CN211778560U - Air bearing comprising self-adaptive elastic material damper - Google Patents

Abstract

The utility model provides an air bearing containing self-adaptation elastic material attenuator for install between pivot and stator, the cover is equipped with the intermediate junction spare between air bearing and the stator, set up at least one first attenuator between air bearing and the intermediate junction spare, set up at least one second attenuator between intermediate junction spare and the stator, first attenuator is for having elastic O type ring or hollow cylindrical rubber damper. The utility model discloses can solve between bearing and the stator collision, the card is dead, how to adjust the damping and eliminate resonant technical problem.

Description

Air bearing comprising self-adaptive elastic material damper

Technical Field

The utility model relates to a bearing technical field, concretely relates to air bearing who contains self-adaptation elastic material attenuator.

Background

Due to the characteristics of small friction coefficient and friction torque, high motion precision and the like, the non-contact bearing is more and more commonly used in some occasions with high rotating speed. But compared with a contact type mechanical bearing, the non-contact type mechanical bearing has small bearing clearance and higher processing difficulty.

For example, in the case of a non-contact radial bearing, the gap between the bearing and the stator is narrow, which requires high machining precision and assembly precision of the stator and the bearing, otherwise, collision and seizure phenomena are easily generated, and abrasion and damage are caused to the bearing.

When a non-contact bearing, such as an air bearing, is just started, air between the bearing and a rotor is in a compressed state, pressure exists, when the excitation frequency generated by the unbalanced force of the rotor is consistent with the natural frequency of the rotor and a supporting system thereof, resonance can be caused, the system noise and the vibration are serious if the resonance is light, and parts are scrapped if the resonance is heavy.

Disclosure of Invention

In order to solve the technical problem, an object of the present invention is to provide an air bearing with an adaptive elastic damper, which can solve the technical problems of collision, jamming, damping adjustment and resonance elimination between the bearing and the stator.

The technical scheme of the utility model as follows:

the utility model provides an air bearing who contains self-adaptation elastic material attenuator for install between pivot and stator, the cover is equipped with intermediate junction spare between air bearing and the stator, set up at least one first attenuator between air bearing and the intermediate junction spare, set up at least one second attenuator between intermediate junction spare and the stator, first attenuator is for having elastic O type ring or hollow cylindrical rubber damper.

Further, the middle connecting piece is a hollow cylindrical pressing cylinder.

Furthermore, an axial limit is arranged between the middle connecting piece and the stator.

Furthermore, the outer wall of the air bearing is provided with at least one accommodating groove in a surrounding mode parallel to the end face of the outer wall of the air bearing, the O-shaped ring is nested in the accommodating groove, and the O-shaped ring is higher than the accommodating groove.

Furthermore, the number of the accommodating grooves is one, and the accommodating grooves and the O-shaped rings are arranged in the middle of the air bearing.

Furthermore, two ends of the air bearing are respectively provided with at least one accommodating groove and an O-shaped ring.

Furthermore, an annular air cavity is arranged on the outer wall of the air bearing, two sides of the annular air cavity are respectively provided with at least one accommodating groove in a surrounding mode parallel to the end face of the annular air cavity, the O-shaped ring is nested in the accommodating groove, and the O-shaped ring is higher than the accommodating groove.

Further, the outer diameter of the outer wall of the bearing at one side of the annular air cavity is larger than the outer diameter of the outer wall of the bearing at the other side of the annular air cavity, and correspondingly, the inner diameter and the outer diameter of the O-ring and the accommodating groove at one side of the annular air cavity are larger than those of the O-ring and the accommodating groove at the other side of the annular air cavity; or the radial thickness of the O-shaped ring at one side of the annular air cavity is larger than that at the other side of the annular air cavity.

Further, the section of the O-shaped ring is circular or rectangular or trapezoid or oval when the O-shaped ring is not compressed.

Further, the hollow cylindrical rubber damper is fixed in the intermediate connecting member.

Furthermore, the O-ring or hollow cylindrical rubber damper is made of rubber or metal rubber.

The utility model has the advantages that:

1. the utility model discloses an air bearing structure can make the fit clearance between stator and the air bearing match automatically under the condition that does not change air bearing structure and size, and it can solve between bearing and the stator collision, the card is dead, how to adjust the damping and eliminate resonant technical problem.

2. The utility model discloses can play the effect of sealing up gas when the attenuator contains O type ring, it is very big to act on in hydrostatic bearing, can guarantee in external air feed can get into the bearing through the orifice, and can keep certain air feed pressure to be unlikely to reveal.

3. The utility model discloses a attenuator can be through the deformation absorption vibration energy of self, and the installation suitable attenuator can be with rotor vibration and whirlpool (the vibration that rotor self leads to, for example because the vibration that dynamic balance problem or lead to through critical speed) complete absorption or most absorption, and the help rotor is spent critical speed or is reduced the dynamic balance grade requirement smoothly, or can play the cushioning effect when the external world has the interference vibration, keeps the collision not between rotor and the bearing, plays the guard action.

4. The air bearing has extremely high requirement on the coaxiality because the working clearance is very small, so the machining requirement is extremely high, when the air bearing starts to work, a certain pressure exists between the rotor and the bearing, and when the damper is properly designed and selected and the air pressure in the bearing is higher than the deformation pressure of the damper, the rotor can automatically correct the coaxiality, so the damper greatly reduces the requirement of the air bearing on the coaxiality, namely the requirements on machining equipment and a machining process are reduced, and the production cost is greatly reduced;

when the hydrostatic bearing is started, the bearing is forced to be coaxial with the rotor due to the fact that rigidity between the bearing and the rotor is high, tolerance between the bearing and the stator is offset by means of compression of the damper, coaxiality and roundness can be guaranteed without being forced on a finish machining layer manually, and machining precision requirements and difficulty of the bearing are greatly reduced.

5. The utility model discloses in, the attenuator is given with power transmission to the rotor through the interact of power, and the attenuator is through the deformation of oneself with the energy absorption of rotor resonance for vibration energy reduces, and the help rotor is fast through the resonance mode.

6. Adopt the utility model discloses a floating platform (floating platform effect) is made to the attenuator, makes it not only can be along with decide, the coaxial direction translation of rotor, the stick up that can also be free moves. The clearance between the bearing and the stator is larger than the clearance between the bearing and the rotor, meanwhile, the support rigidity between the bearing and the stator is much lower than the support rigidity between the bearing and the rotor, the coaxiality or roundness and other precisions of the 2 bearings on the stator cannot be completely coaxial due to process conditions, and the rotor-bearing-stator is actually clamped in a static state, so that the rotor can be self-locked when not needing to rotate, the situation that the rotor is repeatedly collided with the bearing due to external vibration in the transportation process is avoided, and the static reliability and the total service life of the system are greatly improved.

Drawings

FIG. 1 is a schematic structural diagram of an adaptive damper;

FIG. 2 is a schematic structural view of an embodiment of an air bearing with an O-ring;

FIG. 3 is a schematic structural view of another embodiment of an O-ring on an air bearing;

FIG. 4 is a schematic view of an alternative embodiment of an O-ring on an air bearing;

FIG. 5 is a schematic size-indicating view of an O-ring;

FIG. 6 is a schematic view of a damper configuration with different diameters of the air bearing support arms;

FIG. 7 is a schematic view showing an installation structure of a hollow cylindrical rubber damper;

FIG. 8 is a schematic structural diagram of an embodiment of an adaptive damper;

FIG. 9 is a graph of rotor speed versus vibration frequency for different damping effects.

Detailed Description

In order to better understand the technical solution of the present invention, the present invention will be further explained with reference to the following specific embodiments and the accompanying drawings.

As shown in fig. 1, an air bearing including an adaptive elastic material damper is provided for an embodiment of the present invention. The air bearing is used for being arranged between a rotating shaft and a stator.

An intermediate connector 83 is sleeved between the air bearing 1 and the stator, at least one first damper 81 is arranged between the air bearing 1 and the intermediate connector 83, at least one second damper 82 is arranged between the intermediate connector 83 and the stator, and the first damper 81 is one of an elastic O-ring or a hollow cylindrical rubber damper 4.

In the present embodiment, the second damper 82 is one of an O-ring 2 having elasticity, a hollow cylindrical rubber damper 4, and a metal damper. The following six embodiments are included:

(1) the first damper 81 is an O-ring 2, and the second damper 82 is an O-ring 2: the outer wall of the air bearing 1 and the outer wall of the middle connecting piece 83 are both provided with a containing groove 12, and an O-shaped ring 2 is nested in the containing groove 12.

(2) The first damper 81 is a hollow cylindrical rubber damper 4, and the second damper 82 is an O-ring 2: a bearing seat is fixed on the inner wall of the middle connecting piece 83, two ends of the bearing seat are convex, the middle of the bearing seat is concave, and the hollow cylindrical rubber damper 4 is nested in the middle concave part of the bearing seat; the outer wall of the intermediate connecting member 83 is provided with a containing groove 12, and the O-ring 2 is nested in the containing groove 12.

(3) The first damper 81 is an O-ring 2, and the second damper 82 is a hollow cylindrical rubber damper 4: the outer wall of the air bearing 1 is provided with a containing groove 12, and an O-shaped ring 2 is nested in the containing groove 12; a bearing seat is fixed in the stator, and two ends of the bearing seat are raised and the middle of the bearing seat is depressed; the hollow cylindrical rubber damper 4 is nested in the middle concave part of the bearing seat.

(4) The first damper 81 and the second damper 82 are both hollow cylindrical rubber dampers 4: bearing seats are fixed on the inner walls of the stator and the middle connecting piece 83, and two ends of each bearing seat are protruded and the middle of each bearing seat is sunken; the hollow cylindrical rubber damper 4 is nested in the middle concave part of the bearing seat.

(5) The first damper 81 is an O-ring 2, and the second damper 82 is a metal damper, particularly a metal foil damper 5: the outer wall of the air bearing 1 is provided with a containing groove 12, and an O-shaped ring 2 is nested in the containing groove 12; the metal foil damper 5 includes at least one protrusion and support portion, which support the outer wall of the intermediate connector 82 and the inner wall of the stator, respectively, of the metal foil damper 5.

(6) The first damper 81 is a hollow cylindrical rubber damper 4, and the second damper 82 is a metal damper, in particular, a metal foil damper 5: a bearing seat is fixed on the inner wall of the middle connecting piece 83, two ends of the bearing seat are convex, the middle of the bearing seat is concave, and the hollow cylindrical rubber damper 4 is nested in the middle concave part of the bearing seat; the metal foil damper 5 includes at least one protrusion and support portion, and the protrusion and support portion of the metal foil damper 5 support the outer wall of the intermediate connector 83 and the inner wall of the stator, respectively.

Further, the metal foil damper 5 is a one-piece corrugated structure, and the above-described "supporting" manner of the boss and the support of the metal foil damper 5 is fixed. For example: the convex part 51 and the supporting part 52 are respectively fixed on the outer wall of the hollow cylindrical pressing cylinder 6 and the inner wall of the stator.

For each of the above embodiments, by providing the intermediate connecting member 83, the fitting clearance between the stator and the air bearing 1 can be automatically matched without changing the structure and size of the air bearing 1.

Preferably, the intermediate connecting member 83 is a hollow cylindrical press cylinder.

In order to prevent the intermediate connecting piece 83 from moving axially, the intermediate connecting piece 83, the stator and the air bearing 1 can be axially limited, so that the intermediate connecting piece 83 can transmit deformation force in the radial direction while being axially limited, and the damping adjustment function is achieved.

In the embodiment of the present invention, the adaptive elastic material damper structure includes a first damper 81, a second damper 82 and an intermediate connecting member 83.

The embodiment of the utility model provides a still be provided with first attenuator 81 structure.

Examples

When the air bearing is a hydrostatic bearing, the outer wall of the bearing is provided with an annular air cavity, and the bottom of the annular air cavity is provided with a throttling hole (not shown in the figure) which is communicated with a gap between the inner wall of the air bearing and the rotating shaft.

An annular air cavity 11 is arranged on the outer wall of the air bearing 1, at least one accommodating groove 12 is formed in the two ends of the annular air cavity 11 respectively surrounding the outer wall of the bearing, an O-shaped ring 2 is arranged in the accommodating groove 12, and the O-shaped ring 2 is annularly sleeved in the accommodating groove 12 and is higher than the accommodating groove 12.

The position of the O-ring 2 can be determined according to the specific requirements of the structural design.

As shown in fig. 2, it is an embodiment of the O-ring 2 arrangement method provided by the present invention. In this embodiment, the two side edges of the air bearing 1 are respectively provided with an O-ring 2, which can simultaneously play a role in air sealing and damping, and can also reduce the requirement for coaxiality. Specifically, fig. 2 shows a symmetrical air bearing 1, and two O-rings 2 are respectively arranged at two ends of an annular air cavity 11.

Fig. 3 shows another embodiment of the O-ring 2 arrangement provided by the present invention. In this embodiment, for the asymmetrically arranged air bearing 1, one and two O-rings 2 are respectively arranged at both ends of the annular air cavity 11.

Fig. 4 shows another embodiment of the O-ring 2 arrangement according to the present invention. In this embodiment, two O-rings 2 are respectively disposed at two ends of the annular air cavity 11 for the symmetrically disposed air bearings 1.

When the air bearing is a dynamic pressure bearing, the air film between the inner wall of the bearing and the rotating shaft is gradually generated by whirling the surrounding air through the rotation of the rotating shaft, an air cavity and a throttling hole are not required to be arranged on the outer wall of the bearing, and the rest parts are the same as the static pressure bearing in the above embodiment.

Preferably, the cross section of the O-ring 2 when uncompressed may be circular, rectangular, trapezoidal, elliptical, or the like.

The O-ring 2 shown in fig. 5 has a circular cross-section and becomes elliptical after compression. According to the figure shown:

for the air bearing 1 with the diameter of the rotating shaft 3 being 20-30 mm, the O-ring 2 with the line diameter being 1.2-1.8 mm can be used, the proportional relation a/b between the inner diameter a of the O-ring 2 and the outer diameter b of the accommodating groove 12 is 0.7-0.85, the radial compression amount of the O-ring 2 is 0.25-0.35 mm, and the width c of the accommodating groove 12 is 1.7-1.8 mm. The clearance d between the outside height of the accommodating groove 12 and the stator is 0.1-0.35 mm, the size of the clearance is related to the radial vibration amplitude of the rotor 3 required by a machine, the smaller the clearance is, the smaller the radial vibration amplitude of the rotating shaft 3 is, and the larger the clearance is, the larger the radial vibration amplitude of the rotating shaft 3 is.

For the air bearing 1 with the diameter of the rotating shaft 3 of 30-50 mm, an O-ring 2 with the line diameter of 1.3-2 mm can be used, the proportional relation a/b between the inner diameter a of the O-ring 2 and the diameter b of the accommodating groove 12 is 0.7-0.85, the radial compression amount of the O-ring 2 is 0.25-0.35 mm, and the width c of the accommodating groove 12 is 1.7-1.8 mm. The clearance d between the outside height of the containing groove 12 and the stator is 0.1-0.35 mm. An O-ring 2 having a wire diameter of 2.0mm may be used, the proportional relationship a/b between the inner diameter a of the O-ring 2 and the outer diameter b of the housing groove 12 may be 0.6 to 0.85, the compression amount of the O-ring 2 may be 0.15 to 0.4mm, and the width c of the housing groove 12 may be 2.2 to 2.3 mm. The clearance d between the outside height of the containing groove 12 and the stator is 0.1-0.5 mm.

For the air bearing 1 with the diameter of the rotating shaft 3 of 36-50 mm, an O-ring 2 with the linear diameter of 2-3.5 can be used, the proportional relation between the inner diameter a of the O-ring 2 and the outer diameter b of the accommodating groove 12 is approximately 0.6-0.9, the radial compression amount of the O-ring 2 is 0.2-0.5 mm, and the width c of the accommodating groove 12 is 2.7-2.9 mm. The clearance d between the outside height of the containing groove 12 and the stator is 0.1-0.5 mm.

Further, the embodiment of the utility model provides a mode of adjusting the damping size is still provided.

1. Varying the number of O-rings

In special cases, such as the case of increasing the damping according to the rotor dynamics requirement, a plurality of O-rings 2 (see fig. 3 and 4) can be arranged at the relevant positions of the bearing (the number of O-rings 2 is positively correlated with the damping provided by the O-rings 2), so as to improve the damping characteristic of the bearing.

2. Changing the diameter of an O-ring

(1) The radial thickness of the O-rings 2 on both sides increases: and meanwhile, the outer diameters of the O-shaped rings 2 on the two sides are increased, so that the compression amount of the O-shaped rings 2 can be increased, and the damping of the O-shaped rings is improved.

(2) Only the radial thickness of the one-sided O-ring 2 is increased: only the outer diameter of the one-side O-ring 2 is increased, so that when the O-ring 2 on the non-expansion side is normally compressed by the stator having the same diameter, the expansion-side O-ring 2 is compressed more than the non-expansion side, thereby improving the damping.

(3) The radial thickness of the O-shaped rings 2 on the two sides is not changed: referring to fig. 6, the outer diameter of the one-side support arm of the air bearing 1 is increased to enlarge the inner and outer diameters of the one-side O-ring 2 and the receiving groove 12, so that the damping can be improved by increasing the amount of compression of the enlarged-side O-ring 2 to be greater than that of the non-enlarged side when the non-enlarged-side O-ring 2 is normally compressed by the same-diameter stator. Conversely, the damping may be reduced.

3. Changing the axial length of an O-ring

As the axial length of the O-ring 2 is increased, the volume compressed between the O-ring and the stator is also increased, and the damping of the O-ring can be improved. When the axial length is sufficiently large, the O-ring 2 is converted into a cylindrical ring, and the hollow cylindrical rubber damper 4 can be obtained:

as shown in fig. 7, a ring of hollow cylindrical rubber dampers 4 is provided between the air bearing 1 and the air bearing housing, and the thickness and material of the hollow cylindrical rubber dampers 4 need to be designed according to the bearing performance. The hollow cylindrical rubber damper 4 can generate different rigidity damping characteristics when different thicknesses and different materials are selected.

Preferably, the present embodiment further comprises a bearing seat 13, the hollow cylindrical rubber damper 4 is fixed in the bearing seat 13 of the air bearing 1, and the bearing seat 13 is fixed on the inner wall of the stator.

In the above embodiment of the present invention, the O-ring 2 or the hollow cylindrical rubber damper 4 is made of rubber or metal rubber. Specifically, the rubber can be selected from nitrile rubber, fluorine rubber and silica gel, and fluorine rubber is preferred.

The embodiment of the utility model provides a still provide a modular damper, constitute the modular damper structure of this embodiment promptly when second attenuator 82 adopts the metal damper.

As shown in fig. 8, the adaptive elastic material damper, the first damper 81 is an O-ring 2, the second damper is a 82-metal damper, and a metal damper, such as a metal foil damper 5, or other various metal dampers, is disposed outside the air bearing 1 using the O-ring 2.

Specifically, an annular air cavity 11 is arranged on the outer wall of the air bearing 1, two ends of the annular air cavity 11 are respectively provided with at least one accommodating groove 12 around the outer wall of the bearing, an O-ring 2 is arranged in the accommodating groove 12, and the O-ring 2 is sleeved in the accommodating groove 12 and is higher than the accommodating groove 12; the metal damper is established to the stator endotheca, and air bearing 1 sets up in the metal damper, and has the space between O type ring 2 on the air bearing 1 and the metal damper.

Preferably, the metal damper is a metal foil damper 5.

In the present embodiment, the metal foil damper 5 includes at least one boss portion 51 and a support portion 52.

Referring to fig. 8, a stator, a metal foil damper 5 and a hollow cylindrical pressure cylinder 6 are sequentially nested from outside to inside, an air bearing 1 is arranged in the hollow cylindrical pressure cylinder 6, a rotating shaft 3 is sleeved in the air bearing 1, an annular air cavity 11 is arranged on the outer wall of the air bearing 1, at least one accommodating groove 12 is formed in the two ends of the annular air cavity 11 respectively surrounding the outer wall of the bearing, an O-ring 2 is arranged in the accommodating groove 12, the O-ring 2 is arranged in the accommodating groove 12 and higher than the accommodating groove 12, and the convex portion 51 and the supporting portion 52 of the metal foil damper 5 respectively support the outer wall of the hollow cylindrical pressure cylinder 6 and the inner wall of the stator.

In this embodiment, the O-ring 2 can adjust the distance between the air bearing 1 and the hollow cylindrical pressure cylinder 6 by deformation, and further adjust the distance between the air bearing 1 and the rotor 3; the metal foil damper 5 can adjust the distance between the hollow cylindrical pressure cylinder 6 and the stator by deformation, adjust the distance between the air bearing 1 and the hollow cylindrical pressure cylinder 6, and further adjust the distance between the air bearing 1 and the rotor 3.

In order to prevent the metal foil damper 5 and the hollow cylindrical pressing cylinder 6 from moving axially, the metal foil damper 5, the stator and the hollow cylindrical pressing cylinder 6 can be axially limited.

Preferably, the limiting mode is a pin connection, so as to ensure that the metal foil damper 5 can deform in the radial direction and play a role of a damper while being limited in the axial direction. Specifically, the pins 7 are uniformly arranged in a circle along a certain cross section. One end of the pin 7 is fixed on the outer wall of the hollow cylindrical pressing cylinder 6, and the other end of the pin is arranged outside the stator and has a gap with the outer wall of the stator.

The utility model discloses the attenuator that provides in the above-mentioned embodiment has following characteristics:

the damper of the embodiment is applied to the air bearing 1, the air bearing 1 is sleeved on the rotating shaft 3, the stator is sleeved outside the air bearing 1, and the damping effect is achieved between the air bearing 1 and the stator through deformation of elastic materials/structural deformation.

Before the air bearing 1 is started, a gap exists between the part of the damper close to the top of the stator and the stator, and the part at the bottom of the stator is contacted with the stator due to the action of gravity and is extruded and deformed.

Before the air bearing 1 is started, a gap exists between the part of the damper close to the top of the stator and the stator, and the part at the bottom of the stator is contacted with the stator due to the action of gravity and is extruded and deformed.

At the very start of the air bearing 1, the air between the air bearing 1 and the rotating shaft 3 is in a compressed state, and a pressure F1 exists. Damper deformation force F2. When the resonance mode is reached, the rotating shaft 3 approaches the bearing, so that F1 rises sharply, and F1> F2 is formed. When F1> F2, the damper deforms, so that the bearing moves towards the direction of the movement of the rotating shaft 3 actively and avoids the rotating shaft 3, and collision is avoided. The rotary shaft 3 transmits force to the damper through the interaction of the force, and the damper absorbs the resonance energy of the rotary shaft 3 through the deformation of the damper, so that the vibration energy is reduced, and the rotary shaft 3 is helped to rapidly pass through a resonance mode.

The damper can also play a role in absorbing the vibration energy of the rotating shaft 3 when the rotating shaft 3 vibrates. And under the condition that the rotating shaft 3 is eccentric, the bearing can move in a certain range, so that the direct collision between the rotating shaft 3 and the bearing can be avoided to the greatest extent. Before the rotating shaft 3 touches the bearing, the bearing can actively move a certain distance in the moving direction of the rotating shaft 3 to avoid the collision with the rotating shaft 3. This cooperative nature greatly facilitates the rapid passage of the shaft 3 through the resonant modes.

Fig. 9 shows the vibration frequency at different damping. Wherein, the abscissa RPM represents the rotation speed of the rotating shaft 3, the ordinate AMP represents the amplitude, the curve C0 is in a non-damping state, and the damping of the curves C1, C2 and C3 is increased from small to large. It can be seen that as the damping increases, the shaft 3 is most smooth when passing through the critical speed at C3.

The above description is only a preferred embodiment of the application and is illustrative of the principles of the technology employed. It will be understood by those skilled in the art that the scope of the present invention is not limited to the specific combination of the above-mentioned features, but also covers other embodiments formed by any combination of the above-mentioned features or their equivalents without departing from the spirit of the present invention. For example, the features described above have similar functions to (but are not limited to) those disclosed in this application.

Claims (10)

1. The utility model provides an air bearing who contains self-adaptation elastic material attenuator for install between pivot and stator, its characterized in that, the cover is equipped with the intermediate junction spare between air bearing and the stator, set up at least one first attenuator between air bearing and the intermediate junction spare, set up at least one second attenuator between intermediate junction spare and the stator, first attenuator is for having elastic O type ring or hollow cylindrical rubber damper.

2. An air bearing incorporating an adaptive elastic material damper according to claim 1, wherein the intermediate connecting member is a hollow cylindrical pressure cylinder.

3. An air bearing incorporating an adaptive elastic material damper according to claim 1, wherein an axial stop is provided between the intermediate connection member and the stator.

4. An air bearing including an adaptive elastic material damper according to claim 1, wherein said outer wall of said air bearing is provided with at least one receiving groove running parallel to its end face, said receiving groove being nested with said O-ring, said O-ring being higher than said receiving groove.

5. The air bearing of claim 4 wherein the number of receiving grooves is one, and the receiving grooves and the O-ring are disposed in the middle of the air bearing.

6. The air bearing including an adaptive elastic material damper according to claim 4, wherein at least one receiving groove and an O-ring are respectively disposed at both ends of the air bearing.

7. The air bearing with the adaptive elastic material damper as claimed in claim 1, wherein the outer wall of the air bearing is provided with an annular air chamber, two sides of the annular air chamber are respectively provided with at least one accommodating groove in parallel with the end surface of the annular air chamber in a surrounding manner, the accommodating groove is internally nested with the O-ring, and the O-ring is higher than the accommodating groove.

8. The air bearing with the adaptive elastic material damper as recited in claim 7, wherein the outer diameter of the outer wall of the bearing on one side of the annular air chamber is larger than the outer diameter of the outer wall of the bearing on the other side, and correspondingly, the inner diameter and the outer diameter of the O-ring and the accommodating groove on one side of the annular air chamber are larger than the inner diameter and the outer diameter of the O-ring and the accommodating groove on the other side of the annular air chamber; or the radial thickness of the O-shaped ring at one side of the annular air cavity is larger than that at the other side of the annular air cavity.

9. An air bearing incorporating an adaptive elastic material damper according to claim 1, wherein said hollow cylindrical rubber damper is fixed within an intermediate connecting member.

10. An air bearing with an adaptive elastic damper according to any one of claims 1 to 9, wherein the O-ring or hollow cylindrical rubber damper is made of rubber or metal rubber.

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