4 and a hybrid dynamic pressure gas thrust bearing 5.
  • the housing 25 is an annular cylindrical structure in which two cavities are formed by inner and outer cylinders, and the rotary connecting member 3 is a cylindrical structure having a cavity, and the rotating connecting member 3 is sleeved close to
  • the rotating shaft 23 of the impeller 1 is coupled to the end of the impeller 1 and the rotating shaft 23, and the side portion 31 of the rotating connecting member 3 is located in a cavity formed by the outer cylinder 251 and the inner cylinder 252 of the casing;
  • the slotted dynamic pressure gas radial bearing 4 and the rotating shaft 23 are both located in the cavity of the inner cylinder 252 of the casing, and the slot type dynamic pressure gas radial bearing 4 is sleeved on the rotating shaft 23;
  • the stator 22 is fixed On the outer wall of the inner cylinder 252 of the casing, the rotor 21 is fixed to the inner wall of the side portion 31 of the rotary joint 3.
  • the trough dynamic pressure gas radial bearing 4 includes a bearing outer casing 41 and a bearing inner sleeve 42;
  • the hybrid dynamic pressure gas thrust bearing 5 includes two side discs 51 and is interposed between the two side discs Disk 52, in each side disk 51 and middle plate 52 A foil-type elastic member 53 is disposed therebetween, and the hybrid dynamic pressure gas thrust bearing 5 is disposed in a cavity formed by the housing 25 and the end cover 24, and is sleeved on the rotating shaft 23.
  • a plurality of air guide vanes 32 are formed in the side portion 31 of the rotary link 3 above the air flow passage formed at the end of the rotary shaft 23 and the slot type dynamic pressure gas radial bearing 4.
  • a plurality of intake holes 253 and a plurality of heat dissipation vent holes 254 are opened on the circumferential side of the outer cylinder 251 of the casing, and the intake holes 253 communicate with the air guide vanes 32.
  • the impeller 1 is connected and fixed to the rotary joint 3 and the rotating shaft 23 by a locking bolt 6.
  • the rotating shaft 23 and the locking bolt 6 both open a cavity (231/61).
  • the ultra high speed blower further comprises an impeller casing 11 which is fixedly connected to the outer cylinder 251 of the casing by bolts 7.
  • the end cap 24 is fixedly coupled to the middle disc adjusting ring 54 of the hybrid dynamic pressure gas thrust bearing 5 and the tail portion of the housing 25 by bolts 8.
  • the outer circumferential surface and the left and right end surfaces of the bearing inner sleeve 42 each have a regular shape of the groove pattern 43 (431, 432 and 433 in the figure, the groove in this embodiment).
  • the pattern is an impeller shape
  • the groove pattern 432 of the left end surface is mirror-symmetrical with the groove pattern 433 of the right end surface.
  • the axial contour line of the groove pattern 431 located on the outer circumferential surface of the bearing inner sleeve 42 forms a one-to-one correspondence with the radial contour lines of the groove patterns (432 and 433) of the left and right end surfaces, and is mutually overlapped, that is, external
  • the axially high bit line 4311 in the circumferential groove pattern 431 corresponds to the radial high bit lines (4321 and 4331) in the groove patterns (432 and 433) of the left and right end faces, and is chamfered before the end face is chamfered Interacting with each other;
  • the axial center line 4312 in the groove pattern 431 of the outer circumferential surface corresponds to the radial center line (4322 and 4332) in the groove patterns (432 and 433) of the left and right end faces, and
  • the front end is circumferentially chamfered to each other;
  • the groove pattern 432 of the left end surface and the groove pattern 433 of the right end surface are mirror-symmetrical and outer circumference.
  • the axial contour line of the groove pattern 431 forms a one-to-one correspondence with the radial contour lines of the groove patterns (432 and 433) of the left and right end faces, and mutually intersects each other, thereby ensuring the groove pattern of the impeller shape at both end faces.
  • the pressurized gas generated by (432 and 433) is transported from the axial direction of the shaft to the groove passage formed by the groove pattern 431 of the outer circumferential surface, so as to form a gas film required for supporting the high-speed running bearing more strongly, and
  • the gas film is used as a lubricant for the dynamic pressure gas radial bearing, and thus is advantageous for achieving high-speed stable operation of the trough type dynamic pressure gas radial bearing 4 in an air floating state.
  • the fitting clearance between the bearing outer casing 41 and the bearing inner sleeve 42 is preferably 0.003 to 0.008 mm to further ensure the reliability and stability of the bearing at high speed.
  • a hybrid dynamic pressure gas thrust bearing provided by the embodiment includes: two side discs 51, and a middle disc 52 is interposed between the two side discs 51, at each side disc A foil-shaped elastic member 53 is disposed between the 51 and the intermediate plate 52.
  • the left end surface of the intermediate plate 52 is provided with a groove pattern 521 having a regular shape, and the right end surface is provided with a groove pattern 522 having a regular shape.
  • the groove pattern 521 of the left end surface of the middle plate 52 and the groove pattern 522 of the right end surface form mirror symmetry, and the radial contour line and the right end surface of the groove pattern 521 of the left end surface are formed.
  • the radial contours of the troughs 522 form a one-to-one correspondence.
  • the troughs 521 and 522 have the same shape, and are in the shape of an impeller in this embodiment.
  • the foil-type elastic member 53 is fixed on the inner end surface of the corresponding side disk 51 (for example, the left side disk 511 to which the foil-type elastic member 53a is fixed as shown in Fig. 12a and the left side disk 511 shown in Fig. 12b
  • the right side disc 512 to which the foil type elastic member 53b is fixed, and the foil type elastic member 53a fixed to the left side disc 511 is mirror-symmetrical with the foil type elastic member 53b fixed to the right side disc 512.
  • the foil-type elastic member 53 By providing the foil-type elastic member 53 between the side disk 51 and the intermediate disk 52, regular groove patterns (521 and 522) are provided on the left and right end faces of the middle plate 52, and the groove pattern 521 of the left end face is The groove pattern 522 of the right end surface is mirror-symmetrical, thereby obtaining a rigid characteristic of a high limit rotation speed of the groove type dynamic pressure gas thrust bearing, and a high impact resistance and load of the foil type dynamic pressure gas thrust bearing.
  • the hybrid dynamic pressure gas thrust bearing of the flexible nature of the capability because the foil-shaped elastic member 53 forms a wedge-shaped space with the intermediate disk 52, when the disk 52 rotates, the gas is driven by its own viscous action and is compressed to the wedge shape.
  • the axial dynamic pressure can be significantly enhanced, compared with the existing simple foil dynamic pressure gas thrust bearing, which can have a limit rotation speed which is multiplied under the same load; meanwhile, due to the increased foil type
  • the elastic member 53 can also significantly improve the bearing capacity, the impact resistance and the ability to suppress the whirl of the bearing under the elastic action, and can have the same in comparison with the existing simple groove type dynamic pressure gas thrust bearing. Doubling the speed of impact resistance and load capacity.
  • the foil-shaped elastic member 53 is composed of a wave foil 531 and a flat foil 532 , and the top end of the curved protrusion 5311 of the wave foil 531 is in contact with the flat foil 532 .
  • the inter-wave transition bottom edge 5312 of the wave foil 531 is in contact with the inner end surface of the corresponding side disk 51.
  • a wear-resistant coating (not shown) is provided on the mating surface of the foil-type elastic member 53 which is engaged with the intermediate plate 52.
  • a hybrid dynamic pressure gas thrust bearing provided by this embodiment differs from Embodiment 1 only in that:
  • a groove pattern 523 is also provided on the outer circumferential surface of the intermediate disk 52, and the shape of the groove pattern 523 of the outer circumferential surface is the same as that of the groove patterns (521 and 522) of the left and right end faces (this embodiment)
  • the axial contour of the groove pattern 523 of the outer circumferential surface and the radial contour lines of the groove patterns (521 and 522) of the left and right end faces are in one-to-one correspondence with each other and intersect with each other; :
  • the axially high bit line 5231 in the groove pattern 523 of the outer circumferential surface corresponds to the radial high line line 5211 in the groove pattern 521 of the left end surface, and is mutually overlapped before the end face is chamfered;
  • the groove of the outer circumferential surface The axial center line 5232 in the pattern 523 corresponds to the radial center line 5212 in the groove pattern 521 of the left end surface, and is mutually overlapped before the end surface is chamfered;
  • the axial low bit line 5233 corresponds to the radially lower bit line 5213 in the groove pattern 521 of the left end face, and overlaps each other before the end face is chamfered (as shown in FIG. 18);
  • the axially high bit line 5231 in the groove pattern 523 of the outer circumferential surface corresponds to the radial high line 5221 in the groove pattern 522 of the right end face, and is mutually overlapped before the end face is chamfered;
  • the groove of the outer circumferential surface The axial center line 5232 in the pattern 523 corresponds to the radial center line 5222 in the groove pattern 522 of the right end surface, and is mutually overlapped before the end surface is chamfered;
  • the axially lower bit line 5233 corresponds to the radially lower bit line 5223 in the groove pattern 522 of the right end face, and is mutually overlapped before the end face is chamfered (as shown in FIG. 20).
  • a groove pattern is also provided on the outer circumferential surface of the intermediate disk 52, and the shape of the groove pattern 523 of the outer circumferential surface is the same as that of the groove patterns (521 and 522) of the left and right end faces, and When the axial contour line of the groove pattern 523 of the circumferential surface forms a one-to-one correspondence with the radial contour lines of the groove patterns (521 and 522) of the left and right end faces, the groove pattern of both end faces of the inner disk can be obtained.
  • the pressurized gas generated by (521 and 522) is transported from the axial direction of the shaft to the groove passage formed by the groove pattern 523 of the outer circumferential surface so as to form a gas film which is stronger for supporting the high speed running bearing, and
  • the gas film is used as a lubricant for the dynamic pressure gas thrust bearing, so that the high-speed stable operation of the hybrid dynamic pressure gas thrust bearing in the air floating state can be further ensured, and further guarantee for realizing the high limit rotation speed of the air blower.
  • a card slot 513 (shown in Fig. 16) for fixing the foil-type elastic member 53 is provided on the inner end surface of the side disk 51.
  • the fitting clearance of the foil-type elastic member 53 and the intermediate disk 52 is preferably 0.003 to 0.008 mm to further ensure the reliability and stability of the high-speed operation of the bearing.
  • the foil-type elastic member 53 is preferably subjected to surface heat treatment.
  • composition of the foil-type elastic member 53 of the present invention is not limited to that described in the above embodiments. It is also possible to use a wave foil and a flat foil composition, but the transition edge between the wave arches of the wave foil is bonded to the flat foil; or, directly, two flat foils are used, wherein the flat foil near the end surface of the side disk has a plurality of bubbling The bubbled convex top end is conformed to the other flat foil; or other existing structures are employed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Motor Or Generator Frames (AREA)
  • Supercharger (AREA)
  • Slot Machines And Peripheral Devices (AREA)
  • Support Of The Bearing (AREA)

Abstract

La présente invention concerne une soufflante à très haute vitesse, comprenant une roue (1), un moteur (2), une pièce de raccordement rotative (3) et un palier radial à gaz sous pression dynamique de type à rainure (4). Le moteur comprend un rotor (21), un stator (22), un arbre rotatif (23), un couvercle d'extrémité (24) et un logement (25), le logement (25) étant une structure cylindrique annulaire composée d'un cylindre interne et d'un cylindre externe et présentant deux cavités, la pièce de raccordement rotative (3) étant une structure cylindrique présentant une seule cavité, la pièce de raccordement rotative étant emmanchée sur l'arbre rotatif (23) à proximité de la roue (1), et étant montée respectivement avec et raccordée à la roue (1) et à une partie d'extrémité de l'arbre rotatif (23), une partie latérale (31) de la pièce de raccordement rotative étant située à l'intérieur d'une cavité formée par le cylindre externe (251) et le cylindre interne (252) du logement. Le palier radial à gaz sous pression dynamique de type à rainure (4) et l'arbre rotatif (23) sont situés à l'intérieur d'une cavité du cylindre interne (252) du logement, et le palier radial à gaz sous pression dynamique de type à rainure (4) est emmanché sur l'arbre rotatif (23). Le stator (22) est fixé sur une paroi externe du cylindre interne (252) du logement, et le rotor (21) est fixé sur une paroi interne de la partie latérale (31) de la pièce de raccordement rotative (3). La soufflante met en œuvre un fonctionnement à très haute vitesse dans un vitesse dans un état d'air, et par rapport à des exigences de puissance identiques, la taille de la soufflante est nettement réduite pour miniaturisation.
PCT/CN2016/082676 2015-05-19 2016-05-19 Soufflante à très haute vitesse Ceased WO2016184404A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
CNPCT/CN2015/079233 2015-05-19
PCT/CN2015/079233 WO2016183787A1 (fr) 2015-05-19 2015-05-19 Palier radial à gaz sous pression dynamique de type à rainure
PCT/CN2015/079234 WO2016183788A1 (fr) 2015-05-19 2015-05-19 Palier de butée à gaz sous pression dynamique de type mixte
CNPCT/CN2015/079234 2015-05-19
CN201610327807.5A CN105889097B (zh) 2015-05-19 2016-05-18 一种超高速鼓风机
CN201610327807.5 2016-05-18

Publications (1)

Publication Number Publication Date
WO2016184404A1 true WO2016184404A1 (fr) 2016-11-24

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Application Number Title Priority Date Filing Date
PCT/CN2016/082676 Ceased WO2016184404A1 (fr) 2015-05-19 2016-05-19 Soufflante à très haute vitesse
PCT/CN2016/082711 Ceased WO2016184414A1 (fr) 2015-05-19 2016-05-19 Moteur à turboréacteur à vitesse ultra-élevée
PCT/CN2016/082707 Ceased WO2016184410A1 (fr) 2015-05-19 2016-05-19 Dispositif de turbocompression de génération d'énergie et entraîné par moteur à vitesse ultra-élevée
PCT/CN2016/082705 Ceased WO2016184408A1 (fr) 2015-05-19 2016-05-19 Turbogénérateur à vitesse ultra élevée
PCT/CN2016/082702 Ceased WO2016184406A1 (fr) 2015-05-19 2016-05-19 Moteur à ultra-haute vitesse
PCT/CN2016/082709 Ceased WO2016184412A1 (fr) 2015-05-19 2016-05-19 Turbogénérateur à gaz à vitesse ultra élevée
PCT/CN2016/082713 Ceased WO2016184416A1 (fr) 2015-05-19 2016-05-19 Turbocompresseur à vitesse ultra élevée

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Application Number Title Priority Date Filing Date
PCT/CN2016/082711 Ceased WO2016184414A1 (fr) 2015-05-19 2016-05-19 Moteur à turboréacteur à vitesse ultra-élevée
PCT/CN2016/082707 Ceased WO2016184410A1 (fr) 2015-05-19 2016-05-19 Dispositif de turbocompression de génération d'énergie et entraîné par moteur à vitesse ultra-élevée
PCT/CN2016/082705 Ceased WO2016184408A1 (fr) 2015-05-19 2016-05-19 Turbogénérateur à vitesse ultra élevée
PCT/CN2016/082702 Ceased WO2016184406A1 (fr) 2015-05-19 2016-05-19 Moteur à ultra-haute vitesse
PCT/CN2016/082709 Ceased WO2016184412A1 (fr) 2015-05-19 2016-05-19 Turbogénérateur à gaz à vitesse ultra élevée
PCT/CN2016/082713 Ceased WO2016184416A1 (fr) 2015-05-19 2016-05-19 Turbocompresseur à vitesse ultra élevée

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CN (14) CN205858730U (fr)
TW (2) TWI694210B (fr)
WO (7) WO2016184404A1 (fr)

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