[go: up one dir, main page]

WO2021129426A1 - 一种并联轴承及转子系统 - Google Patents

一种并联轴承及转子系统 Download PDF

Info

Publication number
WO2021129426A1
WO2021129426A1 PCT/CN2020/135893 CN2020135893W WO2021129426A1 WO 2021129426 A1 WO2021129426 A1 WO 2021129426A1 CN 2020135893 W CN2020135893 W CN 2020135893W WO 2021129426 A1 WO2021129426 A1 WO 2021129426A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
stator
parallel
rotating shaft
air
Prior art date
Application number
PCT/CN2020/135893
Other languages
English (en)
French (fr)
Inventor
靳普
刘慕华
Original Assignee
至玥腾风科技集团有限公司
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by 至玥腾风科技集团有限公司 filed Critical 至玥腾风科技集团有限公司
Priority to KR1020227009498A priority Critical patent/KR20220048030A/ko
Priority to US17/624,260 priority patent/US20220325749A1/en
Priority to JP2022507680A priority patent/JP2022544162A/ja
Priority to AU2020414869A priority patent/AU2020414869B2/en
Priority to CA3156235A priority patent/CA3156235A1/en
Priority to EP20906777.6A priority patent/EP3964723B1/en
Publication of WO2021129426A1 publication Critical patent/WO2021129426A1/zh

Links

Images

Classifications

    • 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
    • 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
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
    • F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
    • F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement
    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • F16C27/045—Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
    • 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
    • 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
    • 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
    • F16C32/0629—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 liquid cushion, e.g. oil 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
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/043—Sliding surface consisting mainly of ceramics, cermets or hard carbon, e.g. diamond like carbon [DLC]
    • 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
    • F16C33/20—Sliding surface consisting mainly of plastics
    • F16C33/201—Composition of the plastic
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/62—Selection of substances
    • 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
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/004—Electro-dynamic machines, e.g. motors, generators, actuators
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/62—Positive connections with pins, bolts or dowels
    • 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/70—Positive connections with complementary interlocking parts
    • F16C2226/76—Positive connections with complementary interlocking parts with tongue and groove or key and slot
    • 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
    • F16C2229/00—Setting preload
    • 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
    • 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
    • F16C2360/24—Turbochargers
    • 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
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators

Definitions

  • the invention relates to the technical field of bearings, in particular to a parallel bearing and a rotor system.
  • the DN value is a reference value for the selection of rolling bearing lubricants, where D is the bearing diameter and N is the relative speed of the inner and outer rings of the bearing. Bearings with a high DN value have higher requirements on the adhesion, working life, and working temperature of grease or oil, and the price of such grease or oil is usually higher.
  • the patent application No. 201480053353.6 entitled “Bearing device for turbocharger and manufacturing method of bearing device for turbocharger” provides a bearing device which is outside the ball bearing
  • the cylinder body equivalent to the oil film bearing is nested, but the inner wall of the cylinder and the outer ring of the ball bearing are fixed, and there is relative rotation between the outer wall and the stator, which is equivalent to adding a protective sleeve to the outside of the ball bearing, but there is no
  • high-performance grease or lubricating oil is still required.
  • the support function is achieved by the compressed air between the shaft and the inner ring of the bearing.
  • a rubber ring is installed between the outer diameter of the bearing and the bearing seat, relying on the rubber ring and the outer ring of the bearing.
  • the friction between the diameters fixes the bearing and prevents it from rotating in the circumferential direction.
  • the rotation speed of the rotating shaft reaches more than 100,000 revolutions, there will be air friction between the compressed air film and the rotating shaft, and this friction also increases with the increase of the rotating shaft speed.
  • the torque generated by the friction force makes the air bearing rotate more obviously and frequently with the rotating shaft.
  • the present invention provides a parallel bearing and a rotor system with a parallel bearing, which can solve the problem that the existing contact bearing is highly dependent on lubricant, the existing non-contact bearing and the high-speed rotating shaft The friction between the technical problems is too large.
  • the present invention adopts the following technical solutions.
  • a parallel bearing includes a rotating shaft bearing and a stator bearing; the rotating shaft bearing is a contact bearing, and the rotating shaft bearing is sleeved on the rotating shaft; the stator bearing is a non-contact bearing, the stator bearing is sleeved on the rotating shaft bearing, and the stator bearing and the rotating shaft bearing are reserved. There is a gap, and the stator bearing is fixed on the stator.
  • the parallel bearing also includes a bearing housing, the bearing housing is arranged on one end surface and the outer circumference of the stator bearing, the bearing end cover is arranged on the other end surface of the stator bearing and is fixed to the bearing housing, the bearing housing The body and/or the bearing end cover are fixed on the stator, and the stator bearing and the bearing housing or the bearing end cover are fixed in the circumferential direction.
  • the outer peripheral surface of the stator bearing is provided with an air cavity, and the bottom of the air cavity is provided with an air hole.
  • One end of the air hole is connected to the air cavity, and the other end is connected to the gap between the stator bearing and the shaft bearing.
  • the circumferential fixed connection mode of the stator bearing and the bearing housing or the bearing end cover is pin connection, pin connection or key connection.
  • the rotating shaft bearings are ball bearings, ceramic bearings or tetrafluoroethylene bearings, and the ball bearings can be single-row, double-row or multi-row ball bearings;
  • the rotating shaft bearing is a pair of angular contact ball bearings arranged oppositely, and a preloaded spring is arranged between the outer rings of the two angular contact ball bearings.
  • the stator bearing is an air bearing, an oil film floating ring bearing or a tilting pad bearing.
  • the rotating shaft bearing is a ball bearing
  • the stator bearing is an air bearing
  • the parallel bearing further includes at least one intermediate bearing, the intermediate bearing is a contact bearing, the intermediate bearing is sleeved between the rotating shaft bearing and the stator bearing, and a gap is left between the stator bearing and the intermediate bearing.
  • the intermediate bearing is a ball bearing.
  • the present invention also provides a rotor system with parallel bearings.
  • the rotor system includes two identical parallel bearings as described above, namely, a first parallel bearing and a second parallel bearing.
  • the first parallel bearing and the second parallel bearing are sleeved in pairs On the shaft.
  • the rotor system further includes a turbine, a compressor, a motor, and a thrust bearing; the rotating shaft passes through the thrust bearing, the first parallel bearing, the motor, the second parallel bearing, the compressor and the turbine arranged in sequence.
  • the rotating shaft rotates in the stator of the thrust bearing, the first parallel bearing, the stator of the motor, and the second parallel bearing, and the rotating shaft is fixedly connected with the thrust plate of the thrust bearing, the turbine of the turbine, and the compression wheel of the compressor .
  • the present invention can be applied to a micro gas turbine, which has the above-mentioned rotor system.
  • Microturbine (Microturbine or Micro-turbines) is a newly developed small heat engine with a single power range of 25 ⁇ 300kW.
  • the basic technical feature is the use of radial impeller machinery (radial turbine and centrifugal compressor) and Regeneration cycle.
  • the advanced micro gas turbine has a series of advanced technical features such as multiple integrated expansion, multiple fuel, low fuel consumption rate, low noise, low emission, low vibration, low maintenance rate, remote control and diagnosis, etc.
  • distributed power generation it can also be used for Standby power stations, combined heat and power, grid-connected power generation, peak load power generation, etc., are the best way to provide clean, reliable, high-quality, multi-purpose, small-scale distributed power generation and combined heat and power, whether for central cities, remote suburbs or even remote rural areas. Applicable to all regions.
  • micro gas turbines have advantages in civil transportation (hybrid vehicles), military vehicles, and land and sea defenses. They have attracted the attention of military powers such as the United States and Russia. Therefore, the development of micro gas turbines is also very important from the perspective of national security.
  • Micro gas turbines can be used for distributed power generation. Compared with central power stations, the power station is closer to users and has better reliability; for end users, it is a better environmentally friendly power generation device than other small power generation devices. Or it will become one of the basic components of public utilities in the future, which can operate in parallel with central power plants in the future.
  • the beneficial effects of the present invention are that the parallel bearing has low cost, the relative speed of each stage bearing in the parallel bearing is reduced, is not limited by the theoretical DN value, and the dependence on lubricating oil is low.
  • an air film exists between the rotating shaft and the air bearing. As the speed of the rotating shaft increases or the shaft diameter of the rotating shaft increases, the friction force further increases.
  • the parallel bearing of the present invention is used, the air The film exists between the outer ring of the rolling bearing and the air bearing. Because the speed of the outer ring of the rolling bearing is small, the relative speed between the air film and the air bearing is relatively small, the friction is small, and the rotation speed relative to the bearing seat is also small.
  • the rubber ring between the air bearing and the bearing housing is not easy to wear and has a long service life.
  • the speed of multiple parallel bearings on the same rotating shaft can be adjusted adaptively, without artificial setting or adjustment of the speed, and the effect of synchronous rotation can be achieved.
  • Fig. 1 is a schematic diagram of a parallel bearing structure according to the first embodiment of the present invention.
  • Fig. 2 is a side view of the parallel bearing structure according to the first embodiment of the present invention.
  • Fig. 3 is a schematic diagram of the parallel bearing structure of the second embodiment of the present invention.
  • Figure 4 is a schematic structural diagram of a rotor system with parallel bearings.
  • Fig. 5 is a structural diagram of the parallel bearing of the present invention arranged at both ends of the shaft.
  • Fig. 6 is a schematic diagram of the positional relationship of the bearing when the rotating shaft is started in the present invention.
  • Fig. 7 is a schematic diagram of the positional relationship of the bearing when the rotating shaft is stable in the present invention.
  • Fig. 8 is a schematic structural diagram of an angular contact ball bearing selected for the shaft bearing in the third embodiment of the present invention.
  • Fig. 9 is a structural schematic diagram of an integrated multi-layer bearing selected for the shaft bearing of the present invention.
  • a parallel bearing provided by the present invention is used to be installed on the rotating shaft 100 to support the rotating shaft 100 in the radial direction.
  • the parallel bearing in this embodiment includes a rotating shaft bearing 1 and a stator bearing 2.
  • the rotating shaft bearing 1 is sleeved on the rotating shaft 100, and the stator bearing 2 is sleeved outside the rotating shaft bearing 1 and maintains a certain gap with the outer wall of the rotating shaft bearing 1.
  • the bearing housing 4 is arranged on one end surface and the outer circumference of the stator bearing 2, and the bearing end cover 5 is arranged on the other end surface of the stator bearing 2 and is fixed in contact with the bearing housing 4, and the bearing housing 4 and the bearing end cover 5 are fixed.
  • the stator bearing 2 and the bearing housing 4 or the bearing end cover 5 are fixed in the circumferential direction.
  • the outer peripheral surface of the stator bearing 2 is provided with an air cavity 22, and the bottom of the air cavity 22 is provided with an air hole 23.
  • One end of the air hole 23 is connected to the air cavity 22, and the other end is connected to the gap between the stator bearing 2 and the rotating shaft bearing 1.
  • the stator bearing 2 and the bearing shell An apron 21 is also provided between the bodies 4.
  • the circumferential fixed connection mode of the stator bearing 2 and the bearing housing 4 or the bearing end cover 5 is pin connection, pin connection or key connection.
  • the pin can be fixedly installed on the end surface of the stator bearing 2, and the bearing housing 4 is provided with corresponding accommodating holes.
  • the pin can be fixedly installed on the end surface of the bearing housing 4 facing the stator bearing 2, and the stator bearing 2 is provided with a corresponding accommodating hole.
  • the pin or pin can be installed from the outer circumference of the bearing housing 4 along the radial direction of the bearing housing 4. One end of the pin is fixed to the bearing housing 4, and the other end is inserted into the outer circumference of the stator bearing 2.
  • the outer circumference of the stator bearing 2 is provided with a corresponding accommodation hole.
  • the key can be fixedly installed on the end face of the stator bearing 2 or integrally formed with one end face of the stator bearing 2, and the bearing housing 4 is provided with a corresponding key groove.
  • the key can be fixedly installed on the inner diameter surface of the bearing housing 4, or integrally formed with the inner diameter surface of the bearing housing 4, and the stator bearing 2 is provided with a corresponding key groove.
  • the present invention uses a ball bearing as the rotating shaft bearing 1 and an air bearing as the stator bearing 2.
  • the rotating shaft 100 When the rotating shaft 100 rotates, it drives the inner ring of the ball bearing to rotate, and an air film is formed between the outer ring of the rolling bearing and the air bearing.
  • the air bearing is fixed on the stator and has a relative speed with the outer ring of the rolling bearing.
  • the inner ring speed of the ball bearing is set to V2
  • the outer ring speed is V1
  • the air bearing speed is V0
  • the air bearing is fixed on the stator
  • V0 is approximately 0
  • the parallel bearing of the present invention is suitable for working conditions of large shaft diameter and high speed.
  • the damping and stiffness of the parallel bearing of the present invention are not lower than the damping and stiffness of a single bearing.
  • the parallel bearing includes a rotating shaft bearing 1, a stator bearing 2 and an intermediate bearing 6.
  • an intermediate bearing 6 is sleeved on the shaft bearing 1 (or a plurality of intermediate bearings 6 are sleeved in sequence and each intermediate bearing 6 is coaxial), and the stator bearing 2 is sleeved on the outermost periphery
  • the middle bearing 6 is outside and a certain gap is maintained with the outer wall of the outermost middle bearing 6.
  • the intermediate bearing 6 is a ball bearing.
  • the rotating shaft 100 starts, the outer ring of the intermediate bearing 6 contacts the bottom of the stator bearing 2.
  • the inner ring of the rotating shaft bearing 1 is driven to rotate.
  • the outer ring of the intermediate bearing 6 and the rotating shaft bearing 1 Due to the gradual separation of the outer ring due to the action of the air or oil film, the rotating shaft 100 drives the rotating shaft bearing 1 and the intermediate bearing 6 to rotate eccentrically in the stator bearing 2.
  • the rotating shaft 100, the rotating shaft bearing 1, and the intermediate bearing 6 are at the same time. Shaft, and eccentrically rotates around a certain circle in the stator bearing 2.
  • the outer ring of the shaft bearing 1 and the inner ring and outer ring of each intermediate bearing 6 all rotate.
  • the ball bearing or roller bearing of the rotating shaft bearing 1 in the first and second embodiments of the present invention is an integrated multi-layer bearing, and the ball or roller layer is arranged in multiple layers, see FIG. 9.
  • the solution provided by the present invention is to select a pair of angular contact ball bearings to be arranged oppositely, and to set a preloaded spring between the outer rings of the two angular contact ball bearings.
  • the ball and the cage can be moved closer or farther away, that is, the internal friction of the bearing can be increased or decreased, so as to achieve the purpose of the friction suitable for the required working conditions.
  • the parallel bearing of the present invention can be arranged in pairs on the rotating shaft 100. See Figure 5.
  • the rotating shaft 100 rotates, it drives the inner ring of the rotating shaft bearing 1 to rotate.
  • the outer ring of the rotating shaft bearing 1 or the outer ring of the outermost intermediate bearing 6 is It rotates under the action of air bearing or oil film floating ring bearing.
  • the speed of multiple parallel bearings on the same rotating shaft will be adaptively adjusted according to the force to achieve the effect of synchronous rotation.
  • the parallel bearing of the present invention can be applied to high-speed rotating shaft operating conditions such as rotor systems and micro gas turbine systems.
  • the present invention also provides a rotor system including the above-mentioned parallel bearing, which includes: a rotating shaft 100, a turbine 700, a compressor 600, a motor 400, a first parallel bearing 300, a second parallel bearing 500, and thrust
  • the shaft 100 passes through the thrust bearing 200, the first parallel bearing 300, the motor 400, the second parallel bearing 500, the compressor 600, and the turbine 700 that are arranged in sequence.
  • the shaft 100 is mounted on the thrust bearing 200,
  • the first parallel bearing 300, the stator of the motor 400, and the second parallel bearing 500 rotate inside, and the rotating shaft 100 is fixedly connected to the thrust plate 210 of the thrust bearing 200, the turbine of the turbine 700, and the compression wheel of the compressor 600.
  • the first parallel bearing 300 and the second parallel bearing 500 adopt the parallel bearing of the present invention.
  • the rotation speed of the outer ring of the shaft bearing 1 of the first parallel bearing 300 and the second parallel bearing 500 is fully dependent on the rotation conditions to adapt to The effect of reliably rotating the shaft 100.
  • the thrust bearing 200 is a non-contact bearing.
  • the thrust bearing 200 is a gas bearing, which may specifically be any one of a dynamic pressure bearing, a static pressure bearing, or a dynamic and static pressure parallel bearing.
  • the turbine of the turbine 700 may be made of ceramic turbine materials or other materials with lower thermal conductivity.
  • a reinforcing ring is provided between the compressor 600 and the turbine 700.
  • the lighter the weight of the shaft 100 the better, and the smaller the diameter of the shaft 100, the lighter the weight.
  • the strength of the shaft 100 is very high. Claim.
  • the shaft diameter between the compressor 600 and the turbine 700 can be set thinner, and at the same time, a reinforcement ring can be installed between the compressor 600 and the turbine 700 to meet Its requirements on the stiffness of the rotor.
  • the rotor system of the present invention includes but is not limited to the above distribution.
  • the present invention is applied to a miniature gas turbine, all the bearings are arranged in the motor casing, so it is only necessary to ensure the machining accuracy of the part in the casing for setting the bearing stator, and the casing is used for connection during assembly
  • the position of the bearing stator can be completed by one-time clamping and processing. It can be seen that the present invention reduces the processing precision and assembly precision of the micro gas turbine, reduces the cost, and is suitable for engineering batch production.
  • the micro gas turbine of the present invention has a compact layout, short axial length of the rotating shaft, and good stability of the high-speed operation of the rotor system.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Ceramic Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Sliding-Contact Bearings (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Abstract

一种并联轴承，包括转轴轴承（1）和定子轴承（2）；转轴轴承（1）为接触式轴承，转轴轴承（1）套设于转轴（100）上；定子轴承（2）为非接触式轴承，定子轴承（2）套设于转轴轴承（1）上，定子轴承（2）与转轴轴承（1）留有间隙。该并联轴承成本低廉，每一级轴承的相对转速减小，不受理论DN值限制，对润滑油的依赖性低。具有该并联轴承的转子系统，该系统同一转轴上的多个并联轴承的转速可以自适应调节，能够达到同步转动的效果，转子系统高速运行的平稳性好。

Description

一种并联轴承及转子系统 技术领域
本发明涉及轴承技术领域，具体涉及一种并联轴承及转子系统。
背景技术
DN值是选用滚动轴承润滑油的一个参考值，其中，D为轴承直径，N为轴承内外圈相对转速。高DN值的轴承对润滑脂或润滑油的附着性、工作寿命、工作温度要求都比较高，而这类润滑脂或润滑油的价格通常也较高。
理论上来说，转轴轴径越粗，就能承受更大的载荷，也能承受更大的临界转速，但是这样会使与之相配合的轴承DN值变大，就需要较高性能的润滑油，否则会造成轴承磨损、卡轴等故障。
为了解决轴承磨损这一问题，申请号为201480053353.6、名为“涡轮增压器用轴承装置、以及涡轮增压器用轴承装置的制造方法”的专利提供了一种轴承装置，该装置是在滚珠轴承外嵌套了相当于油膜轴承的筒体，但是该筒体内壁与滚珠轴承外圈是固定的、外壁与定子之间存在相对转动，相当于为滚珠轴承外部增加了一层保护套，但是并没有改变轴承的相对转速，仍然需要高性能润滑脂或润滑油。
对于非接触式轴承，如径向空气轴承，是依靠轴和轴承内圈之间的压缩空气来实现支撑功能，通常采用在轴承外径和轴承座之间安装橡胶圈，依靠橡胶圈和轴承外径之间的摩擦力来固定轴承，防止其发生周向转动。但是在空气轴承的实际运用过程中，当旋转轴的转速达到大概10万转以上时，压缩空气气膜和旋转轴之间会存在气摩擦，该摩擦也随着转轴转速的增大而增大，该摩擦力产生的扭矩使得空气轴承随着旋转轴转动更加明显和频繁。并且随着旋转轴转速的进一步提高或者旋转轴的轴径的增大，气膜与径向空气轴承内径之间的摩擦力进一步增大，径向空气轴承相对于轴承座之间的旋转速度增大，橡胶圈会很容易磨损损坏。
发明内容
为了克服现有技术的上述缺陷，本发明提供一种并联轴承以及具有并联轴承的转子系统，可解决现有接触式轴承对润滑剂的依赖性高、现有非接触式轴承与高速旋转的转轴之间的摩擦力过大的技术问题。
为了实现上述目的，本发明采用如下技术方案。
一种并联轴承，包括转轴轴承和定子轴承；转轴轴承为接触式轴承，转轴轴承套设于转 轴上；定子轴承为非接触式轴承，定子轴承套设于转轴轴承上，定子轴承与转轴轴承留有间隙，定子轴承固定于定子上。
作为进一步改进，所述并联轴承还包括轴承壳体，轴承壳体罩设于定子轴承的一个端面及外周上，轴承端盖设置在定子轴承的另一个端面上并与轴承壳体固定，轴承壳体和/或轴承端盖固定于定子上，定子轴承与轴承壳体或轴承端盖在周向上固定。
所述定子轴承的外周面设置有气腔，气腔底部设置有气孔，气孔一端连通气腔，另一端连接定子轴承与转轴轴承之间的间隙，定子轴承与轴承壳体之间还设有胶圈。
进一步地，定子轴承与轴承壳体或轴承端盖的周向固定连接方式为销连接、销钉连接或键连接。
所述转轴轴承为滚珠轴承、陶瓷轴承或四氟乙烯轴承，而滚珠轴承可选单列、双列或多列滚珠轴承；
所述转轴轴承为相对设置的一对角接触球轴承，两个角接触球轴承的外圈之间设置预载弹簧。
定子轴承为空气轴承、油膜浮环轴承或可倾瓦轴承。
所述转轴轴承为滚珠轴承，所述定子轴承为空气轴承。
作为进一步改进，所述并联轴承还包括至少一个中间轴承，中间轴承为接触式轴承，中间轴承套设于转轴轴承和定子轴承之间，定子轴承与中间轴承留有间隙。
所述中间轴承为滚珠轴承。
本发明还提供了一种具有并联轴承的转子系统，该转子系统包括两个相同的上述并联轴承，即第一并联轴承和第二并联轴承，第一并联轴承和第二并联轴承成对套设在转轴上。
作为进一步改进，所述转子系统还包括透平、压气机、电机、和推力轴承；所述转轴穿过依次设置的推力轴承、第一并联轴承、电机、第二并联轴承、压气机和透平，所述转轴在所述推力轴承的定子、第一并联轴承、电机的定子和第二并联轴承内旋转，所述转轴与推力轴承的推力盘以及透平的涡轮、压气机的压缩轮固定连接。
本发明可应用于微型燃气轮机，微型燃气轮机具有上述转子系统。
微型燃气轮机(Microturbine或Micro-turbines)是一类新近发展起来的小型热力发动机，其单机功率范围为25～300kW，基本技术特征是采用径流式叶轮机械(向心式透平和离心式压气机)以及回热循环。
先进微型燃气轮机具有多台集成扩容、多燃料、低燃料消耗率、低噪音、低排放、低振动、低维修率、可遥控和诊断等一系列先进技术特征，除了分布式发电外，还可用于备用电 站、热电联产、并网发电、尖峰负荷发电等，是提供清洁、可靠、高质量、多用途、小型分布式发电及热电联供的最佳方式，无论对中心城市还是远郊农村甚至边远地区均能适用。此外，微型燃气轮机在民用交通运输(混合动力汽车)以及军车以及陆海边防方面均具有优势，受到美、俄等军事大国的关注，因此，从国家安全看发展微型燃气轮机也是非常重要的。
微型燃气轮机可用于分布式发电，与中心电站相比，使电站更靠近用户，可靠性更好；对终端用户来说，与其它小型发电装置相比，是一种更好的环保型发电装置，或将成为未来公用事业的基本构成之一，将来可与中心电厂平行运行。
本发明的有益效果是，本并联轴承成本低廉，并联轴承中每一级轴承的相对转速减小，不受理论DN值的限制，对润滑油的依赖性低。现有技术中，气膜存在于转轴和空气轴承之间，随着旋转轴转速的进一步提高或者旋转轴的轴径的增大，摩擦力进一步增大，而采用本发明的并联轴承后，气膜存在于滚动轴承外圈和空气轴承之间，由于滚动轴承外圈的转速较小，气膜和空气轴承之间的相对转速就比较小，摩擦力小，相对于轴承座之间的旋转速度也小，因此空气轴承和轴承壳体之间的胶圈不容易磨损，使用寿命高。同一转轴上的多个并联轴承的转速可以自适应调节，不需要人为设定或调节转速，能够达到同步转动的效果。
附图说明
图1是本发明实施例一的并联轴承结构的示意图。
图2是本发明实施例一的并联轴承结构的侧视图。
图3是本发明实施例二的并联轴承结构示意图。
图4是具有并联轴承的转子系统的结构示意图。
图5是本发明并联轴承布置在轴两端的结构示意图。
图6是本发明中转轴启动时轴承的位置关系示意图。
图7是本发明中转轴稳定时轴承的位置关系示意图。
图8是本发明实施例三中转轴轴承选用角接触球轴承的结构示意图。
图9是本发明中转轴轴承选用一体式多层轴承的结构示意图。
具体实施方式
下面将结合附图对本发明的技术方案进行清楚、完整地描述，显然，所描述的实施例是本发明一部分实施例，而不是全部的实施例。
本发明提供的一种并联轴承，用于安装到转轴100，以在径向上支撑转轴100。
实施例一
参见图1、图2，本实施例中并联轴承包含一个转轴轴承1和一个定子轴承2。转轴轴承1套设于转轴100上，定子轴承2套设于转轴轴承1外，并与转轴轴承1外壁保持一定的间隙。
轴承壳体4罩设于定子轴承2的一个端面与外周，轴承端盖5设置在定子轴承2的另一个端面上并与轴承壳体4抵接固定，轴承壳体4及轴承端盖5固定于电机定子上，定子轴承2与轴承壳体4或轴承端盖5在周向上固定。
定子轴承2的外周面设置有气腔22，气腔22底部设置有气孔23，气孔23一端连通气腔22，另一端连接定子轴承2与转轴轴承1之间的间隙，定子轴承2与轴承壳体4之间还设有胶圈21。
定子轴承2与轴承壳体4或轴承端盖5的周向固定连接方式为销连接、销钉连接或键连接。
销可以固定安装于定子轴承2的端面，轴承壳体4上设置有相应的容纳孔。
销可以固定安装于轴承壳体4的朝向定子轴承2的端面，定子轴承2上设置有相应的容纳孔。
销或销钉可以从轴承壳体4的外周沿轴承壳体4的径向安装，销的一端固定于轴承壳体4，另一端插入定子轴承2的外周，定子轴承2的外周设置有相应的容纳孔。
键可以固定安装于定子轴承2的端面或者与定子轴承2的一个端面一体成型，轴承壳体4上设置有相应的键槽。
键可以固定安装于轴承壳体4的内径面，或者与轴承壳体4的内径面一体成型，定子轴承2上设置有相应的键槽。
参见图6，当转轴100启动时，转轴100外套的转轴轴承1与定子轴承2底部接触，随着转轴100的转动，带动转轴轴承1内圈转动，与此同时，定子轴承2与转轴轴承1外圈之间由于气膜或油膜作用逐渐分离，转轴轴承1在定子轴承2内偏心转动，当转轴100稳定高速运转时，转轴100、转轴轴承1同轴，并在定子轴承2内绕一圆周偏心转动，参见图7。同时，转轴轴承1的外圈发生自转。
进一步地，参见图1，本发明采用一个滚珠轴承作为转轴轴承1，采用一个空气轴承作为定子轴承2。
转轴100转动时，带动滚珠轴承内圈转动，滚动轴承的外圈和空气轴承之间形成气膜。空气轴承固定在定子上，与滚动轴承的外圈之间存在相对转速。
对于原有的滚珠轴承来说，当轴径一定时，对于原来的轴上设置的转轴轴承来说，当转轴转动时，设滚珠轴承内圈转速为V2、外圈转速为V0，由于外圈固定在定子上，V0近似为0，所以滚珠轴承外圈的相对转速n＝V2-V0。
采用本发明并联轴承后，当转轴100转动时，设滚珠轴承内圈转速为V2，外圈转速为V1，空气轴承转速为V0，空气轴承固定在定子上，V0近似为0，滚珠轴承外圈相对于内圈的速度差a＝V2-V1，相对于空气轴承的速度差b＝V1-V0，a和b均小于n。可见，滚动轴承内外圈相对转速是降低的，即同等情况下，实际DN值减小，选用普通的润滑脂即可满足需求。
以此类推，不论转轴轴承1上依次并联套设多少个滚动轴承，均不会使实际DN值变得过大，轴径D与轴承转速N之间已被解耦。因此，本发明的并联轴承，适用于大轴径、高转速工况。且本发明并联轴承的阻尼和刚度不低于单个轴承的阻尼和刚度，具体地，并联轴承阻尼＝空气轴承阻尼+各轴承胶圈阻尼；并联轴承刚度＝空气轴承刚度。
实施例二
参见图3，本实施例中，并联轴承包括一个转轴轴承1、一个定子轴承2和一个中间轴承6。
本实施例是在实施例一的基础上，在转轴轴承1上套设一个中间轴承6(或依次外套多个中间轴承6且各中间轴承6同轴)，定子轴承2套设于最外围的中间轴承6外，并与最外围的中间轴承6外壁保持一定的间隙。
具体地，中间轴承6选用滚珠轴承。参见图8，当转轴100启动时，中间轴承6外圈与定子轴承2底部接触，随着转轴100的转动，带动转轴轴承1内圈转动，与此同时，中间轴承6外圈与转轴轴承1外圈之间由于气膜或油膜作用逐渐分离，转轴100带动转轴轴承1及中间轴承6在定子轴承2内偏心转动，当转轴100稳定高速运转时，转轴100、转轴轴承1、中间轴承6同轴，并在定子轴承2内绕某一圆周偏心转动。同时，转轴轴承1的外圈、各中间轴承6的内圈及外圈均发生自转。
进一步地，本发明实施例一和实施例二中的转轴轴承1的滚珠轴承或滚柱轴承为一体式多层轴承，滚珠层或滚柱层设置为多层，参见图9。
实施例三
参见图8，当本发明的转轴轴承1选用角接触球轴承时，由于轴承内圈固定在转轴100上，外圈、保持架与滚珠之间会发生相对位移，通俗来讲是指轴承内部滚珠过于松动，需要采用适当的处理措施。
本发明提供的解决方案是选用一对角接触球轴承相对设置，两个角接触球轴承的外圈之 间设置预载弹簧。
通过调节弹簧的预载力，可以使滚珠和保持架之间靠近或远离，即可以使轴承内部摩擦力增大或减小，以达到适用于所需工况条件下的摩擦力的目的。
具体应用时，本发明的并联轴承可成对设置在转轴100上，参见图5，转轴100转动时，带动转轴轴承1内圈转动，转轴轴承1外圈或者最外围中间轴承6的外圈在空气轴承或者油膜浮环轴承的作用下转动。且同一转轴上的多个并联轴承的转速会根据受力进行自适应调节，达到同步转动的效果。
本发明的并联轴承可应用于转子系统、微型燃气轮机系统等高速转轴工况。
如图4所示，本发明还提供一种包含上述并联轴承的转子系统，其包括：转轴100、透平700、压气机600、电机400、第一并联轴承300、第二并联轴承500和推力轴承200，所述转轴100穿过依次设置的推力轴承200、第一并联轴承300、电机400、第二并联轴承500、压气机600和透平700，所述转轴100在所述推力轴承200、第一并联轴承300、电机400的定子和第二并联轴承500内旋转，所述转轴100与推力轴承200的推力盘210以及透平700的涡轮、压气机600的压缩轮固定连接。
上述转子系统中，第一并联轴承300和第二并联轴承500即采用本发明的并联轴承，第一并联轴承300和第二并联轴承500的转轴轴承1外圈转速完全依靠转动情况自适应，达到使转轴100可靠旋转的效果。
进一步地，推力轴承200为非接触式轴承。
进一步地，推力轴承200为气体轴承，其具体可以为动压轴承、静压轴承或者动静压并联轴承中的任一种。
进一步地，为降低涡轮热端导热对压气机600效率的影响，透平700的涡轮可以采用导热系数更低的陶瓷涡轮材料或其他材料制造。
优选地，在压气机600和透平700之间设置有加强环。
出于转子动力学性能方面的考虑，转轴100的重量越轻越好，而转轴100的直径越小则重量越轻，但是在转子系统高速旋转过程中，对转轴100的强度又有很高的要求。为了同时考虑转子动力学特性和转轴100的强度，可将压气机600与透平700之间的轴径设置的较细，而同时在压气机600和透平700之间安装加强环，以满足其对转子刚度的要求。
本发明的转子系统包括但并不限于以上分布情况。
本发明应用于微型燃气轮机中，所有的轴承全部设置在电机机匣内，这样只需保证该机 匣内用于设置轴承定子的部位的加工精度即可，在装配时该机匣内用于连接轴承定子的部位通过一次装卡加工即可完成，可见，本发明降低了微型燃气轮机的加工精度和装配精度，降低了成本，适合工程化批量生产。同时，本发明的微型燃气轮机布局紧凑，转轴的轴向长度短，转子系统高速运行的平稳性好。
上述虽然结合附图对本发明的具体实施方式进行了描述，但并非对本发明保护范围的限制，所属领域技术人员应该明白，在本发明的技术方案的基础上，本领域技术人员不需要付出创造性劳动即可做出的各种修改或变形仍在本发明的保护范围以内。

Claims (12)

  1. 一种并联轴承，其特征在于，包括转轴轴承和定子轴承；转轴轴承为接触式轴承，转轴轴承套设于转轴上；定子轴承为非接触式轴承，定子轴承套设于转轴轴承上，定子轴承内壁与转轴轴承外壁之间留有间隙，定子轴承固定于定子上。
  2. 如权利要求1所述的并联轴承，其特征在于，所述并联轴承还包括轴承壳体，轴承壳体罩设于定子轴承的一个端面及外周上，轴承端盖设置在定子轴承的另一个端面上并与轴承壳体固定，轴承壳体和/或轴承端盖固定于定子上，定子轴承与轴承壳体或轴承端盖在周向上固定。
  3. 如权利要求1所述的并联轴承，其特征在于，所述转轴轴承为滚珠轴承、陶瓷轴承或四氟乙烯轴承。
  4. 如权利要求1所述的并联轴承，其特征在于，所述转轴轴承为单列、双列或多列滚珠轴承。
  5. 如权利要求1所述的并联轴承，其特征在于，所述转轴轴承为相对设置的一对角接触球轴承，两个角接触球轴承的外圈之间设置预载弹簧。
  6. 如权利要求1所述的并联轴承，其特征在于，所述定子轴承为空气轴承、油膜浮环轴承或可倾瓦轴承。
  7. 如权利要求6所述的并联轴承，其特征在于，所述定子轴承为空气轴承，其外周面设置有气腔，气腔底部设置有气孔，气孔一端连通气腔，另一端连接定子轴承与转轴轴承之间的间隙，定子轴承与轴承壳体之间还设有胶圈。
  8. 如权利要求1所述的并联轴承，其特征在于，所述转轴轴承为滚珠轴承，所述定子轴承为空气轴承。
  9. 如权利要求1所述的并联轴承，其特征在于，所述并联轴承还包括至少一个中间轴承，中间轴承为接触式轴承，中间轴承套设于转轴轴承和定子轴承之间，定子轴承与中间轴承留有间隙。
  10. 如权利要求9所述的并联轴承，其特征在于，所述中间轴承为滚珠轴承。
  11. 一种转子系统，其特征在于，该转子系统包括两个相同的、如上述权利要求1或9所述的并联轴承，即第一并联轴承和第二并联轴承，第一并联轴承和第二并联轴承成对套设在转轴上。
  12. 如权利要求11所述的转子系统，其特征在于，所述转子系统还包括透平、压气机、电机、和推力轴承；所述转轴穿过依次设置的推力轴承、第一并联轴承、电机、第二并联轴承、压气机和透平，所述转轴在所述推力轴承的定子、第一并联轴承、电机的定子和第二并联轴承内旋转，所述转轴与推力轴承的推力盘以及透平的涡轮、压气机的压缩轮固定连接。
PCT/CN2020/135893 2019-12-23 2020-12-11 一种并联轴承及转子系统 WO2021129426A1 (zh)

Priority Applications (6)

Application Number Priority Date Filing Date Title
KR1020227009498A KR20220048030A (ko) 2019-12-23 2020-12-11 병렬 베어링 및 로터 시스템
US17/624,260 US20220325749A1 (en) 2019-12-23 2020-12-11 Parallel bearing and rotor system
JP2022507680A JP2022544162A (ja) 2019-12-23 2020-12-11 並列接続軸受及び回転子システム
AU2020414869A AU2020414869B2 (en) 2019-12-23 2020-12-11 Parallel bearing and rotor system
CA3156235A CA3156235A1 (en) 2019-12-23 2020-12-11 Parallel bearing and rotor system
EP20906777.6A EP3964723B1 (en) 2019-12-23 2020-12-11 Parallel bearing and rotor system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201911340107.X 2019-12-23
CN201911340107.XA CN110905919A (zh) 2019-12-23 2019-12-23 一种并联轴承

Publications (1)

Publication Number Publication Date
WO2021129426A1 true WO2021129426A1 (zh) 2021-07-01

Family

ID=69827243

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2020/135893 WO2021129426A1 (zh) 2019-12-23 2020-12-11 一种并联轴承及转子系统

Country Status (8)

Country Link
US (1) US20220325749A1 (zh)
EP (1) EP3964723B1 (zh)
JP (1) JP2022544162A (zh)
KR (1) KR20220048030A (zh)
CN (1) CN110905919A (zh)
AU (1) AU2020414869B2 (zh)
CA (1) CA3156235A1 (zh)
WO (1) WO2021129426A1 (zh)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110905919A (zh) * 2019-12-23 2020-03-24 至玥腾风科技集团有限公司 一种并联轴承
CN111022491A (zh) * 2019-12-23 2020-04-17 至玥腾风科技集团有限公司 一种并联轴承转子系统、电机及电器
CN114688062A (zh) * 2020-12-25 2022-07-01 珠海格力电器股份有限公司 气悬浮压缩机的控制方法、装置、存储介质及压缩机
CN112897121A (zh) * 2021-01-19 2021-06-04 宝武杰富意特殊钢有限公司 防止钢件表面刮伤的方法及立轮
CN114890216A (zh) * 2022-04-20 2022-08-12 义乌晶澳太阳能科技有限公司 旋转器及胶带机

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104203721A (zh) * 2012-04-12 2014-12-10 Zf操作系统有限公司 用于转向机构的浮动轴承
CN105431638A (zh) * 2013-05-30 2016-03-23 诺沃皮尼奥内股份有限公司 带有至少一个主动磁力轴承和辅助滚动轴承的旋转机械
CN108930715A (zh) * 2018-10-10 2018-12-04 杭州江河水电科技有限公司 一种双向相邻互质磁力及滚子混合推力轴承系统
CN109963769A (zh) * 2016-11-21 2019-07-02 罗伯特·博世有限公司 转向系统
CN110905919A (zh) * 2019-12-23 2020-03-24 至玥腾风科技集团有限公司 一种并联轴承
CN211343730U (zh) * 2019-12-23 2020-08-25 至玥腾风科技集团有限公司 一种并联轴承

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5544117A (en) * 1978-09-21 1980-03-28 Toshiba Corp Bearing unit
JPS56113224U (zh) * 1980-02-01 1981-09-01
US9234542B2 (en) * 2005-08-11 2016-01-12 Alpha Turbo Technologies, Llc Bearing system
JP2008008412A (ja) * 2006-06-29 2008-01-17 Jtekt Corp ジャーナル軸受ユニット
GB0714309D0 (en) * 2007-07-21 2007-08-29 Cummins Turbo Tech Ltd Turbocharger
CA2730109A1 (en) * 2010-04-28 2011-10-28 Mitsubishi Heavy Industries, Ltd. Direct-drive wind turbine generator and bearing structure
DE102010054996A1 (de) * 2010-12-17 2012-06-21 Schaeffler Technologies Gmbh & Co. Kg Lagereinheit für einen Turbolader
JP2016078721A (ja) * 2014-10-20 2016-05-16 株式会社ショーワ ストッパピース及び軸受装置
JP2019019751A (ja) * 2017-07-18 2019-02-07 パナソニックＩｐマネジメント株式会社 ガスタービンロータ及びガスタービン発電機
CN108868892B (zh) * 2018-01-12 2024-04-02 刘慕华 一种转子系统及其控制方法和燃气轮机发电机组及其控制方法

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104203721A (zh) * 2012-04-12 2014-12-10 Zf操作系统有限公司 用于转向机构的浮动轴承
CN105431638A (zh) * 2013-05-30 2016-03-23 诺沃皮尼奥内股份有限公司 带有至少一个主动磁力轴承和辅助滚动轴承的旋转机械
CN109963769A (zh) * 2016-11-21 2019-07-02 罗伯特·博世有限公司 转向系统
CN108930715A (zh) * 2018-10-10 2018-12-04 杭州江河水电科技有限公司 一种双向相邻互质磁力及滚子混合推力轴承系统
CN110905919A (zh) * 2019-12-23 2020-03-24 至玥腾风科技集团有限公司 一种并联轴承
CN211343730U (zh) * 2019-12-23 2020-08-25 至玥腾风科技集团有限公司 一种并联轴承

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3964723A4

Also Published As

Publication number Publication date
AU2020414869A1 (en) 2022-01-06
JP2022544162A (ja) 2022-10-17
EP3964723A4 (en) 2022-08-10
CN110905919A (zh) 2020-03-24
US20220325749A1 (en) 2022-10-13
AU2020414869B2 (en) 2024-01-04
CA3156235A1 (en) 2021-07-01
KR20220048030A (ko) 2022-04-19
EP3964723B1 (en) 2023-06-07
EP3964723A1 (en) 2022-03-09

Similar Documents

Publication Publication Date Title
WO2021129426A1 (zh) 一种并联轴承及转子系统
US7517154B2 (en) Turbocharger shaft bearing system
US7371011B2 (en) Turbocharger shaft bearing system
US7025579B2 (en) Bearing system for high-speed rotating machinery
US6739845B2 (en) Compact turbocharger
US20080087018A1 (en) Bearing systems for high-speed rotating machinery
US8845271B2 (en) Turbocharger bearing system
CN103206271B (zh) 涡轮机轴密封装置
WO2021129427A1 (zh) 一种组合轴承
US9695708B2 (en) Turbocharger spring assembly
US20110064340A1 (en) Method and apparatus for stabilizing a squeeze film damper for a rotating machine
JP2014159869A (ja) 転がり軸受装置
CN110094236A (zh) 一种氦气涡轮机轴系结构
CN211343730U (zh) 一种并联轴承
JP4383708B2 (ja) 低コストボールベアリングを有するターボチャージャのロータ
CN108054852B (zh) 一种电主轴
CN102163887B (zh) 高速电机用静压升举与滚动环轴承混合支承及该旋转机械
JP2009203846A (ja) ターボチャージャ用軸受装置
RU126056U1 (ru) Узел опоры газотурбинного двигателя
WO2021129428A1 (zh) 一种使用并联轴承的电机
CN108317159B (zh) 一种适用于多自由度球面运动装置的润滑轴承
CN101771307A (zh) 一种高速电动旋转机械的转子支承结构及该旋转机械
CN201420603Y (zh) 采用浮环球轴承的微型燃气轮机转子系统
CN216540869U (zh) 一种气静压陶瓷球复合轴承电主轴
RU2649280C1 (ru) Комбинированный радиальный подшипник с широким диапазоном рабочих скоростей и нагрузок (варианты)

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 20906777

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2020906777

Country of ref document: EP

Effective date: 20211130

ENP Entry into the national phase

Ref document number: 2020414869

Country of ref document: AU

Date of ref document: 20201211

Kind code of ref document: A

ENP Entry into the national phase

Ref document number: 2022507680

Country of ref document: JP

Kind code of ref document: A

ENP Entry into the national phase

Ref document number: 20227009498

Country of ref document: KR

Kind code of ref document: A

ENP Entry into the national phase

Ref document number: 3156235

Country of ref document: CA

NENP Non-entry into the national phase

Ref country code: DE