CN105889317A - Supporting structure used for measuring parameter influence characteristics of extrusion oil film damper - Google Patents
Supporting structure used for measuring parameter influence characteristics of extrusion oil film damper Download PDFInfo
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- CN105889317A CN105889317A CN201610255109.9A CN201610255109A CN105889317A CN 105889317 A CN105889317 A CN 105889317A CN 201610255109 A CN201610255109 A CN 201610255109A CN 105889317 A CN105889317 A CN 105889317A
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- Prior art keywords
- oil film
- bearing
- bearing block
- face
- damper
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- 238000001125 extrusion Methods 0.000 title abstract 5
- 230000033228 biological regulation Effects 0.000 claims description 30
- 241000446313 Lamella Species 0.000 claims description 5
- 238000013461 design Methods 0.000 claims description 5
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 230000004323 axial length Effects 0.000 claims description 2
- 238000013016 damping Methods 0.000 abstract description 26
- 241000555745 Sciuridae Species 0.000 abstract 2
- 239000003921 oil Substances 0.000 description 171
- 230000004044 response Effects 0.000 description 39
- 238000009434 installation Methods 0.000 description 10
- 238000000034 method Methods 0.000 description 6
- 230000006399 behavior Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 239000010687 lubricating oil Substances 0.000 description 5
- 238000011160 research Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000001629 suppression Effects 0.000 description 4
- 230000009286 beneficial effect Effects 0.000 description 3
- 239000000945 filler Substances 0.000 description 3
- 238000005259 measurement Methods 0.000 description 3
- 238000013475 authorization Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000013519 translation Methods 0.000 description 1
Classifications
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- 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
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
- F16F15/0237—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means involving 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
- F16F15/027—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means comprising control arrangements
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2230/00—Purpose; Design features
- F16F2230/0047—Measuring, indicating
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Support Of The Bearing (AREA)
Abstract
The invention discloses a supporting structure used for measuring parameter influence characteristics of an extrusion oil film damper. A supporting seat and an independent support are fixed to a base. A disc spring is located between the bottom surface of the independent support and the upper surface of the base. One end of a squirrel cage type elastic support is embedded in the supporting seat, and the other end face of the squirrel cage type elastic support is embedded in one end face of a bearing seat. An oil film outer ring is arranged on the bearing seat in a sleeving manner, and one end of the oil film outer ring is embedded in the inner surface of the independent support. An oil film layer is arranged between the bearing seat and the oil film outer ring. Position adjustment of the oil film outer ring is conducted through the independent support, and the purpose of changing parameters of the damper is achieved. After the supporting structure used for measuring the parameter influence characteristics of the extrusion oil film damper is introduced, under the condition that the parameters of a rotor are not changed, the structure parameters of the extrusion oil film damper are changed only in the manner of changing the independent support. The supporting structure is simple and convenient to install, and the influences of the structure parameters on the vibration damping performance of the extrusion oil film damper can be measured more accurately.
Description
Technical field
The present invention relates to rotor oscillation control field, be a kind of employing Parameter adjustable structure, can be used for measuring squeeze film resistance
The supporting structure of Buddhist nun's device parameter influencing characterisitic.
Background technology
The high-speed rotating machines such as aero-engine are frequently with flex rotor, and working rotor rotating speed often faces at single order or several rank
More than boundary's rotating speed.In the course of the work, as when startup, parking, variable working condition etc. rotor must Multiple through then out critical speed,
Cause rotor generation high vibration, even rotor-support-foundation system is produced harm, have a strong impact on the reliability of aero-engine.
Therefore, the vibration damping of rotor-support-foundation system becomes an important research field of rotor dynamics.
Squeeze film damper, as a kind of tradition damper mechanism, present Multiple Type aero-engine is applied.
Squeeze film damper Chang Youke occurs the bearing block of translation displacements to provide interior oil film face, static oil film outer shroud provide
Outer oil film face, dissipation energy during oil film in two oil film face top clearances, thus reach to reduce the effect of vibration.
The gap of squeeze film damper oil film, radius, length and initial eccentricity ratio (axle journal initial eccentricity and oil film
The ratio in gap) etc. factor, all damper vibration damping effect is played vital effect.When parameter is unreasonable,
Squeeze film damper even there will be the situation that vibration damping lost efficacy.Conventional damper structure provides inside and outside oil film face
Bearing block and oil film outer shroud are together connected on hold-down support, can not adjust therebetween position so that damper is grinding
Being inconvenient to during studying carefully regulate, parameter to be changed is necessary for again dismounting rotor and changes parts, it is impossible to accurately measure each heavy
Want parameter, also cannot accomplish unitary variant control, more cannot be by damper state optimization.Therefore, a kind of parameter of design can
The damper supporting structure individually regulating, be easily installed and measuring, the research to damper is significant.
In domestic and international Patents document and paper, the content about squeeze film damper focuses mostly in squeeze film damping
The structure of device and bearing method research.After its research contents essentially consists in installation squeeze film damper, rotor can reach and subtracts
The purpose shaken, does not considers that squeeze film damper can show different damping behaviors under different parameters.Need to change
Must first dismount rotor during damperparameters, change damper parts the most again, thus the concrete of damper cannot be measured
The parameter impact on damping behavior.When structure changes, it is impossible to determine the validity of damper vibration damping, structure side
The expansion of method is by a definite limitation.One is disclosed in the utility model patent that Authorization Notice No. is 204267598 U
Planting " the Zigzag type elastic bearing of band film damper ", this invention proposes a kind of supporting structure.This supporting structure is by oil
Film damper and Zigzag type elastic bearing compose in parallel, beneficially the use of small mechanical equipment.This invention is a kind of special
The fixed supporting structure being applied to GT25000 gas turbine, the structural parameters installing rear damper are non-adjustable, do not consider
The parameter impact on damper vibration damping performance.One is disclosed in the patent of Patent No. US 008167494 B2
" Squeeze-Film Damper Arrangement ", this invention proposes a kind of squeeze film damper structure, installs
The structural parameters of rear damper are non-adjustable, do not consider the parameter impact on damper vibration damping performance.
War roc is in paper " squeeze film damper is in the application solved in certain low-pressure compressor testpieces vibration problem "
(ISSN:1672-3147) have developed squeeze film damper based on certain h type engine h low-pressure compressor in, and devise
The squeeze film damper of three kinds of different oil clearances, analyzes its influencing characterisitic.Designed squeezing in this thesis work
Force feed film damperparameters cannot change after installation is complete, changes parameter every time and must again dismount rotor, and process is multiple
Miscellaneous, disassembly process may introduce in rotor-support-foundation system other influence factor, be unfavorable for that location parameter is to damper vibration damping
The impact of characteristic.Zhu Chang-sheng, Wang Xi-xuan is at paper " Vibration Control of Flexible Rotor
By Controlled Structure Parameters conical squeeze film damper " in propose one and can change
The squeeze film damper of bearing structure of oil clearance.This structure does not considers the parameter such as oil film length and initial eccentricity ratio
Impact, and be unfavorable for after rotor installation measure oil film parameter.
Summary of the invention
For overcoming present in prior art that parameter measurement non-adjustable, difficult, oil film outer shroud are independent, cannot single argument grind
The deficiency studied carefully, the present invention proposes a kind of supporting structure for measuring squeeze film damper parameter influencing characterisitic.
The present invention includes base, bearing, rotor cage type elastic support, bearing block, oil film outer shroud, independent floor support, dish
Shape spring and regulation bolt.Wherein:
Described bearing and independent floor support are each attached on described base, and make propping up with independent of described bearing centre bore
The center line of seat centre bore overlaps.Described disk spring is between the basal surface and base upper surface of independent floor support.Institute
The one end stating rotor cage type elastic support is inlaid in described bearing, and makes the end face of this rotor cage type elastic support with described
Prop up bearing interference fit；The end face of described rotor cage type elastic support is fixing with the inner surface of described bearing to be connected, described
Another end face of rotor cage type elastic support is embedded in an end face into bearing block, and makes this rotor cage type elastic support with described
Fixing connection between bearing block；Interference fit between described rotor cage type elastic support and bearing block.
Described oil film exterior ring cap is contained on described bearing block, and make that one end of this oil film outer shroud is embedded in into independent floor support interior
Surface；Oil lamella is had between bearing block and oil film outer shroud.
Bearing is arranged in described bearing block, and is realized this bearing by outer race nut and bearing inner ring nut
Location.Described rotating shaft loads the installing hole of described bearing, and makes one end of this rotating shaft load in described bearing.
When installing bearing, the outer shroud of this bearing is inlaid on the inner cylinder face of described bearing block, and makes outside this bearing
One end face of ring fits with the end face of described bearing block inner cylinder face one end rib；The outer shroud of bearing and bearing block it
Between interference fit.The inner ring sleeve of described bearing is contained in rotating shaft, and makes an end face of described bearing inner ring with described
The shaft shoulder end face of rotating shaft fits.Interference fit between inner ring and the rotating shaft of bearing.
The inner surface of described bearing block one end has rib, and the inner surface of this bearing block other end is for join with outer race nut
The flank closed；One end face of described bearing block has boss；This boss external diameter is identical with bearing block external diameter, internal diameter and institute
State rotor cage type elastic support less end flange external diameter identical, for coordinating with rotor cage type elastic support；Described boss
Height end flange thickness less with described rotor cage type elastic support is identical.Described bearing block other end have vertically to
The boss of outer extension, this boss external diameter is identical with bearing block external diameter；Thickness is satisfied to be deformed by oil film pressure rear boss part
Amount is less than one of percentage of oil clearance value；Highly meet bearing block width more than damper oil film design length.Described
Bearing block external cylindrical surface is smooth, is used for providing oil film face in damper；External peripheral surface has an axial length scale
Mark line, extends axially outwardly the end face of boss described in mark line " 0 " value correspondence.
Described outer race nut is by being threaded in the internal thread of described bearing block, on the internal thread of described bearing block
Presetting locking plate, the outer shroud of described bearing is compressed by an end face of described outer race nut, and uses locking plate to lock
Described outer race nut prevents from loosening.Described bearing inner ring nut by being threadably mounted in described rotating shaft, described turn
Presetting locking plate on the screw thread of axle, the inner ring of described bearing is compressed by an end face of described bearing inner ring nut, and makes
Lock described bearing inner ring nut with locking plate to prevent from loosening.
Described oil film outer shroud is inlaid on described independent floor support, makes the end face of described oil film outer shroud and described independent floor support mistake
It is full of cooperation.
Described disk spring is sleeved on regulation bolt, and by the bolt hole on underside being together arranged on described independent floor support,
Described disk spring is made to contact with the bottom surface of described independent floor support.Described independent floor support and described disk spring are by described
Regulation bolt is arranged on described base, and makes described disk spring and described base contacts.Described independent floor support can
On described base circumferentially moved.
There is base plate the lower end of described bearing, has on which floor plate for the screw affixed with base.Prop up bearing upper end
Inner surface has the groove of the one end fits with rotor cage type elastic support；There is through hole at the center of this groove, turn for installing
Axle.There is base plate the lower end of described independent floor support, has on which floor plate for the screw affixed with base.On independent floor support
The inner surface of end has the groove of the one end fits with oil film outer shroud；Through hole is had at the center of this groove.
In the present invention, described bearing and described independent floor support are installed on base；The one of described rotor cage type elastic support
Holding and be arranged in a bearing by bolt, the other end is embedded in bearing block by bolt；Described bearing is by " T "
Type groove bolt is installed on base；Described bearing block is arranged in rotating shaft by bearing；Described disk spring is positioned at solely
Vertical between bearing and base, by regulation bolt, independent floor support and disk spring are installed on base jointly；Described oil
Film outer shroud is embedded on independent floor support by bolt, and is sleeved on formed gap on bearing block, is used for filling lubricating oil.
The T-shape slot being distributed at described base upper surface, for installation bearing seat and independent floor support, plays fixed rotor
Effect.Described bearing seat inner diameter is equal to outer race external diameter at this rotor supports, it is possible to bearing interference fit used.
Described bearing block external cylindrical surface is smooth, is used for providing oil film face in damper.By the length scale mark of external peripheral surface
Note line, it is possible to measure the oil film length of damper.
Described oil film outer shroud is cylindrical shape, and one end is flanged, and flange embeds described independent floor support, by bolt with described
Independent floor support connects；There is oil filler point directly over the face of cylinder, by this hole, lubricating oil is injected oil clearance；Inner cylinder face light
Sliding, be used for providing damper outer oil film face, internal diameter size be described bearing block external diameter with twice oil clearance and；Add
Man-hour can process, by multiple oil clearances, the oil film outer shroud that multiple only internal diameter is different respectively.
Described disk spring rigidity is much larger than described rotor cage type elastic support rigidity, and disk spring diameter is slightly larger than described tune
The joint diameter of bolt.The screw thread of described regulation bolt is closely-pitched, and bolt is applicable to T-shape slot.
Having four bolt holes bottom described independent floor support, there is concave station this through hole bottom surface, is used for positioning described disk spring；
Prop up bearing to be fixed on described base by described regulation bolt with disk spring.Described independent floor support one side end face has recessed
Platform, and it is uniformly distributed bolt hole, this concave station external diameter is identical with the flange outer diameter of described oil film outer shroud, is used for embedding oil
Film outer shroud.Described independent floor support has axially extending bore, and aperture is more than bearing block external diameter.
The groundwork mode of the present invention is: install damper structure according to above-mentioned parts connected mode, and then at oil film
Oil clearance can be formed between outer shroud and bearing block.Prop up after bearing is fixed on base and the most no longer dismantle the parts of rotor own,
The most do not change rotor inherent parameters, change independent floor support state in this case, single argument control research can be realized and squeeze
Force feed film damperparameters affects, and reaches to measure the structural parameters purpose to damper vibration damping performance impact.By independence
Four regulation bolts of rest base can finely tune the angle of inclination between oil film outer shroud and bearing block and relative position, real
Now regulation oil film initial eccentricity ratio, and then measure the impact of initial eccentricity comparison damper vibration damping performance；At the beginning of measurement oil film
During beginning eccentricity ratio, clearance gauge be can be used directly and measure the oil film distribution of a week, measure in multiple angle outside oil film outer shroud simultaneously
Footpath calculates this measuring point oil clearance with the distance of bearing block external diameter, can be missed after the result of comprehensive two kinds of measuring methods
The film distribution situation that difference is less, calculates the initial eccentricity ratio of oil film according to distribution situation.Independent floor support can be on base
It is adjusted axially relative to a bearing, by the position that oil film outer shroud edge is corresponding on bearing block external cylindrical surface graduation mark
Put, the oil film length of this installation situation bottombearing damper can be read, now it should be noted that record the distribution situation of oil clearance,
And ensure that under each length, distribution situation is identical, and then measure the impact on damper vibration damping performance of the oil film length.Solely
Change the oil film outer shroud that internal diameter is different on vertical bearing, now it should be noted that record oil film length, and ensure that oil film length is constant,
Ensure that oil clearance is uniformly distributed simultaneously, and then measure the oil clearance impact on damper vibration damping performance.
The technical solution adopted in the present invention is, oil film outer shroud non-adjustable for existing squeeze film damper structural parameters
Independently, it is not unfavorable for measuring structural parameters to problems such as squeeze film damper damping behavior impacts.Introducing is used for measuring
After the supporting structure of squeeze film damper parameter influencing characterisitic, only can pass through in the case of not changing rotor parameter
The mode changing independent floor support changes the structural parameters of squeeze film damper.Present configuration is simple, easy for installation,
Can more accurately measure the structural parameters impact on squeeze film damper damping property.
After the supporting structure that the application present invention proposes, determine oil film length and squeeze film damper is subtracted by oil clearance
The impact of characteristic of shaking, can be to calculate the dynamics with squeeze film damper rotor to provide experimental data reference,
During for designing squeeze film damper, the selection to oil film length and oil clearance lays the foundation.By applying institute of the present invention
The structure proposed, determines different oil film initial eccentricity than the damping behavior of lower squeeze film damper, has obtained oil film
The initial eccentricity comparison far-reaching conclusion of squeeze film damper damping behavior, to the design of squeeze film damper and
Application has guiding significance.Therefore, supporting structure proposed by the invention convenient can measure extruding oil exactly
Film damperparameters influencing characterisitic, lays the foundation for experimental study squeeze film damper.
Accompanying drawing explanation
Accompanying drawing 1 is the structural representation of the present invention.
Fig. 2 is the connection diagram of independent floor support and base.
Fig. 3 is the structural representation of bearing block, and wherein Fig. 3 a is front view, and Fig. 3 b is left view.
Fig. 4 is the bearing block structure axonometric drawing with oil film length scale, and wherein Fig. 4 a is the axonometric drawing of one end, figure
4b is the axonometric drawing of the other end.
Fig. 5 is the flexibly mounted structural representation of mouse cage.
Fig. 6 be mouse cage elastic bearing with bearing block coordinate schematic diagram.
Fig. 7 is the position view of oil lamella.
Fig. 8 is squeeze film damper damper oil clearance effectiveness in vibration suppression when being 0.16mm under difference oil film length
Schematic diagram.
Fig. 9 be oil clearance be 0.16mm, oil film a length of 11mm time squeeze film damper effectiveness in vibration suppression show
It is intended to.
Figure 10 be oil clearance be 0.20mm, oil film a length of 11mm time squeeze film damper effectiveness in vibration suppression show
It is intended to.
Figure 11 is that rotor parameter is constant, the effectiveness in vibration suppression schematic diagram of squeeze film damper during oil film uniformity difference.
In figure:
1. a bearing；2. rotor cage type elastic support；3. bearing block；4. oil film outer shroud；5. independent floor support；6. outside bearing
Ring nut；7. bearing inner ring nut；8. rotating shaft；9. bearing；10. regulation bolt；11. nuts；12. disk springs；
13. bases；14. oil film length scale；15. locking plate grooves；16. oil lamellas；Vibration during the 17. a length of 0mm of oil film rings
Answer curve；Vibration response curve during the 18. a length of 8.07mm of oil film；Vibration during the 19. a length of 11.90mm of oil film
Response curve；Vibration response curve during the 20. a length of 13.86mm of oil film；During the 21. a length of 15.27mm of oil film
Vibration response curve；Vibration response curve during the 22. a length of 17.30mm of oil film；The 23. a length of 20.00mm of oil film
Time vibration response curve；Vibration response curve during 24. undamped device；25. oil clearances are vibration during 0.16mm
Response curve；26. oil clearances are vibration response curve during 0.20mm；When 27. oil film initial eccentricity ratios are 0.06
Vibration response curve；28. oil film initial eccentricity ratios are vibration response curve when 0.25；29. oil film initial eccentricity ratios
It it is vibration response curve when 0.56；30. oil film initial eccentricity ratios are vibration response curve when 0.69；31. oil films
Initial eccentricity ratio is vibration response curve when 0.75；32. oil film initial eccentricity ratios are vibration response curve when 0.88；
33. oil film initial eccentricity ratios are vibration response curve when 1.00.
Detailed description of the invention
The present embodiment is a kind of supporting structure for measuring squeeze film damper parameter influencing characterisitic, the end of including
Seat 13, bearing 1, rotor cage type elastic support 2, bearing block 3, oil film outer shroud 4, independent floor support 5, disk spring
12 and regulation bolt 10.Wherein:
Described bearing 1 and independent floor support 5 are all fixed on described base with regulation bolt 10 respectively by T-shape slot
On 13, and fastened by nut 11.The center line with independent floor support centre bore of described bearing centre bore overlaps.
Disk spring 12 is laid between the basal surface and base upper surface of described independent floor support.
One end of described rotor cage type elastic support 2 is inlaid in described bearing 1, and makes this rotor cage type elastic support 2
End face and described bearing 1 interference fit；The end face of described rotor cage type elastic support 2 is interior with described bearing 1
It is bolted between surface.Described another end face of rotor cage type elastic support 2 is embedded in into described bearing block 3
Individual end face, and connected fixing between described rotor cage type elastic support 2 and described bearing block 3 by bolt；Described mouse
Interference fit between cage elastic bearing and bearing block.Bearing 9 is arranged in described bearing block, and passes through outer race
Nut 6 and bearing inner ring nut 7 realize the location to this bearing.Described rotating shaft 8 loads the installation of described bearing 1
Hole, and make one end of this rotating shaft load in described bearing 9.One end of described oil film outer shroud 4 is embedded in into independent floor support 5
Inner surface, and be sleeved on the excircle of bearing block 3；It it is matched in clearance between this bearing block and oil film outer shroud.
Described bearing seat inner diameter is equal to outer race external diameter at this rotor supports, it is possible to described bearing 9 interference fit.
There is rib described bearing block inner cylinder face one end, is used for positioning outer race；In the inner cylinder face other end has diameter to be more than
The internal thread in footpath, with the locking plate groove 15 of escape and T-shape, is used for installing described outer race nut 6.Described
One end face of bearing block has boss, and this boss external diameter is identical with bearing block external diameter；Internal diameter and described rotor cage type elastic support
Less end flange external diameter is identical, and for coordinating with rotor cage type elastic support, the two is bolted；Height and institute
State rotor cage type elastic support less end flange thickness identical.Described bearing block other end has and extends axially outwardly
Boss, this boss external diameter is identical with bearing block external diameter；Thickness meets by oil film pressure rear boss part deflection less than oil
One of percentage of intermembrane space value；Highly meet bearing block width more than damper oil film design length.Outside described bearing block
The face of cylinder is smooth, is used for providing oil film face in damper；External peripheral surface has an oil film length scale in the horizontal direction
14, extend axially outwardly the end face of boss described in mark line " 0 " the value correspondence of this oil film length scale, be used for measuring
The oil film length of damper.
When installing described bearing 9, the outer shroud of this bearing is inlaid on the inner cylinder face of described bearing block 3, and makes
One end face of this outer race fits with the end face of described bearing block inner cylinder face one end rib；The outer shroud of bearing with
Interference fit between bearing block.The inner ring sleeve of described bearing is contained in rotating shaft 8, and makes the one of described bearing 9 inner ring
Individual end face fits with the shaft shoulder end face of described rotating shaft 8.Interference fit between inner ring and the rotating shaft of bearing.
Described rotating shaft 8 is arranged on described bearing block 3 by described bearing 9, and makes inner ring and the outer shroud of bearing 9
Relative position deviation is less than using allowed band.Described outer race nut 6 is by being threaded into described bearing block 3
Internal thread in, the internal thread of described bearing block 3 presets locking plate, an end face of described outer race nut 6
The outer shroud of described bearing 9 is compressed, and uses the locking plate described outer race nut 6 of locking to prevent from loosening.Described bearing
Inner ring nut 7, by being threadably mounted in described rotating shaft 8, the screw thread of described rotating shaft 3 presets locking plate, described axle
The inner ring of described bearing 9 is compressed by the end face holding inner ring nut 7, and uses locking plate to lock described bearing inner ring spiral shell
Female 7 prevent from loosening.
Described oil film outer shroud 4 is inlaid on described independent floor support 5, makes the end face of described oil film outer shroud 4 and described independence
Bearing 5 is fitted, and its cooperation face is interference fit.Described disk spring 12 is sleeved on described regulation bolt 10, and
By on the bolt hole on underside being together arranged on described independent floor support 5, make described disk spring 12 and described independent floor support 5
Bottom surface contact.Described independent floor support 5 and described disk spring 12 are arranged on the described end by described regulation bolt 10
On seat 13, and described disk spring 12 is made to contact with described base 13.Described independent floor support 5 can be at described base
On 13 circumferentially moved.
Described oil film outer shroud 4 is sleeved on described bearing block 3, the inner surface of described oil film outer shroud 4 and described bearing block
Gap is had between the outer surface of 3, when injecting lubricating oil by the oil filler point of described oil film outer shroud 4 to damper, lubricating oil
Described oil lamella 16 can be formed in this gap.Described oil film outer shroud 4 carries out position adjustments by described independent floor support 5,
Reach to change the purpose of damperparameters.
There is base plate the lower end of described bearing 1, has on which floor plate for the screw affixed with base 13.Prop up bearing 1
The inner surface of upper end has the groove of the one end fits with rotor cage type elastic support 2；There is through hole at the center of this groove, use
In installing rotating shaft 8.
There is base plate the lower end of described independent floor support 5, has on which floor plate for the screw affixed with base 13.Independent
The inner surface of seat 5 upper ends has the groove of the one end fits with oil film outer shroud 4；Through hole is had at the center of this groove.
During assembling:
First, installation bearing seat part, the most first rotor is built.Concretely comprise the following steps: first by four T-shape slots
Insert with bolt in the T-shape slot of base, and a bearing is placed on base by four bolts；Horizontal positioned axle
Bearing, the inner cylinder face of heated mandrel bearing, then outer race is loaded, during loading, outer race to be guaranteed is not skewed；
In the locking plate groove of bearing block screw thread, place locking plate, screw in outer race nut and compress outer race, and lock with locking plate
Outer race nut；Use bolt that end face corresponding with bearing block for rotor cage type elastic support is connected fastening, re-use
The other end of rotor cage type elastic support is connected fastening with a bearing by bolt, notes guaranteeing oil film length scale line during installation
It is in the angle of easily observation, makes bearing block, rotor cage type elastic support and a bearing be connected；By bearing inner ring
On the corresponding cooperation face of press-in rotating shaft, and guarantee that bearing inner ring is not skewed；Again the bearing being connected is pushed to
Rotating shaft, makes rotating shaft penetrate bearing block, adjusts a seating position, it is ensured that bearing inner ring is located exactly on outer race and axle
To position in bearing uses allowed band；In the screw fastening film trap of rotating shaft, place locking plate, screw in bearing inner ring nut
Compress bearing inner ring, and lock bearing inner ring nut with locking plate；Finally use spring shim and nut screwing clamping foundation bolt,
Rest portion is fixed.
Secondly, independent floor support part is installed.Concretely comprise the following steps: first four regulation bolts are inserted the T-shape slot of base
In, then four disk springs are respectively penetrated regulation bolt and is placed on base；By independent floor support by four regulations
Bolt is positioned on disk spring；Finally by oil film outer shroud embed independent floor support, note during installation oil supplying hole in surface,
And use bolt that oil film outer shroud and independent floor support are connected fastening.
Finally, squeeze film damper is adjusted.Concretely comprise the following steps: independent floor support is pushed to a bearing direction, makes oil film
Outer shroud is inserted in bearing block；According to required oil film length, regulate separate support by the oil film length scale on bearing block
Axial location；Regulation bolt overlaps Upper gasket and nut, then fastening nut, makes nut and regulation bolt by dish
Spring compression also produces certain deformation；Clearance gauge is finally used to measure the oil clearance of a week between oil film outer shroud and bearing block,
Note during measurement making a record, by the moment of fine-tuning nut, change the relative angle of oil film outer shroud and bearing block, make
Oil clearance keeps uniformly for one week.
During work, by the oil filler point above oil film outer shroud, lubricating oil being injected squeeze film damper, squeeze film damps
Device just can play damping effect.
During regulation squeeze film damper length parameter, first measure and record the oil film uniformity situation of a week with clearance gauge,
Then unclamp regulation bolt, move axially independent floor support, carry out reading by the oil film length scale on bearing block, reach
Just tightening regulation bolt to desired value, and change nut moment, the uniformity situation making oil clearance is as before,
Just complete the independent change of length parameter, be beneficial to measure the impact on squeeze film damper performance of the oil film length.Right
In this example, first determine the rotor vibration response curve 17 when a length of 0mm of oil film, when i.e. damper does not works
The vibration response curve of rotor；Then by changing damper oil film length parameter, oil film is successively determined a length of
Vibration response curve 19 during a length of 11.90mm of the vibration response curve 18 during 8.07mm, oil film, oil film length
Long for the vibration response curve 21 when the vibration response curve 20 during 13.86mm, a length of 15.27mm of oil film, oil film
Degree is the vibration response curve 23 when the vibration response curve 22 during 17.30mm and a length of 20.00mm of oil film,
Vibration response curve 17 during the vibration response curve 0mm a length of with oil film of these six kinds of oil film length lower rotor parts is carried out
Contrast, can analyze the damping property of corresponding oil film length parameter bottombearing damper, and then determine oil film length parameter
Impact on damper vibration damping performance.
During regulation squeeze film damper oil clearance parameter, first record oil film length now, then measure also with clearance gauge
The record oil film uniformity situation of a week, then unclamps regulation bolt, is extracted out vertically by independent floor support, changes internal diameter
Different oil film outer shrouds, then independent floor support is pushed again, the oil film length before recovery, tighten regulation bolt and lead to
Overregulate the oil film uniformity before nut moment recovers, just complete the independent change of oil clearance parameter, be beneficial to survey
The impact on squeeze film damper performance of the stand oil intermembrane space.For this example, first determine rotor when undamped device
Vibration response curve 24, determining oil clearance the most respectively is the vibration response curve 25 during 0.16mm and oil film
Gap is the vibration response curve 26 during 0.20mm, by the vibration response curve of two kinds of oil clearance lower rotor parts with without hindrance
Vibration response curve 24 during Buddhist nun's device contrasts, and can analyze the damping of corresponding oil clearance parameter bottombearing damper
Can, and then determine the impact on damper vibration damping performance of the oil clearance parameter.
When the oil film initial eccentricity of regulation squeeze film damper is than parameter, changes the moment on regulation bolt, reduce power
Square can make to move on the oil film outer shroud 4 of respective direction, increases moment then contrary, and then changes oil film outer shroud 4 relative to axle
The relative position of bearing 3.When changing moment, the oil film distribution situation of a week, record oil are measured and recorded to attention clearance gauge
The situation of the film uniformity, just can complete the independent change of oil film initial eccentricity ratio, be beneficial to measure oil film initial eccentricity comparison
The impact of squeeze film damper performance.For this example, by changing the moment of regulation bolt, determine respectively and turn
Son oil film initial eccentricity than be vibration response curve 27 when 0.06, oil film initial eccentricity ratio be vibration when 0.25
Response curve 28, oil film initial eccentricity than be vibration response curve 29 when 0.56, oil film initial eccentricity ratio be 0.69
Time vibration response curve 30, oil film initial eccentricity is than being vibration response curve 31 when 0.75, oil film initial eccentricity
Than being the vibration response curve 32 when 0.88 and oil film initial eccentricity ratio is the vibration response curve 33 when 1.00,
These seven kinds of oil film initial eccentricities are contrasted than the vibratory response of lower rotor part, corresponding oil film initial eccentricity can be analyzed
The ratio damping property of parameter bottombearing damper, and then measure oil film initial eccentricity than the parameter impact on damper vibration damping performance.
Claims (7)
1. one kind for measuring the supporting structure of squeeze film damper parameter influencing characterisitic, it is characterised in that include base,
Prop up bearing, rotor cage type elastic support, bearing block, oil film outer shroud, independent floor support, disk spring and regulation bolt；
Wherein:
Described bearing and independent floor support are each attached on described base, and make described bearing centre bore and independent floor support
The center line of centre bore overlaps；Described disk spring is between the basal surface and base upper surface of independent floor support；Institute
The one end stating rotor cage type elastic support is inlaid in described bearing, and makes end face and the institute of this rotor cage type elastic support
State a bearing interference fit；The end face of described rotor cage type elastic support is fixing with the inner surface of described bearing to be connected,
Another end face of described rotor cage type elastic support is embedded in an end face into bearing block, and makes this rotor cage type elastic support
It is connected with fixing between described bearing block；Interference fit between described rotor cage type elastic support and bearing block；
Described oil film exterior ring cap is contained on described bearing block, and makes one end of this oil film outer shroud be embedded in the interior table into independent floor support
Face；Oil lamella is had between bearing block and oil film outer shroud；
Bearing is arranged in described bearing block, and realizes determining this bearing by outer race nut and bearing inner ring nut
Position；Described rotating shaft loads the installing hole of described bearing, and makes one end of this rotating shaft load in described bearing.
2. as claimed in claim 1 for measuring the supporting structure of squeeze film damper parameter influencing characterisitic, it is characterised in that
When installing bearing, the outer shroud of this bearing is inlaid on the inner cylinder face of described bearing block, and makes this outer race
The end face of an end face and described bearing block inner cylinder face one end rib fit；The outer shroud of bearing and bearing block it
Between interference fit；The inner ring sleeve of described bearing is contained in rotating shaft, and makes an end face and the institute of described bearing inner ring
The shaft shoulder end face stating rotating shaft fits；Interference fit between inner ring and the rotating shaft of bearing.
3. as claimed in claim 1 for measuring the supporting structure of squeeze film damper parameter influencing characterisitic, it is characterised in that
The inner surface of described bearing block one end has rib, and the inner surface of this bearing block other end is and outer race nut screw connection
Flank；One end face of described bearing block has boss；This boss external diameter is identical with bearing block external diameter, internal diameter and institute
State rotor cage type elastic support less end flange external diameter identical, for coordinating with rotor cage type elastic support；Described boss
Height end flange less with described rotor cage type elastic support thickness identical；Described bearing block other end has along axle
To outward extending boss, this boss external diameter is identical with bearing block external diameter；Thickness meets by oil film pressure rear boss portion
Divide one of deflection percentage less than oil clearance value；Highly meet bearing block width long more than the design of damper oil film
Degree；Described bearing block external cylindrical surface is smooth, is used for providing oil film face in damper；External peripheral surface has axial length
Spend scale mark line, described in mark line " 0 " value correspondence, extend axially outwardly the end face of boss.
4. as claimed in claim 1 for measuring the supporting structure of squeeze film damper parameter influencing characterisitic, it is characterised in that
Described outer race nut is by being threaded in the internal thread of described bearing block, pre-on the internal thread of described bearing block
Being equipped with locking plate, the outer shroud of described bearing is compressed by an end face of described outer race nut, and uses locking plate to lock
Described outer race nut prevents from loosening；Described bearing inner ring nut is by being threadably mounted in described rotating shaft, described
Presetting locking plate on the screw thread of rotating shaft, the inner ring of described bearing is compressed by an end face of described bearing inner ring nut,
And use the locking plate described bearing inner ring nut of locking to prevent from loosening.
5. as claimed in claim 1 for measuring the supporting structure of squeeze film damper parameter influencing characterisitic, it is characterised in that
Described oil film outer shroud is inlaid on described independent floor support, makes the end face of described oil film outer shroud and described independent floor support interference
Coordinate.
6. as claimed in claim 1 for measuring the supporting structure of squeeze film damper parameter influencing characterisitic, it is characterised in that
Described disk spring is sleeved on regulation bolt, and by the bolt hole on underside being together arranged on described independent floor support,
Described disk spring is made to contact with the bottom surface of described independent floor support；Described independent floor support and described disk spring pass through institute
State regulation bolt to be arranged on described base, and make described disk spring and described base contacts；Described independent floor support
Can be circumferentially moved on described base.
7. as claimed in claim 1 for measuring the supporting structure of squeeze film damper parameter influencing characterisitic, it is characterised in that
There is base plate the lower end of described bearing, has on which floor plate for the screw affixed with base；Prop up the interior of bearing upper end
There is the groove of the one end fits with rotor cage type elastic support on surface；There is through hole at the center of this groove, turn for installing
Axle；There is base plate the lower end of described independent floor support, has on which floor plate for the screw affixed with base；Independent floor support
The inner surface of upper end has the groove of the one end fits with oil film outer shroud；Through hole is had at the center of this groove.
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Cited By (7)
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| CN108279119A (en) * | 2017-12-28 | 2018-07-13 | 华中科技大学 | A kind of squeeze film damper performance test apparatus of Parameter adjustable |
| CN108506354A (en) * | 2017-02-28 | 2018-09-07 | 长沙泽骏装饰设计有限公司 | A kind of bearing block |
| CN108506353A (en) * | 2017-02-28 | 2018-09-07 | 长沙泽骏装饰设计有限公司 | A kind of adjustable bearing base |
| CN109538636A (en) * | 2018-12-11 | 2019-03-29 | 贵州天马虹山轴承有限公司 | A kind of can improve is coupled the squirrel-cage elasticity support of precision and holds |
| CN110320044A (en) * | 2019-05-27 | 2019-10-11 | 西北工业大学 | Active load shedding device after aero-engine tester sudden applied load |
| CN111075885A (en) * | 2019-12-16 | 2020-04-28 | 浙江大学 | Main machine vibration isolation device of super-gravity geotechnical centrifuge vacuum container |
| CN112727994A (en) * | 2020-12-25 | 2021-04-30 | 中国船舶重工集团公司第七0三研究所 | Adjustable squeeze film damper |
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Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108506354A (en) * | 2017-02-28 | 2018-09-07 | 长沙泽骏装饰设计有限公司 | A kind of bearing block |
| CN108506353A (en) * | 2017-02-28 | 2018-09-07 | 长沙泽骏装饰设计有限公司 | A kind of adjustable bearing base |
| CN108279119A (en) * | 2017-12-28 | 2018-07-13 | 华中科技大学 | A kind of squeeze film damper performance test apparatus of Parameter adjustable |
| CN108279119B (en) * | 2017-12-28 | 2019-05-21 | 华中科技大学 | A kind of squeeze film damper performance test apparatus of Parameter adjustable |
| CN109538636A (en) * | 2018-12-11 | 2019-03-29 | 贵州天马虹山轴承有限公司 | A kind of can improve is coupled the squirrel-cage elasticity support of precision and holds |
| CN110320044A (en) * | 2019-05-27 | 2019-10-11 | 西北工业大学 | Active load shedding device after aero-engine tester sudden applied load |
| CN110320044B (en) * | 2019-05-27 | 2020-12-08 | 西北工业大学 | Active load reduction device after sudden loading of aircraft engine tester |
| CN111075885A (en) * | 2019-12-16 | 2020-04-28 | 浙江大学 | Main machine vibration isolation device of super-gravity geotechnical centrifuge vacuum container |
| CN112727994A (en) * | 2020-12-25 | 2021-04-30 | 中国船舶重工集团公司第七0三研究所 | Adjustable squeeze film damper |
| CN112727994B (en) * | 2020-12-25 | 2022-08-30 | 中国船舶重工集团公司第七0三研究所 | Adjustable squeeze film damper |
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| CN105889317B (en) | 2018-03-27 |
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