CN101749322A

CN101749322A - Self-adapting mixed gas radial journal bearing using integral silk net damper

Info

Publication number: CN101749322A
Application number: CN200810186375A
Authority: CN
Inventors: B·H·埃塔斯
Original assignee: General Electric Co
Current assignee: General Electric Co
Priority date: 2008-12-05
Filing date: 2008-12-05
Publication date: 2010-06-23

Abstract

The present invention relates to a self-adapting mixed gas radial journal bearing using an integral silk net damper. The self-adapting mixed gas radial journal bearing (10) comprises a self-adapting mixed bearing pad (12) with a fluid static force convex part (22) and a capillary throttleer (28) for providing pressurized gas flow to the self-adapting mixed gas radial journal bearing (10).The self-adapting mixed gas radial journal bearing (10) also comprises an inner ring (32), an outer ring (34) and a damper bridge (36).Each side of the damper bridge (36) forms a damper cavity (42).the integral silk net damper (62) is located in the damper cavity (42).Integral pair middle springs (46,48) are between the inner ring and the outer ring (32,34) to conveniently provide radial and turning self adaption to the self-adapting mixed bearing pad (12).A bearing design without oil solves the properties of low dumping and low loading ability in the existing self-adapting air chaff bearing design, and meanwhile, the self adaption for the geometry changes of rotors is reserved.

Description

Use the self-adapting mixed gas radial journal bearing of integral silk net damper

Technical field

The present invention generally relates to a kind of bearing, and in particular, relates to the self adaption gas bearing (compliantgas bearing) of a kind of use integral silk net damper (integral wire mesh dampers).

Background technique

High-speed equipment, for example aeronautical engine turbomachinery, and boat changes application, and for example steamturbine, gas turbine and compressor etc. must pass through several natural frequencys (natural frequencies) or critical speed before reaching design and operation speed.When system moved under its natural frequency or critical speed, it is big that system/rotor oscillation amplitude becomes.These vibrations that derive from rotor unbalance may be destructive or or even catastrophic (if it can not get sufficient inhibition).Bearing with enough damping characteristics can limit or weaken synchronous vibration, passes through critical speed to allow device security ground.In addition, the rotor dynamic stability under good bearing damp helps at a high speed by the subsynchronous excitation that suppresses rotor intrinsic frequency.

Fluid film or oil film shaft bearing are from being used to suppress (dampen) for a long time by vibration that turbomachinery produced.Rotor in aviation gas turbine engine and the industrial centrifugal compressor usually uses squeeze-film damping bearing (it is supported by the mouse cage centralizing spring) based on oil (oil-based) to control vibration amplitude.In fluid-film bearing, thin fluid film forms buffering between the journal surface of rotation and fixing bearing surface, and has suppressed the vibration from rotor.In the squeeze-film damping bearing, the film of the fluid of liquid form (normally oil) is pushed by two non-rotary cylinders.A face is fixed, and another face is located by the centralizing spring structure and made track type movement with the motion of rotor.Being pressed through bearings of fluid film that the rail mounted rotor motion caused and suppressed rotor oscillation.

The simplest squeeze-film damping design bearing does not comprise centralizing spring.Outer bearing shell under the outer shroud of rolling element bearing or the fluid-film bearing situation is allowed in the clearance space between bearing outer diameter and housing inner diameter to extrude and float.The disappearance of mechanical centralizing spring means at when starting damper axle journal will reduce as far as possible (bottomed out) in this design configurations.Begin rotation along with speed increases with axle, the axle journal of damper (bearing shell outer surface) will rise.Oil film in the squeeze-film damping device also produces direct rigidity (directstiffness) unlike traditional fluid-film bearing.Yet damper has manifested the proterties (directstiffness-like behavior) that direct rigidity characteristic is arranged really.This direct rigidity is owing to cross-linked damping constant, and it presents (spring) of rigidity characteristic characteristic.

Non-damper placed in the middle is a kind of in the design of the most nonlinear squeeze-film damping device.This non-linear proterties is owing to two kinds of fundamental mechanisms.First kind of these two kinds of Nonlinear Mechanism owing to nonlinear characteristics that cross-linked damping constant produced.And second root of the non-linear proterties that such damper embodied comes from the direct result that the damper axle journal reduces as far as possible.

The simplest method that centralizing spring is provided in the squeeze-film damping device is the use by elastomer O shape ring.The advantage of this design comes from its simplicity, be easy to make and damper is incorporated into ability in the little big envelope.Some shortcoming of this design is owing to the limited range of utilizing the obtainable rigidity of elastomer.In elastic material, owing to materials variances and temperature and time reasons such as influence, predict that rigidity is difficulty comparatively with good certainty degree to its attribute.In addition, the design of O shape ring is subjected to the influence of creep easily, causes damper to touch the end, and it may cause bilinear spring proterties as mentioned above.

The squeeze-film damping device design that is used the most at large, the squeeze-film damping device that especially is used the most at large in aeronautical engine design is a mouse cage supporting type damper.The inevitable unique features of this designing institute is needed relatively large axial space (comparing with damper length).This is major defect wherein a kind of of this damper designs.The mouse cage that is formed for the centralizing spring of damper usually needs to be equivalent to three times to four times so much axial spaces of damper itself.

In clearance space, axle journal is all needed special instrument and skill to neutralization assembling mouse cage spring.The mouse cage spring also makes design of damper end seal and assembling complicate.Make spring assembly biasing (offset) with compensation because the gravitational load that the weight of axle causes also is very difficult.Keeping parallelism then is to increase the uncertainty of this design and another factor of complexity between damper axle journal and housing.

Another squeeze-film damping device design based on oil comprises integrated type damper centralizing spring.In this design, the cantilever type supporting rib forms the centralizing spring element together with they sections (sector) in the supporting of place, two ends.Little gap has formed squeeze-film damping device clearance space between section and outer shroud.Different with the design of mouse cage spring, the design of integrated type damper centralizing spring does not take any extra axial space that exceeds the shared existing length of bearing.Complete assemblies can comprise the section of any amount, and this depends on the damping at concrete application, required rigidity and load.Wire spark-erosion machine tool (EDM) provides a kind of good method, by this method precision that can be very high and repeatable obtain required gap and keep superior parallelism between damper axle journal and the housing simultaneously.

Although these squeeze film bearing structures provide these advantages,, the bearing of oil lubrication has caused higher cost and maintenance workload and the integrity problem relevant with leakage, filtration and the conduit of oil.These defectives of oil-lubricated bearing and other defective have impelled industrial quarters to manage to develop self adaption air foil bearing (air foil bearing).Yet current airfoil blade technolgy mainly is confined to small-sized light weight rotor and machine, i.e. air cycle machine on the aircraft (ACM).Thereby, though the benefit that pneumatic bearing is incorporated in the aircraft is fine understanding, must overcome great technological challenge, the design of conforming to the actual situation with development.These challenges comprise that development has and are higher than current air foil significantly and hold the load carrying capacity of technology and the gas bearing of damping.

Summary of the invention

Briefly, a kind of self-adapting mixed gas radial journal bearing comprises a plurality of ADAPTIVE MIXED bearing bushs; Inner ring (it is adjacent with these a plurality of bearing bushs), the outer ring, and radially and with one heart place damper bridge between this inner ring and the outer ring, this damper bridge has such axial length, this axial length is less than the axial length of these a plurality of bearing bushs and outer ring, thereby forms damper chamber in each side of damper bridge; And, be arranged in the integral silk net damper at damper chamber (it is at each side place of damper bridge).

In another aspect of this invention, a kind of self-adapting mixed gas radial journal bearing comprises a plurality of ADAPTIVE MIXED bearing bushs, and at least one bearing bush comprises the hydrostatic recess and is used to provide the capillary restrictor of flow of pressurized gas; And the inner ring adjacent with these a plurality of bearing bushs, outer ring and radially and with one heart place damper bridge between inner ring and the outer ring, the damper bridge has the littler axial length of axial length than these a plurality of bearing bushs and outer ring, thereby all forms the damper chamber in each side of damper bridge.

In still another aspect of the invention, a kind of self-adapting mixed gas radial journal bearing comprises a plurality of ADAPTIVE MIXED bearing bushs, and at least one bearing bush comprises the hydrostatic recess and is used to provide the capillary restrictor of flow of pressurized gas; The inner ring adjacent with these a plurality of bearing bushs, the outer ring, and radially and with one heart placing damper bridge between this inner ring and the outer ring, this damper bridge has the littler axial length of axial length than these a plurality of bearing bushs and outer ring, thereby forms damper chamber in each side of damper bridge; Be located at the integral silk net damper in the damper chamber at each side place of damper bridge; And a plurality of integrated type centralizing springs between this inner ring and outer ring.

Description of drawings

When describing in detail below the reference accompanying drawing is read, will understand these features of the present invention, aspect and advantage and further feature, aspect and advantage better, similar reference number represents to spread all over the similar parts of accompanying drawing in the accompanying drawing, wherein:

Fig. 1 is partial cross section's perspective view of self-adapting mixed gas radial journal bearing assembly according to an embodiment of the invention.

Fig. 2 is the end elevation of the self-adapting mixed gas radial journal bearing body (bearing housing) of Fig. 1.

Fig. 3 is the sectional view of the self-adapting mixed gas radial journal bearing body that dissects of the hatching 3-3 along Fig. 2.

Fig. 4 is the sectional view of the amplification of transregional section (midspan sector) in the bearing support of Fig. 2 self-adapting mixed gas radial journal bearing body.

Fig. 5 is the sectional view of striding the amplification of the hydrostatic recess of part and capillary restrictor in the bearing support of Fig. 4.

List of parts

10 self-adapting mixed gas radial journal bearings;

12 bearing bushs;

14 pad surfaces;

16 rotors or axle;

18 arrows;

20 axial notches;

22 hydrostatic recesses;

24 degree of depth;

26 width;

28 capillary restrictors;

30

32 inner rings;

34 outer rings;

35 gaps;

36 damper bridges;

38 axial lengths (damper bridge);

40 axial lengths (bearing bush);

42 damper chambeies;

44 width (damper chamber);

46 integrated type centralizing springs;

48 integrated type centralizing springs;

50 sections;

52 angles;

54 horizontal axiss;

56 angles;

58 vertical axis;

60 gaps;

62 integral silk net dampers (IWMD);

64 end plates;

66 end plates;

68 damper compressing surfaces;

70 damper compressing surfaces;

Embodiment

With reference to accompanying drawing, the similar elements that wherein identical reference number representative spreads all over each view, Fig. 1-5 has shown self-adapting mixed gas radial journal bearing according to an embodiment of the invention, totally with shown in the reference number 10.Bearing 10 comprises a plurality of ADAPTIVE MIXED bearing bushs 12.Each bearing bush 12 comprises the pad surfaces 14 near rotor rotated or axle 16, and this rotor or axle 16 rotate on the direction of arrow 18 usually.In one embodiment, bearing bush 12 comprises inclination liner (tilt pads), and it has the integrated type spring (Fig. 2) of biasing.Each bearing bush 12 also comprises axial notch 20, and it is used to reduce the weight of bearing bush 12.The pad surfaces 14 of each bearing bush 12 also comprises hydrostatic recess 22, and it has the degree of depth 24 and width 26 (Fig. 5).For example, hydrostatic recess 22 can have such degree of depth, and this degree of depth is 2 times to 10 times of thickness of the gas film between bearing surface 14 and the rotor cover.In an illustrated embodiment, the area of hydrostatic recess 22 is about 0.027 to the ratio of the area of bearing surface 14.Usually, compare with the bearing surface area, the area of hydrostatic recess 22 is more little, and (stability margin) is high more for the bearing stability margin.

In one embodiment, hydrostatic recess 22 medially is positioned on each bearing bush 12, and therefore locatees symmetrically about axle 16.In another embodiment, be positioned on the bearing bush 12 to hydrostatic recess 22 Off center.Yet even recess 22 is positioned on the bearing bush 12 in off-centered mode, these hydrostatic recesses 22 are located symmetrically about axle 16 and are remained possible.28 one-tenth fluids of each hydrostatic recess 22 and capillary restrictor are communicated with, and are used for flow of pressurized gas, and for example air stream or the like offers bearing bush 12.Each capillary restrictor 28 is attached to pressurized-gas source 30 (Fig. 1), for example compressor by-pass flow (bypass) or the like.In one embodiment, capillary restrictor 28 is located with respect to hydrostatic recess 22 asymmetricly.In another embodiment, capillary restrictor 28 is located symmetrically with respect to hydrostatic recess 22.Superheated steam provides hydrostatic lifting force (liftingforce), so that axle 16 during starts can not reduce as far as possible.In other words, superheated steam provides lifting force, thereby even with axle 16 be lifted away from bearing bush 12 one by one axle 16 do not rotate.In one embodiment, gas has the pressure that is positioned at the extremely about 200psig scope of about 30psig.

In another embodiment, bearing 10 does not have hydrostatic recess 22, and only has to the capillary restrictor 28 on the surface 14 of bearing bush 12.In this state, capillary restrictor 28 equally can be about

axis

54,58 and placed in the middle, perhaps can setover towards the leading edge (leading edge) of bearing bush 12, and this makes this location asymmetric with respect to

axis

54,58.

In an illustrated embodiment, bearing 10 has four bearing bushs 12 of locating symmetrically about axle 16, and wherein, each bearing bush 12 comprises independent hydrostatic recess 22 (having capillary restrictor 28).Yet, should understand that the present invention is not subjected to the restriction of the quantity of recess, capillary restrictor and bearing bush, but, can carry out the present invention with bearing bush, recess and the restrictor of any requirement.

Referring to Fig. 3 and Fig. 4, bearing 10 comprises the inner ring 32 adjacent to bearing bush 12, outer ring 34, and radially and with one heart place damper bridge 36 between inner ring and the outer ring 32,34.Gap 35 is normally to be divided into a plurality of sections 50 with these a plurality of bearing bush 12 corresponding modes with inner ring 32.Damper bridge 36 has axial length 38, and it is less than the axial length 40 of outer ring 34 and bearing bush 12, thereby forms the damper chamber 42 with width 44 in each side of damper bridge 36.

One aspect of the present invention is that bearing 10 comprises a plurality of integrated

type centralizing springs

46,48 that are positioned between inner ring and the outer ring 32,34.In one embodiment, each section 50 of bearing 10 comprises a pair of integrated

type centralizing spring

46,48; Spring 46 is leading edge integrated type springs, and spring 48 is trailing edge (trailing edge) integrated type springs.In an illustrated embodiment, integrated

type centralizing spring

46,48 has the sectional shape of serpentine usually.Integrated

type centralizing spring

46,48 can utilize wire electrical discharge machining (EDM) technology and moulding.Gap 60 between bearing bush 12 and outer ring 34 is that

spring

46,48 provides clearance space, to adapt to owing to high-speed and high-temperature is used centrifugal effect and the thermal effect that produces.In addition, clearance space 60 has reduced the weight of bearing bush and the gross weight of bearing unit.The non-linear proterties that is presented with traditional bump foil bearing (bump foil bearing) is different, and integrated

type centralizing spring

46,48 provides linear proterties.Be different from traditional squirrel-cage design of the extra axial length of needs, this integrated type centralizing spring design does not take any extra axial space that exceeds the axial length 40 of bearing bush 12.Commercial can be from West Greenwich, the KMC company of RI ( Www.kmcbearings.com) obtain a kind of example of integral silk squeeze-film damping device (integral wire squeeze film damper) based on oil.

As shown in Figure 4, the spring that is used for each section 50 is to 46,48 setover with respect to bearing bush 12, rotate (padrotation) to produce inclination liner motion (tilting pad motion) or liner, and it has demonstrated the stability and the load carrying capacity that can greatly strengthen bearing.In other words,

spring

46,48 is located with asymmetric form with respect to bearing bush 12.Specifically, the center line of spring 46 (centerline) has formed angle 52 with respect to the horizontal axis 54 of section 50, and the center line of spring 48 has formed less angle 56 with respect to vertical axis 58, and vertical axis 58 is substantially perpendicular to horizontal axis 54.Make angle 56 less than angle 52, this produces non-moment placed in the middle on bearing bush 12, thereby (global) that cause the integral body of bearing bush 12 tilts or rotation.In one embodiment, the difference of

angle

52,56 can be at about 10 degree to the scope between about 25 degree.For example, angle 52 can be about 28 degree, and angle 56 can be about 18 degree, perhaps poor about 10 degree.In addition, the difference of

angle

52,56 allows that the bearing bush 12 of bearing 10 becomes radially adaptive and is adaptive rotationally, thus allow owing at a high speed, the high temperature radially growth of using the bearing hole that the centrifugal effect that produced and thermal effect cause.In an illustrated embodiment, bearing 10 has four sections 50, has a pair of

spring

46,48 in each section.Yet, should understand, according to load and required rigidity, can under the condition of the spring in each section of the section that has any requirement and any requirement, carry out the present invention at concrete application.

As mentioned above, the asymmetric localization of the asymmetric localization of

integrated type spring

46,48 and hydrostatic recess 22 has produced the inclination or the rotation of the integral body of bearing bush 12.Yet, by provide have relatively low (with trailing edge integrated type spring 48 comparatively speaking) the leading edge integrated type spring 46 of radial rigidity, also can realize the inclination or the rotation of the integral body of bearing bush 12.For example, it is about 75 that leading edge integrated type spring 46 can have, the radial rigidity of 000lb/in, and that trailing edge integrated type spring 48 can have is about 85, the radial rigidity of 000lb/in.The difference of this radial rigidity between

spring

46,48 has caused the inclination or the rotation of the integral body of bearing bush 12.

Another aspect of the present invention is the integral silk net damper (IWMD) 62 that bearing 10 comprises does not have oil (oil-free), and it is arranged in the damper chamber 42 on damper bridge 36 each side.In other words, IWMD 62 is between bearing bush 12 and outer ring 34, as shown in fig. 1.IWMD 62 is wire mesh of braiding, and it comprises and is woven into cancellated plasticity twisted wire (plastic strand) or tinsel.The braiding process produces the net of the ring that connects mutually.These rings can move relative to each other on identical plane, and can not make the net distortion, thereby give the two-way stretchability of mesh grid (stretch).Because each ring plays a part little spring when being subjected to tensile stress or compressive stress, braided metal has intrinsic elasticity.The metal of braiding also provides high machinery not have oil damping characteristic and nonlinear elasticity property coefficient.Vibration and mechanical shock can be controlled effectively, to eliminate fierce resonance condition and to provide enough protection to avoid dynamic overload.Studies show that hold with traditional air foil and compare, IWMD 62 provides thirtyfold at least damping.IWMD 62 can be made of a variety of materials, for example steel, inconel, aluminium, copper, tantalum, platinum, polypropylene, nylon, polyethylene or the like.Can adjust density and the size of IWMD62, use to meet concrete design.Commercial can be from Edison, the Metex company (www.metexcorp.com) of NJ obtains a kind of example of silk net damper.

Between self-adapting mixed gas radial journal bearing 10 of the present invention and traditional bearing unit, there is significant difference.As mentioned above, commercial can be from West Greenwich, the KMC company of RI obtains traditional integral silk squeeze-film damping device based on oil.Using the KMC integral silk squeeze-film damping device (ISFD) of serpentine spring is a kind of like this bearings, and wherein, damping derives from replaces (displacing) to another control volume with fluid from a certain control volume.The viscous that the motion that fluid passes clearance space or hole has produced " based on fluid " dissipates, and it is implemented as the damping in the bearings system.Usually, the squeeze film fluid is identical with the lubricating fluid of rolling element bearing or shaft bearing (ISFD fits together with it).In the flexible pivot of traditional ISFD (flexure pivot) bearing unit, Ding Wei serpentine spring is allowed the radial motion of each inner ring quadrant symmetrically, and this inner ring quadrant has flexible trunnion bearing liner.Flexible pivot allows that bearing bush centers on the base portion of flexible pivoting lever (beam) and pivot revolution or rotate.Therefore, the serpentine spring provides radially adaptivity, and rotation adaptivity in the bearing bush or deflection then realize by this flexible pivot.Each feature, that is, flexible pivot and serpentine spring have single function.

On the contrary, use the ADAPTIVE MIXED shaft bearing 10 of integral silk net damper 62 not produce damping, but by mechanical structure, promptly silk net damper 62, produce damping by the mode of extruding or displacement fluid.Lubricating fluid in the bearing 10 of the present invention is gas and do not provide viscous to dissipate in bearings or damping, and damping derives from combining of lag structure damping (hysteretic structural damping) and coulomb friction.Structural damping derives from the bending of the unanimity of thousands of independent silk thread section (wire segments), and coulomb friction derives from little slip that silk thread is being gone up each other.Especially for requiring oil free type operation maybe may benefit from for the machine of oil free type operation, this combination provides a kind of damping source of fabulous no oil.Use the favourable of ADAPTIVE MIXED shaft bearing 10 of integral silk net damper 62 to be characterised in that, only just can obtain radially adaptivity and rotation adaptivity function by serpentine spring 46,48.This is because the serpentine spring 46,48 among the present invention is located in asymmetric mode about each quadrant or the section 50 of inner ring 32.Serpentine spring 46,48 is located the deflection of the rotation in the bearing bush 12 that has caused each in asymmetric mode, this makes and also turns except that translation radially.Except a feature is carried out the dual functions, another advantage is that shared radial space reduces to some extent, and this is because flexible pivot has not existed, and this has reduced the weight of bearing.This is very important in aerospace applications, because weight is a main drive factor at performance.Further the reducing to come from of the weight of bearing carries out EDM machining to the material between the serpentine spring 46,48.

Bearing 10 also comprises a pair of

end plate

64,66, it provides damper compressing surface (compression lands) 68,70 respectively, preventing the axial motion of unwanted IWMD 62, and can be used for adjusting rigidity and damping constant according to the level of end plate compression.

Self-adapting mixed gas radial journal bearing 10 of the present invention can use under several operating modes.A kind of operating mode is pure fluid dynamic operating mode.In the simplest this operating mode, use the self adaption gas bearing of integral silk net damper to have the self adaption liner of not being with the hydrostatic ability.This operating mode is applicable to the situation that is difficult to obtain to remain superheated steam.This operating mode produces pressure by fluid dynamic between self adaption liner and rotor.Under this operating mode, for given load, bearing bush will lift away from rotor surface under corresponding spinner velocity.Yet, come into force and before bearing bush lifts away from, have the moment friction area in fluid dynamic.

Another kind of operating mode comprises the transformation that moves to mixing (fluid dynamic and hydrostatic) operation from fluid dynamic.For example, this pattern will be present in following the time, that is, and and when during starts unavailable the and this initial running state of external fluid static(al) pressurization is subjected to the fluid dynamic domination.In this case, friction area is present in the place that has sliding friction between rotor surface and the bearing bush surface moment.Finally, because fluid dynamic, bearing bush lifts away from.To under a certain definite speed, begin to start to the hydrostatic of each bearing bush, and probably by emitting superheated steam and energy supply from the main working fluid in the turbine stage.In this, bearing moves in a kind of mixed mode.

Another operating mode is to mixed running from the hydrostatic run transition.This situation will be present in, for example, and when all can obtain superheated steam in the whole service order that runs through machine.It is favourable having superheated steam before the rotor rotation, because this gas can prevent the moment friction, reduces starting torque, and tolerable dead halt under urgency (for example stall).In this operating mode, bearing bush need not rotation just can raise rotor, and it is pure hydrostatic.Along with rotor quickens, derive from hydrokinetic contribution become more account for outstanding.Under high speed, reach mixed running.

As mentioned above, self-adapting mixed gas radial journal bearing 10 of the present invention provides the oilless bearing design, its be devoted to solve current air foil hold in the design intrinsic low resistance and the problem of low-load ability characteristics.In addition, self-adapting mixed gas bearing of the present invention provides the damping (30 times or more) more much higher than traditional foil bearing technology, bigger load carrying capacity and higher significantly manufacturing repeatability significantly.In addition, compare with the fluid film damper designs or based on the damper designs of oil, no oil gas axon of the present invention is held significantly and is provided cost savings.

The specification usage example of being write comprises optimal mode, and makes any those of skill in the art can construct and use the present invention with open the present invention.Patentable scope of the present invention is defined by the claims, and can comprise other example that those of skill in the art can expect.If it not is the structural element that is different from the claim literal language that these other examples have, if perhaps it comprises the structural element that does not have the equivalence of essence difference with the claim language, these other examples all fall within the scope of claim so.

Claims

1. a self-adapting mixed gas radial journal bearing (10), it comprises:

A plurality of ADAPTIVE MIXED bearing bushs (12);

The inner ring (32) adjacent with these a plurality of bearing bushs (12), outer ring (34), and radially and with one heart place described inner ring and described outer ring (32,34) the damper bridge (36) between, described damper bridge (36) has the axial length (38) littler than the axial length (40) of described a plurality of bearing bushs (12) and described outer ring (34), thereby forms damper chamber (42) in each side of described damper bridge (36); And

Be located at the integral silk net damper (62) in the described damper chamber (42) of each side of described damper bridge (36).

2. bearing according to claim 1 is characterized in that, described bearing also comprises a plurality of integrated type centralizing springs (46,48) that are positioned between described inner ring and outer ring (32,34).

3. bearing according to claim 2 is characterized in that, described a plurality of integrated type centralizing springs (46,48) have the sectional shape of serpentine.

4. bearing according to claim 2 is characterized in that, gap (35) are separated into described inner ring (32) usually and the corresponding a plurality of sections of described a plurality of bearing bushs (12) (50).

5. bearing according to claim 4 is characterized in that, each section (50) comprises a pair of integrated type centralizing spring (46,48).

6. bearing according to claim 5, it is characterized in that, this is to horizontal axis (54) formation first angle (52) of the integrated type centralizing spring (46) in the integrated type centralizing spring with respect to described bearing (10), and this forms second angle (56) to another integrated type centralizing spring (48) of integrated type centralizing spring with respect to the vertical axis (58) of described bearing (10), and wherein, described first angle (52) is different from described second angle (56).

7. bearing according to claim 5, it is characterized in that, this is to integrated type centralizing spring (46,48) an integrated type centralizing spring in has first radial rigidity, and wherein, this another integrated type centralizing spring to integrated type centralizing spring (46,48) has second radial rigidity different with described first radial rigidity.

8. bearing according to claim 1 is characterized in that, each bearing bush (12) also comprises the pad surfaces (14) that has hydrostatic recess (22), and described hydrostatic recess (22) has the degree of depth (24) and width (26).

9. bearing according to claim 8 is characterized in that, described bearing also comprises the capillary restrictor (28) that becomes fluid to be communicated with described hydrostatic recess (22), and it is used for providing flow of pressurized gas to described bearing (10).

10. bearing according to claim 9 is characterized in that, described capillary restrictor (28) is located in asymmetric mode with respect to described hydrostatic recess (22).