CN102121875A - Dynamic loading comprehensive experimental table for gas bearing-rotor system - Google Patents
Dynamic loading comprehensive experimental table for gas bearing-rotor system Download PDFInfo
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Abstract
The invention discloses a dynamic loading integrated experimental table for gas bearing-rotor system and relates to an ultrahigh-speed rotating machine loading technology which is mainly based on the key technologies of an ultrahigh-speed gas bearing supporting module, an integrated foundation supporting structure, a labyrinth-gas film joint sealing structure, static and dynamic loading mechanisms, a rotor system and the like. The experimental table comprises a radial gas bearing, a thrust gas bearing, a radial-thrust joint gas bearing, a bearing disassembling tool, an integrated case, a boss, a cover plate, a sealing bracket, a labyrinth sealing ring, a gas film sealing ring, a main support frame, a vibration exciter, an adjustable simple support beam, a discontinuous variable-cross-section simple support beam, a simple support beam loading adjusting bolt, a loading spring, a force-frequency sensor, a tilting pad loading bearing, a volute, a driving turbine, a thrust disc, a rotating shaft and the like. The experimental table has the advantages of simple structure, high reliability and strong comprehensiveness, is convenient to assemble and disassemble, and can ensure the gas bearings of the experimental table to be in a fully centered state; and in addition, the static loading force is stable and reliable, and the dynamic loading force and frequency are controllable.
Description
Technical field
The present invention relates to hypervelocity rotating machinery loading technique, be used to study that various hypervelocity rotating machinery block bearings are quiet, the experiment table of dynamic perfromance.
Background technology
Rotating machinery has important use in the every field of national economy, and the core component of rotating machinery supporting is a bearing.Bearing type commonly used at present has oil lubrication sliding bearing, rolling bearing, ceramic bearing, electromagnetic bearing, gas bearing etc.Gas bearing is a high-tech product that develops rapidly mid-term in 20th century, and it is compared with traditional rolling bearing or oily sliding bearing, has high rotating speed, high precision, low-power consumption, pollution-free, advantage such as the life-span is long, environmental suitability is strong.Therefore be widely used in industries such as national defence, the energy, lathe and medical treatment, especially obvious superiority more arranged at hypervelocity rotating machinery and ultraprecise Instrument technology field.
The performance of gas bearing-rotor-support-foundation system is to be related to quiet, the dynamic property of hypervelocity rotating machinery, the key factor of core qualities such as reliability, stability and life-span.Therefore to gas bearing-rotor-support-foundation system carry out experimental study work be the development of hypervelocity rotating machinery must be through one of step.The fundamental purpose of hypervelocity rotating machinery experimental study is quiet, the dynamic perfromance of test gas bearing, the i.e. static rigidity of gas bearing, dynamic rate, damping etc.Because the gas bearing friction power loss is extremely low, so its damping is less, so the major concern gas bearing is quiet, the dynamic rate index.
The experiment table quiet for gas bearing, that dynamic rate is tested, generally need satisfy following condition:
(1) static loading force is stable, easily control.Static loading need apply under the rotor high-speed operation, and static loading force itself needs to stablize, and controls easily and realizes.
(2) size of dynamic load power and changeable frequency.Dynamic load need apply under the rotor high-speed operation, the size of dynamic load power, changeable frequency, and have certain tuning range; The dynamic rate of gas bearing is a most important parameters of weighing the gas bearing performance; The rigidity of the test of gas bearing under dynamic exciting is only the dynamic rate of gas bearing, and the dynamic rate of gas bearing changes with dynamic loading frequency.Dynamic rate and static rigidity differ greatly.
(3) guarantee that each gas bearing of experiment table is in state entirely on the center.Because the gas bearing working clearance is between 20-50um, if the experiment table design is improper, will cause that radially right alignment, radial parallel degree occur than mistake in experiment table processing and the installation process, directly caused gas bearing excentricity and actual conditions not to be inconsistent, and gas bearing rigidity and excentricity are nonlinear relationship, therefore the centering state of experiment table design (comprises axially parallel degree, radial parallel degree, down with) have a strong impact on the precision of gas bearing rigidity test, have a strong impact on the dynamics of gas bearing-rotor-support-foundation system.
(4) simple for structure, the easy accessibility of experiment table itself, favorable repeatability.Because the gas bearing of experiment table is an experimental subjects, they are operated under high rotating speed and the various variable working condition, also are easily worn parts, and in process of the test, often needing, the experimental subjects of replacing different parameters is a gas bearing; Therefore, experiment table also needs to have simple for structure, and easy accessibility be convenient for changing the bearing of testing bearing, damage, but various state has harsh requirements such as comparative, repeatability.
At present for various bearings, especially the experiment table tested of hypervelocity gas bearing does not all possess above characteristics.There are big problem in its function, precision etc.
Patented claim:
Dynamical and static pressure gas bearing test platform radially, application number: 200820028010.6, see shown in Figure 1ly, its main contents are as follows: it by base 1, test bearing 2, test main shaft 3, pole 4, orienting sleeve 5, transfer power screw rod 6, pulling force sensor 7, tension spring 8, load bearings 9, support 10, bearing 11 to constitute.This experiment table test gas bearing static characteristics, guarantee static loading force even aspect, have advantages of high practicability, but have following 3 subject matters:
(1) can't realize the dynamic load of bearing, promptly the frequency of dynamic load power can't change.Therefore can't obtain the dynamic rate performance of gas bearing.This performance is the most important evaluating of gas bearing.
(2) load bearings of two of experiment table symmetric arrangement (original text numbering 9) lays respectively on three different bearing seats (bracing or strutting arrangement of bearing) with a test bearing (original text numbering 2), and load bearings and test bearing structure are not quite similar, this is difficult to guarantee the right alignment that requires with regard to the axle center that causes three bearings, promptly in processing and the installation process, all be difficult to realize the right alignment that requires.Gas bearing air film gap is that off-centre is generally between 20-50um, therefore the off-centre of three gas bearing of experiment table can't guarantee in the permissible accuracy scope, and the off-centre of gas bearing directly has influence on the rigidity of gas bearing, and the stiffness measurement result of gas bearing exists than mistake.
(3) go wrong or because other reasons need change the time, can't guarantee original state, the experiment table repeatability is relatively poor when the experiment table bearing.
Patented claim: the bearing charger, application number: 200620041080.6, to see shown in Figure 2ly, its main contents are as follows: it is made up of trim ring 1, back-up ring 2, bracing ring 3, load screw 4, loading force sensor 5; The main ball bearing that adopts loads, and has determined that its applicable situation is low speed, short life, and can't carry out dynamic load to the experiment bearing, promptly can not change loading frequency.Therefore, this invention is not suitable for the hypervelocity rotating machinery of gas bearing supporting, and can't realize dynamic load.
Summary of the invention
The present invention has overcome the deficiency of above-mentioned bearing loading experiment platform, proposes gas bearing-integrated experiment table of rotor-support-foundation system dynamic load.This experiment table has following characteristics:
(1) static loading force size is stable, variable, control easily, and can under the rotor high-speed operation, load (usually greater than 70,000 rev/mins).
(2) dynamic load in the time of can realizing that rotor moves under each rotating speed, the size of dynamic load power and changeable frequency have certain tuning range.
(3) guarantee that each gas bearing of experiment table is in state entirely on the center.
(4) simple for structure, the easy accessibility, repeatable strong of experiment table itself.
For achieving the above object, technical solution of the present invention is:
Gas bearing-integrated the experiment table of rotor-support-foundation system dynamic load comprises hypervelocity gas bearing support module, integrated base support structure, labyrinth-air film associating hermetically-sealed construction, quiet, dynamic load mechanism and five parts of rotor-support-foundation system.
That hypervelocity gas bearing support module comprises is radial gas bearing provided, thrust gas bearing and radially-thrust associating gas bearing; Radial gas bearing provided, radially-thrust associating gas bearing is as measured bearing.
Integrated base support structure comprises integrated casing, boss and cover plate, integrated casing is a cylindrical shape, the centre is provided with boss, offer square hole in the middle of the integrated casing, be used to lay watt load bearings of to incline, also near thrust gas bearing, offer two through holes on the integrated casing, be used to lay sensor probe; Radial gas bearing provided, radially-the axial right alignment of thrust associating gas bearing realizes by the outside surface of these two bearings and the inside surface of integrated casing; Radially-the radial parallel degree of thrust associating gas bearing, thrust gas bearing realizes by the depth of parallelism of these two bearing sidewalls and boss two sides; Integrated base support structure is owing to simple in structure, machining precision guarantee easily, so the reliability height, working stability, favorable repeatability.
Labyrinth-air film associating hermetically-sealed construction comprises sealed support, labyrinth seal ring and air film sealing ring, the labyrinth seal ring inner surface is offered maze trough, the gas film sealing ring inner surface is offered the pump groove, gas film sealing adopts the extraneous gases at high pressure air feed after step-down, form air film during the rotating shaft rotation between rotating shaft and air film sealing ring, it is that the gas of realizing this air film flows to the labyrinth seal ring outlet by the outlet of gas film sealing ring that the pump groove is offered direction; The sealing principle of labyrinth-air film associating hermetically-sealed construction is to reduce most of gaseous tension by labyrinth seal ring, and the gas by the isolated labyrinth seal outlet of gas film sealing ring spreads to the gas film sealing direction again.
Quiet, dynamic load mechanism comprises that main backstop, vibrator, adjustable free beam, free beam load adjustment bolt, loading spring, power-frequency sensor, watt load bearings of can inclining; Adjustable free beam is a rectangular block, and its thickness is 2-5mm, and its two ends have connecting hole, and two right cylinders of welding on the lower plane are gone up at the place in the middle of the adjustable free beam; Watt load bearings of can inclining mainly is made up of antifriction alloy, supporting mass, air vent, air supply channel and sealing rubber ring, be 3 tile fragments can incline the tile fragments in watt gas bearing of watt gas bearing or 4 tile fragments that can incline, watt load bearings of can inclining can be around 360 ° of dynamic swings of sealing rubber ring elastic support, promptly dynamically finely tune the direction of loading force by the tile fragment that can swing, the direction that guarantees loading force makes loading force stable, reliable by the axle center; Action principle quiet, dynamic load mechanism is to regulate loading frequency by vibrator, size by adjustable free beam, loading spring adjusting loading force, adopt the coupling stiffness effect of crooked free beam and spring, realize the reliable and stable output of loading force, power-frequency sensor is realized the measurement of loading force size, frequency, watt load bearings of can inclining makes loading force stablize, be applied in the rotating shaft reliably, and rotating shaft is given measured bearing with size, the Frequency Transfer of loading force again.
Rotor-support-foundation system comprises spiral case, drives turbine, thrust button and rotating shaft, rotating shaft and thrust button are integrative-structures, thrust button is positioned at rotating shaft 1/5 position, and corresponding labyrinth seal ring position is offered maze trough in the rotating shaft, offers the pod apertures of 2-8 symmetric arrangement on rotating shaft and the thrust button intersection circumference; The rotating shaft of the gas-powered rotor-support-foundation system that turbine is induced by spiral case, pod apertures is used for the gaseous tension of balance thrust button both sides, makes the rotating shaft axially-movable more stable.
Annexation between the integrated experiment table various piece of gas bearing-rotor-support-foundation system dynamic load, each parts is:
Rotor-support-foundation system is by the supporting of hypervelocity gas bearing support module, by labyrinth-air film associating hermetically-sealed construction realization sealing, hypervelocity gas bearing support module, labyrinth-air film associating hermetically-sealed construction install and fix on the integrated base support structure, quiet, dynamic load mechanism is connected with integrated base support structure, realizes the value-added tax function of experiment table.
Place respectively radially in the rotating shaft of thrust button both sides-thrust associating gas bearing, thrust gas bearing, do not have an end of thrust button to place radial gas bearing provided in the rotating shaft; Radially-thrust associating gas bearing, thrust gas bearing and radial gas bearing provided being positioned in the integrated casing, radial gas bearing provided, radially-outer round surface of thrust associating gas bearing and the inside surface of integrated casing fit, radially-sidewall of thrust associating gas bearing, a sidewall of thrust gas bearing fit with two sidewalls of boss respectively; Cover plate is installed on integrated casing right side, sealed support is installed in integrated casing left side, radially-and thrust associating gas bearing left side installation gas film sealing ring, labyrinth seal ring is installed in gas film sealing ring left side, and the outer round surface of labyrinth seal ring and air film sealing ring and sealed support inside surface are fitted; Turbine is installed in the end of rotating shaft, the outside spiral case of installing of turbine; The below of main backstop is used for fixing integrated casing, vibrator is installed on the upper beam, load the adjustment bolt and regulate adjustable free beam by free beam on two sidewalls, adjustable free beam is bent downwardly and compresses loading spring, the holddown spring lower end connects power-frequency sensor, power-frequency sensor lower end connects watt load bearings of can inclining, watt load bearings of can inclining is passed the square hole of offering on the integrated casing and is positioned over rotating shaft top, be positioned at radial gas bearing provided, radially-thrust associating gas bearing centre position;
Turbine, spiral case, sealed support, labyrinth seal ring, gas film sealing ring, integrated casing, radially-thrust associating gas bearing, thrust gas bearing, radial gas bearing provided, boss, baffle plate, watt load bearings of can inclining and rotating shaft are coaxial; Can incline the gap of watt load bearings and rotating shaft at 15-100um, radially-and end play between thrust associating gas bearing, thrust gas bearing and the thrust button is 50um, and radial gas bearing provided, radially-thrust associating gas bearing and rotating shaft radial play are 20-60um;
Described gas bearing-integrated the experiment table of rotor-support-foundation system dynamic load, its described hypervelocity gas bearing supporting is provided with the bearing removal frock, is used for thrust gas bearing and radial gas bearing provided dismounting; The bearing removal frock is made up of screw rod, adjustment nut, positioning disk, folding pawl, the rotating shaft of folding pawl, folding pawl shaft collar; Attacked screw thread on the screw rod, the one end is installed folding pawl shaft collar, offers folding pawl square groove on the folding pawl shaft collar and the rotating shaft of folding pawl is installed, the folding pawl is installed in the rotating shaft of folding pawl, the screw rod other end is put on positioning disk, and nut is adjusted in rotation, and positioning disk is moved vertically; The folding pawl has 2-6, and an end that is connected with the rotating shaft of folding pawl is a semi-circular structure, and the folding pawl can open automatically when screw rod rotates.Its principle of work is: closed folding pawl, with the folding pawl of bearing removal frock via the inside surface of bearing demolition inboard through bearing demolition, rotating screw bolt opens the folding pawl, pulling out screw rod makes the folding dog clutch live the bearing demolition interior sidewall surface, by adjusting nut positioning disk is pressed to integrated casing, the folding pawl just can be pulled out bearing demolition.
Described gas bearing-integrated the experiment table of rotor-support-foundation system dynamic load, its described adjustable free beam can also adopt discontinuous variable cross section free beam to replace; Discontinuous variable cross section free beam is made up of cuboid, groove, connecting hole, right cylinder; The two ends of cuboid respectively have a groove, and groove length is 1: 10 to 1: 20 with the ratio of cuboid length, and the aspect ratio in two cross sections of cuboid is 10: 1 to 4: 1; The cuboid two ends have connecting hole, and two right cylinders of welding on the lower plane are gone up at the place in the middle of the cuboid, are used to connect vibrator and loading spring; Discontinuous variable cross section free beam is by regulating the supporting power at two ends, obtain the effect of Euler's depression bar, the loading spring that install this discontinuous variable cross section free beam and below constitutes the low frequency supporting system together, whole natural frequency quiet, dynamic load mechanism is reduced to below the 5Hz, thereby the resonance problem that has brought when having avoided being close of vibrator frequency and quiet, dynamic load mechanism natural frequency, make dynamic load more stable, measurement result is more accurate.
Gas bearing of the present invention-integrated the experiment table of rotor-support-foundation system dynamic load, advantage is:
(1) experiment table is simple for structure, exquisite, by integrated base support structure guaranteed radial gas bearing provided, radially-thrust associating gas bearing, the axial right alignment of 3 bearings of thrust gas bearing, radial parallel degree.Adopt the bearing removal frock to make things convenient for dismounting, the installation of experiment table, and effectively guaranteed the repeatability of experiment table.
(2) adopt quiet, dynamic load mechanism to realize that the stable, reliable of static loading force size changes, and realized controlled, the scalable of dynamic load power size, frequency, realized the axle center that loading force dynamically passed and followed the tracks of rotating shaft by watt load bearings of can inclining; When quiet, dynamic load mechanism natural frequency and vibrator frequency ratio near the time, can also be quiet, the natural frequency of dynamic load mechanism is to 5Hz by discontinuous variable cross section free beam reduction.
(3) by labyrinth-air film associating hermetically-sealed construction, realized driving completely cutting off between turbine working gas and each gas bearing working gas or the atmosphere, this for gas medium be flammable explosive gas, toxic gas, when easily producing chemical reaction gas, high-temperature gas, cryogenic gas etc., sealing effectiveness is more remarkable.
Description of drawings
Fig. 1 is contrast patent " radially dynamical and static pressure gas bearing test platform " structural representation.
Fig. 2 is contrast patent " bearing charger " structural representation.
Fig. 3 is the gas bearing-integrated experiment table of rotor-support-foundation system dynamic load principal section synoptic diagram.
Fig. 4 is watt load bearings structural representation that can incline.
Fig. 5 is a bearing removal tool structure synoptic diagram.
Fig. 6 is non-continuous variable cross section simple beam structure synoptic diagram.
Among the figure:
01 spiral case; 02 drives turbine; 03 sealed support; 04 labyrinth seal ring; 05 gas film sealing ring; 06 thrust button; 07 rotating shaft; 08 integrated casing; 09 boss; 010 main backstop; 011 cover plate; 012 is radial gas bearing provided; 013 free beam loads adjusts bolt; The 014 watt load bearings of can inclining; 015 power-frequency sensor; 016 loading spring; 017 vibrator; 018 adjustable free beam; 019 thrust gas bearing; 020 radially-thrust associating gas bearing.
014-1 to 014-5 is the structure building block of watt load bearings of can inclining, wherein: the 014-1 antifriction alloy; The 014-2 supporting mass; The 014-3 air vent; The 014-4 air supply channel; The 014-5 sealing rubber ring.
018-1 to 018-4 is discontinuous variable cross section simple beam structure building block, wherein: the 018-1 cuboid; The 018-2 groove; The 018-3 connecting hole; The 018-4 right cylinder.
021-1 to 021-5 is a bearing removal tool structure building block, wherein: the 021-1 screw rod; 021-2 adjusts nut; The 021-3 positioning disk; 021-4 folding pawl; The rotating shaft of 021-5 folding pawl; 021-6 folding pawl shaft collar.
Embodiment
Fig. 3 is the integrated experiment table structural representation of gas bearing of the present invention-rotor-support-foundation system dynamic load; Fig. 4 is watt load bearings structural representation that can incline; Fig. 5 is a bearing removal tool structure synoptic diagram.As shown in the figure, gas bearing of the present invention-integrated experiment table of rotor-support-foundation system dynamic load is by spiral case 01, drive turbine 02, sealed support 03, labyrinth seal ring 04, gas film sealing ring 05, thrust button 06, rotating shaft 07, integrated casing 08, boss 09, main backstop 010, cover plate 011, radial gas bearing provided 012, free beam loads adjusts bolt 013, watt load bearings 014 of can inclining, power-frequency sensor 015, loading spring 016, vibrator 017, adjustable free beam 018, thrust gas bearing 019, radially-thrust associating gas bearing 020, bearing removal frock 021 composition such as grade; Wherein, watt load bearings 014 of can inclining is made up of antifriction alloy 014-1, supporting mass 014-2, air vent 014-3, air supply channel 014-4, sealing rubber ring 014-5 etc.; Bearing removal frock 021 is made up of screw rod 021-1, adjustment nut 021-2, positioning disk 021-3, folding pawl 021-4, folding pawl rotating shaft 021-5, folding pawl shaft collar 021-6 etc.; Adjustable free beam 018 can also be replaced by discontinuous variable cross section free beam, and discontinuous variable cross section free beam is by cuboid 018-1; Groove 018-2; Connecting hole 018-3; Right cylinder 018-4 forms.
In the experiment table installation process, earlier integrated casing 08 is installed on the main backstop 010, radial gas bearing provided 012, thrust gas bearing 019 is installed then; Rotating shaft 07 is installed, behind the adjustment axial location sealed support 03 is installed on the integrated casing 08, gas film sealing ring 05, labyrinth seal ring 04 are installed respectively afterwards; In rotating shaft 07, install and drive turbine 02, spiral case 01 is installed on sealed support 03; At integrated casing 08 1 ends cover plate 011 is installed; Vibrator 017, adjustable free beam 018 are installed respectively on main backstop 010, and are adjusted the vertical position; Loading spring 016, power-frequency sensor 015, watt load bearings 014 of can inclining are installed below adjustable free beam 018, and adjust the free beam loading adjustment bolt 013 at adjustable free beam 018 two ends, reach suitable exciting force; The air supply channel of watt load bearings 014 of can inclining afterwards, radial gas bearing provided 012, thrust gas bearing 019, radially-air supply hose of thrust associating gas bearing 020, spiral case 01 is connected respectively on the source of the gas, gas film sealing ring 05 air supply hose is connected on the origin after by the reduction valve step-down, has promptly finished the installation of whole experiment table.
When carrying out the experiment of bearing dynamic load, give watt load bearings 014 air feed that to incline earlier, make the rotating shaft and watt load bearings 014 of can inclining suspend, the free beam of adjusting adjustable free beam 018 two ends loads adjusts bolt 013, by the size of power-frequency sensor 015 acquisition loading force, till reaching requirement; Adjust vibrator 017 exciting head then and adjust the distance of adjustable free beam 018 upper surface, and adjust the frequency of vibrator 017, can measure after reaching requirement.
In dismounting during experiment table, according to above-mentioned opposite order, dismounting radially-during thrust associating gas bearing 020, need knock gently vertically the tail end (end that non-turbine is installed) of rotating shaft 07, will radially-thrust unites gas bearing 020 and eject; Rotating shaft 07 can be taken out afterwards; In dismounting thrust gas bearing 019 and radial gas bearing provided 012 o'clock, need to use bearing removal frock 021, that is: closed folding pawl 021-4, with it via the inside surface of bearing demolition inboard through bearing demolition, rotating screw bolt 021-1 opens folding pawl 021-4, pull out screw rod 021-1 and make folding pawl 021-4 fasten the bearing demolition interior sidewall surface, by adjusting nut 021-2 positioning disk 021-3 is pressed to integrated casing 08, folding pawl 021-4 just can pull out bearing demolition.
Claims (3)
1. gas bearing-integrated experiment table of rotor-support-foundation system dynamic load comprises hypervelocity gas bearing support module, integrated base support structure, labyrinth-air film associating hermetically-sealed construction, quiet, dynamic load mechanism and five parts of rotor-support-foundation system; It is characterized in that:
That hypervelocity gas bearing support module comprises is radial gas bearing provided, thrust gas bearing and radially-thrust associating gas bearing; Radial gas bearing provided, radially-thrust associating gas bearing is as measured bearing;
Integrated base support structure comprises integrated casing, boss and cover plate, integrated casing is a cylindrical shape, the centre is provided with boss, offer in the middle of the integrated casing and be used to lay the square hole of watt load bearings of to incline, also near thrust gas bearing, offer two through holes that are used to lay sensor probe on the integrated casing;
Labyrinth-air film associating hermetically-sealed construction comprises sealed support, labyrinth seal ring and air film sealing ring, the labyrinth seal ring inner surface is offered maze trough, the gas film sealing ring inner surface is offered the pump groove, gas film sealing adopts the extraneous gases at high pressure air feed after step-down, form air film during the rotating shaft rotation between rotating shaft and air film sealing ring, it is that the gas of realizing this air film flows to the labyrinth seal ring outlet by the outlet of gas film sealing ring that the pump groove is offered direction;
Quiet, dynamic load mechanism comprises that main backstop, vibrator, adjustable free beam, free beam load adjustment bolt, loading spring, power-frequency sensor, watt load bearings of can inclining; Adjustable free beam is a rectangular block, and its thickness is 2-5mm, and its two ends have connecting hole, and two right cylinders of welding on the lower plane are gone up at the place in the middle of the adjustable free beam; Watt load bearings of can inclining mainly is made up of antifriction alloy, supporting mass, air vent, air supply channel and sealing rubber ring, be 3 tile fragments can incline the tile fragments in watt gas bearing of watt gas bearing or 4 tile fragments that can incline, watt load bearings of can inclining is around 360 ° of dynamic swings of sealing rubber ring elastic support;
Rotor-support-foundation system comprises spiral case, drives turbine, thrust button and rotating shaft, rotating shaft and thrust button are integrative-structures, thrust button is positioned at rotating shaft 1/5 position, and corresponding labyrinth seal ring position is offered maze trough in the rotating shaft, offers the pod apertures of 2-8 symmetric arrangement on rotating shaft and the thrust button intersection circumference;
Annexation between gas bearing-each parts of the integrated experiment table of rotor-support-foundation system dynamic load is as follows:
Rotor-support-foundation system is by the supporting of hypervelocity gas bearing support module, by labyrinth-air film associating hermetically-sealed construction realization sealing, hypervelocity gas bearing support module, labyrinth-air film associating hermetically-sealed construction install and fix on the integrated base support structure, quiet, dynamic load mechanism is connected with integrated base support structure, realizes the value-added tax function of experiment table;
Place respectively radially in the rotating shaft of thrust button both sides-thrust associating gas bearing, thrust gas bearing, do not have an end of thrust button to place radial gas bearing provided in the rotating shaft; Radially-thrust associating gas bearing, thrust gas bearing and radial gas bearing provided being positioned in the integrated casing, radial gas bearing provided, radially-outer round surface of thrust associating gas bearing and the inside surface of integrated casing fit, radially-sidewall of thrust associating gas bearing, a sidewall of thrust gas bearing fit with two sidewalls of boss respectively; Cover plate is installed on integrated casing right side, sealed support is installed in integrated casing left side, radially-and thrust associating gas bearing left side installation gas film sealing ring, labyrinth seal ring is installed in gas film sealing ring left side, and the outer round surface of labyrinth seal ring and air film sealing ring and sealed support inside surface are fitted; Turbine is installed in the end of rotating shaft, the outside spiral case of installing of turbine; The below of main backstop is used for fixing integrated casing, vibrator is installed on the upper beam, load the adjustment bolt and regulate adjustable free beam by free beam on two sidewalls, adjustable free beam is bent downwardly and compresses loading spring, the holddown spring lower end connects power-frequency sensor, power-frequency sensor lower end connects watt load bearings of can inclining, watt load bearings of can inclining is passed the square hole of offering on the integrated casing and is positioned over rotating shaft top, be positioned at radial gas bearing provided, radially-thrust associating gas bearing centre position;
Turbine, spiral case, sealed support, labyrinth seal ring, gas film sealing ring, integrated casing, radially-thrust associating gas bearing, thrust gas bearing, radial gas bearing provided, boss, baffle plate, watt load bearings of can inclining and rotating shaft are coaxial; Can incline the gap of watt load bearings and rotating shaft at 15-100um, radially-and end play between thrust associating gas bearing, thrust gas bearing and the thrust button is 50um, and radial gas bearing provided, radially-thrust associating gas bearing and rotating shaft radial play are 20-60um.
2. the gas bearing as claimed in claim 1-integrated experiment table of rotor-support-foundation system dynamic load, its feature also is, hypervelocity gas bearing support module is provided with the bearing removal frock, and this bearing removal frock is made up of screw rod, adjustment nut, positioning disk, folding pawl, the rotating shaft of folding pawl, folding pawl shaft collar; Attacked screw thread on the screw rod, the one end is installed folding pawl shaft collar, offers folding pawl square groove on the folding pawl shaft collar and the rotating shaft of folding pawl is installed, and the folding pawl is installed in the rotating shaft of folding pawl; The screw rod other end is put on positioning disk, and nut is adjusted in rotation, and positioning disk is moved vertically; The folding pawl has 2-6, and an end that is connected with the rotating shaft of folding pawl is a semi-circular structure, and the folding pawl opens automatically when screw rod rotates.
3. the gas bearing as claimed in claim 1-integrated experiment table of rotor-support-foundation system dynamic load, its feature also are, its described adjustable free beam adopts discontinuous variable cross section free beam to replace; Discontinuous variable cross section free beam is made up of cuboid, groove, connecting hole, right cylinder; The two ends of cuboid respectively have a stepped groove, and groove length is 1: 10 to 1: 20 with the ratio of cuboid length, and the aspect ratio in two cross sections of cuboid is 10: 1 to 4: 1; The cuboid two ends have connecting hole, and two right cylinders of welding on the lower plane are gone up at the place in the middle of the cuboid; Discontinuous variable cross section free beam obtains the effect of Euler's depression bar by regulating the supporting power at two ends, and the loading spring that install this discontinuous variable cross section free beam and below constitutes the low frequency supporting system together.
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| CN2010105950483A CN102121875B (en) | 2010-12-17 | 2010-12-17 | Dynamic loading comprehensive experimental table for gas bearing-rotor system |
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| CN2010105950483A CN102121875B (en) | 2010-12-17 | 2010-12-17 | Dynamic loading comprehensive experimental table for gas bearing-rotor system |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2886546Y (en) * | 2006-04-14 | 2007-04-04 | 中国科学院上海技术物理研究所 | Bearing loading device |
| CN201247147Y (en) * | 2008-09-01 | 2009-05-27 | 洛阳工铭机电设备有限公司 | Mechanism for supporting and loading cantilever of helicopter inclinometer thin-wall bearing detection device |
| CN101915662A (en) * | 2010-07-09 | 2010-12-15 | 大连海事大学 | Bearing-rotor system loading test device and method |
| CN201909714U (en) * | 2010-12-17 | 2011-07-27 | 大连理工大学 | Comprehensive dynamic loading test platform for gas bearing-rotor systems |
-
2010
- 2010-12-17 CN CN2010105950483A patent/CN102121875B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2886546Y (en) * | 2006-04-14 | 2007-04-04 | 中国科学院上海技术物理研究所 | Bearing loading device |
| CN201247147Y (en) * | 2008-09-01 | 2009-05-27 | 洛阳工铭机电设备有限公司 | Mechanism for supporting and loading cantilever of helicopter inclinometer thin-wall bearing detection device |
| CN101915662A (en) * | 2010-07-09 | 2010-12-15 | 大连海事大学 | Bearing-rotor system loading test device and method |
| CN201909714U (en) * | 2010-12-17 | 2011-07-27 | 大连理工大学 | Comprehensive dynamic loading test platform for gas bearing-rotor systems |
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| CN114001960B (en) * | 2021-10-29 | 2023-12-12 | 浙江申发轴瓦股份有限公司 | Inverted tilting pad sliding bearing test bed |
| CN114001960A (en) * | 2021-10-29 | 2022-02-01 | 浙江申发轴瓦股份有限公司 | Inverted tilting pad sliding bearing test bed |
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