WO2021143415A1

WO2021143415A1 - Air bearing comprising adaptive damper

Info

Publication number: WO2021143415A1
Application number: PCT/CN2020/135900
Authority: WO
Inventors: 刘慕华
Original assignee: 至玥腾风科技集团有限公司
Priority date: 2020-01-19
Filing date: 2020-12-11
Publication date: 2021-07-22
Also published as: CN111120514A

Abstract

An air bearing (1) comprising an adaptive damper, used for being mounted between a rotating shaft and a stator. A hollow cylindrical intermediate connector (83) is sleeved between the air bearing (1) and the stator; at least one first damper (81) is provided between the air bearing (1) and the intermediate connector (83); at least one second damper (82) is provided between the intermediate connector (83) and the stator. The air bearing can solve the technical problems of collision and jamming between the bearing and the stator, and how to adjust damping and eliminate resonance.

Description

An air bearing containing an adaptive damper

Technical field

The invention relates to the technical field of bearings, in particular to an air bearing containing an adaptive damper.

Background technique

Non-contact bearings, due to their low friction coefficient, low friction torque, and high motion accuracy, are becoming more and more common in some high-speed occasions. However, compared with contact mechanical bearings, non-contact bearings have a small bearing clearance and are more difficult to process.

For example, for non-contact radial bearings, the gap between the bearing and the stator is very narrow, which requires both the stator and the bearing to have high machining accuracy and assembly accuracy. Otherwise, collisions and jams are prone to occur. The bearings cause wear and damage.

In non-contact bearings, such as air bearings, when the air bearing is just started, the air between the bearing and the rotor is compressed and there is pressure. When the excitation frequency generated by the unbalanced force of the rotor is consistent with the natural frequency of the rotor and its supporting system, it will Causes resonance, which can cause system noise and vibration to be serious, and parts are scrapped.

Summary of the invention

In order to solve the above technical problems, the purpose of the present invention is to provide an air bearing including an adaptive damper, which can solve the technical problems of collision and jam between the bearing and the stator, how to adjust the damping and eliminate resonance.

The technical scheme of the present invention is as follows:

An air bearing containing an adaptive damper for installation between a rotating shaft and a stator, a hollow cylindrical intermediate connecting piece is sleeved between the air bearing and the stator, and the air bearing and the intermediate connecting piece are sleeved between the air bearing and the stator. At least one first damper is provided, and at least one second damper is provided between the intermediate connecting piece and the stator.

Further, the first damper or the second damper is one of an O-ring with elasticity, a hollow cylindrical rubber damper, and a metal damper.

Further, the first damper is an O-ring with elasticity, and the second damper is a metal damper;

An annular air cavity is provided on the outer wall of the air bearing, and at least one accommodating groove is opened around the outer wall of the bearing on both sides of the annular air cavity, and the O-ring is arranged in the accommodating groove. Sleeve in the accommodating groove and higher than the accommodating groove; the top of the O-ring supports the inner wall of the intermediate connector;

The metal damper includes a foil, the foil includes at least one protruding part and a supporting part, and the protruding part and the supporting part of the foil respectively support the outer wall of the intermediate connector and the inner wall of the stator.

Further, an axial limiting member is provided between the intermediate connecting member and the stator;

The axial limiter is a pin, one end of the pin is fixed to the outer wall of the intermediate connecting member, passes through the foil, and the other end is arranged outside the stator with a gap between the pin and the outer wall of the stator.

Further, when the O-ring is not compressed, the cross-section is circular, rectangular, trapezoidal, or elliptical.

Further, when the diameter of the rotating shaft is 20-30 mm, the O-ring wire diameter is 1.2-1.8 mm, and the ratio between the inner diameter a of the O-ring and the outer diameter b of the accommodating groove is a/b=0.7-0.85 , The radial compression of the O-ring is 0.25～0.35mm, the value of the accommodating groove width c is 1.7～1.8mm, and the gap d between the outer height of the accommodating groove and the stator is 0.1～0.35mm.

Further, when the diameter of the rotating shaft is 30-50mm, the diameter of the O-ring is 1.3-2mm, and the ratio between the inner diameter a of the O-ring and the diameter b of the accommodating groove is a/b=0.7-0.85, O The radial compression of the ring is 0.25～0.35mm, the value of the accommodating groove width c is 1.7～1.8mm, and the gap d between the height of the outside of the accommodating groove and the stator is 0.1～0.35mm;

Or, the diameter of the O-ring is 2mm, the ratio between the inner diameter a of the O-ring and the outer diameter b of the accommodating groove is a/b=0.6～0.85, the compression of the O-ring is 0.15～0.4mm, The value of the slot width c is 2.2 to 2.3 mm, and the gap d between the outer height of the containing slot and the stator is 0.1 to 0.5 mm.

Further, when the diameter of the rotating shaft is 36-50mm, the diameter of the O-ring is 2～3.5mm, and the ratio between the inner diameter a of the O-ring and the outer diameter b of the accommodating groove is a/b=0.6～0.9 , The radial compression of the O-ring is 0.2-0.5mm, the value of the accommodating slot width c is 2.7-2.9mm, and the gap d between the outer height of the accommodating slot and the stator is 0.1-0.5mm.

Further, the radial thickness of the O-ring on one side of the annular air cavity is greater than the radial thickness of the O-ring on the other side of the annular air cavity.

Further, the outer diameter of the outer bearing wall on one side of the air bearing is larger than the outer diameter of the outer bearing wall on the other side. Correspondingly, the inner diameter and outer diameter of the O-ring and the accommodating groove on one side of the air bearing are larger than the other side. The inner and outer diameters of the O-ring and the accommodating groove.

Further, the O-ring is made of rubber or metal rubber.

The beneficial effects of the present invention:

1. The air bearing structure of the present invention can automatically match the matching gap between the stator and the air bearing without changing the structure and size of the air bearing. It can solve the collision, jamming, and adjustment between the bearing and the stator. Technical problems of damping and eliminating resonance: For example, when the first damper of the present invention is an O-ring, the distance between the air bearing and the hollow cylindrical pressure cylinder can be adjusted through deformation, and then the distance between the air bearing and the rotating shaft can be adjusted; When the second damper is a metal damper, the distance between the hollow cylindrical pressure cylinder and the stator can be adjusted by deformation, and then the distance between the air bearing and the hollow cylindrical pressure cylinder can be adjusted, and the distance between the air bearing and the rotating shaft can be adjusted .

2. When the first damper of the present invention is an O-ring, it can play a role in sealing air. It has a very large role in the hydrostatic bearing. It can ensure that the external air supply can enter the bearing through the orifice, and can maintain a certain level The air supply pressure will not leak.

3. The damper of the present invention can absorb vibration energy through its own deformation. The installation of a suitable damper can completely absorb rotor vibration and vortex (vibration caused by the rotor itself, such as vibration caused by dynamic balance or critical speed). Or most of the absorption can help the rotor to smoothly pass the critical speed or reduce the requirement of dynamic balance level, or it can play a damping role when there is interference from the outside, and keep the rotor and the bearing from colliding and play a protective role.

4. Because the working gap is very small, the air bearing has extremely high requirements for coaxiality, so the processing requirements are extremely high. When the air bearing starts to work, there is a certain pressure between the rotor and the bearing. When the damper is designed With proper selection, when the air pressure in the bearing is higher than the deformation pressure of the damper, the rotor can automatically correct the coaxiality. Therefore, the damper greatly reduces the air bearing’s requirements for coaxiality, which also reduces the processing The requirements of equipment and processing technology have greatly reduced production costs;

When the hydrostatic bearing is turned on, due to the high rigidity between the bearing and the rotor, the bearing is forced to remain coaxial with the rotor, and the tolerance between the bearing and the stator is offset by the compression of the damper, which eliminates the need for human intervention. At the finishing level, the coaxiality and roundness are forcibly ensured, which greatly reduces the accuracy and difficulty of bearing processing.

5. In the present invention, the rotor transmits force to the damper through force interaction, and the damper absorbs the energy of the rotor resonance through its own deformation, which reduces the vibration energy and helps the rotor to quickly pass through the resonance mode.

6. The damper of the present invention is used to make a floating platform (floating table effect), so that it can not only translate along the direction coaxial with the stator and rotor, but also freely warp. The gap between the bearing and the stator is greater than the gap between the bearing and the rotor. At the same time, the support stiffness between the bearing and the stator is much lower than the support stiffness between the bearing and the rotor. The coaxiality or roundness of the two bearings on the stator, etc. The accuracy cannot be completely coaxial due to process conditions. In the static state, the rotor-bearing-stator is actually stuck. This state realizes the function of self-locking when the rotor does not need to rotate, avoiding The rotor repeatedly bumps against the bearing due to external vibration during transportation, which greatly improves the static reliability and total life of the system.

Description of the drawings

Figure 1 is a schematic diagram of the structure of an adaptive damper;

Figure 2 is a schematic structural view of an embodiment in which an O-ring is provided on the air bearing;

Figure 3 is a schematic structural view of another embodiment in which an O-ring is provided on the air bearing;

Figure 4 is a schematic structural view of another embodiment in which an O-ring is provided on the air bearing;

Figure 5 is a schematic diagram illustrating the size of the O-ring;

Figure 6 is a schematic diagram of the damper structure when the diameter of the air bearing support arm is different;

Figure 7 is a schematic diagram of the installation structure of the hollow cylindrical rubber damper;

Figure 8 is a schematic diagram of the specific structure of the adaptive damper;

Figure 9 shows the relationship between rotor speed and vibration frequency under different damping effects.

Detailed ways

In order to better understand the technical solutions of the present invention, the present invention will be further described below in conjunction with specific embodiments and the accompanying drawings of the specification.

As shown in FIG. 1, it is an air bearing including an adaptive damper provided by an embodiment of the present invention.

An intermediate connecting piece 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 connecting piece 83, and at least one second damper is arranged between the intermediate connecting piece 83 and the stator.器82.

The first damper 81 or the second damper 82 is one of an elastic O-ring 2, a hollow cylindrical rubber damper 4, and a metal damper. It includes the following nine implementation methods:

(1) The first damper 81 is an O-ring 2, and the second damper 82 is an O-ring 2: both the outer wall of the air bearing 1 and the outer wall of the intermediate connecting piece 83 are provided with accommodating grooves 12, and An O-ring 2 is nested in the accommodating 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 intermediate connecting piece 83, and the bearing seat is convex at both ends, In the middle recess, the hollow cylindrical rubber damper 4 is nested in the middle recess of the bearing seat; the outer wall of the middle connecting member 83 is provided with a containing groove 12 and an O-ring 2 is nested in the containing groove 12.

(3) The first damper 81 is a metal damper, especially a metal foil damper 5, and the second damper 82 is an O-ring 2: The metal foil damper 5 includes at least one protrusion and The supporting portion; the raised portion and the supporting portion of the metal foil damper 5 respectively support the outer wall of the air bearing 1 and the inner wall of the intermediate connecting piece 83, the outer wall of the intermediate connecting piece 83 is opened with a containing groove 12, and in the containing groove 12 Nested O-ring 2.

(4) The first damper 81 is an O-ring 2, and the second damper 82 is a hollow cylindrical rubber damper 4: an accommodating groove 12 is provided on the outer wall of the air bearing 1, and an O is nested in the accommodating groove 12 Ring 2; a bearing seat is fixed in the stator, and the two ends of the bearing seat are convex and the middle is recessed; the hollow cylindrical rubber damper 4 is nested in the middle recess of the bearing seat.

(5) The first damper 81 and the second damper 82 are both hollow cylindrical rubber dampers 4: the stator and the inner wall of the intermediate connecting piece 83 are both fixed with a bearing seat, and both ends of the bearing seat are convex and the middle is recessed; The hollow cylindrical rubber damper 4 is nested in the middle recess of the bearing seat.

(6) The first damper 81 is a metal damper, especially a metal foil damper 5, and the second damper 82 is a hollow cylindrical rubber damper 4: The metal foil damper 5 includes at least one convex The raised portion and the supporting portion, the raised portion and the supporting portion of the metal foil damper 5 respectively support the outer wall of the air bearing 1 and the inner wall of the intermediate connector; a bearing seat is fixed in the stator, and the bearing seat is convex at both ends and recessed in the middle The hollow cylindrical rubber damper 4 is nested in the middle recess of the bearing seat.

(7) The first damper 81 is an O-ring 2, and the second damper 82 is a metal damper, especially a metal foil damper 5: a housing groove 12 is provided on the outer wall of the air bearing 1, and the housing groove 12 nested O-ring 2; the metal foil damper 5 includes at least one raised portion and a supporting portion, and the raised portion and the supporting portion of the metal foil damper respectively support the outer wall of the intermediate connector 83 and the stator Inner wall.

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

(9) The first damper 81 and the second damper 82 are metal dampers, especially the metal foil damper 5: the metal foil damper 5 of the first damper 81 includes at least one protrusion And the supporting part, the convex part and the supporting part respectively support the outer wall of the air bearing and the inner wall of the intermediate connecting piece 82; the metal foil damper 5 of the second damper 82 includes at least one convex part and a supporting part, which is convex The supporting portion and the supporting portion respectively support the outer wall of the intermediate connector 83 and the inner wall of the stator.

Further, the metal foil damper 5 is a one-piece corrugated structure, and the above-mentioned “supporting” method of the protruding part and the supporting part of the metal foil damper 5 is fixed. For example, the protruding portion 51 and the supporting portion 52 are respectively fixed on the outer wall of the hollow cylindrical pressure cylinder 6 and the inner wall of the stator.

For various situations in the above-mentioned embodiments, through the arrangement of the intermediate connector 83, the matching gap 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 pressing cylinder.

In order to prevent the axial movement of the intermediate connecting piece 83, the intermediate connecting piece 83 and the stator and air bearing 1 can be axially limited to ensure that the intermediate connecting piece 83 can transmit deformation force in the radial direction while being axially limited. , Play a role in adjusting the damping.

The embodiment of the present invention also provides an adaptive elastic material damper structure, that is, an O-ring 2 structure.

Specifically, an annular air cavity 11 is provided on the outer wall of the air bearing 1, and at least one accommodating groove 12 is opened at both ends of the annular air cavity 11 around the outer wall of the bearing, and an O-ring 2 is arranged in the accommodating groove 12. The ring 2 is circumferentially 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 provided by the present invention. In this embodiment, an O-ring 2 is provided on both sides of the air bearing 1, which can simultaneously play the role of air sealing and shock absorption, and can also reduce the coaxiality requirement. Specifically, FIG. 2 shows a symmetrically arranged air bearing 1, and an O-ring 2 is provided at each end of the annular air cavity 11. The annular air cavity 11 communicates with the gap between the rotating shaft and the air bearing through an air hole (not shown in the figure).

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

As shown in FIG. 4, it is another embodiment of the O-ring 2 arrangement provided by the present invention. In this embodiment, the air bearing 1 is symmetrically arranged, and two O-rings 2 are provided at each end of the annular air cavity 11.

Preferably, the cross-section of the O-ring 2 when it is not compressed can be circular, or rectangular, trapezoidal, elliptical, or the like.

The cross-section of the O-ring 2 shown in Fig. 5 is circular and becomes elliptical after compression. According to the figure:

For the air bearing 1 with a diameter of 20-30mm of the shaft 3, an O-ring 2 with a wire diameter of 1.2-1.8mm can be used. The ratio between the inner diameter a of the O-ring 2 and the outer diameter b of the accommodating groove 12 is a/b=0.7 ~0.85, the radial compression of the O-ring 2 is 0.25~0.35mm, and the value of the width c of the accommodating groove 12 is 1.7~1.8mm. The gap d between the outer height of the accommodating slot 12 and the stator is between 0.1 and 0.35 mm. The gap size is related to the radial vibration amplitude of the rotor 3 required by the machine. The smaller the gap, the radial vibration amplitude of the rotating shaft 3 The smaller the value, the larger the gap, and the larger the radial vibration amplitude of the shaft 3 is.

For the air bearing 1 with a diameter of 30-50mm of the shaft 3, an O-ring 2 with a wire diameter of 1.3-2mm can be used. The ratio between the inner diameter a of the O-ring 2 and the diameter b of the accommodating groove 12 is a/b=0.7～0.85 , The radial compression of the O-ring 2 is 0.25 to 0.35 mm, and the value of the width c of the accommodating groove 12 is 1.7 to 1.8 mm. The gap d between the outer height of the accommodating slot 12 and the stator is 0.1 to 0.35 mm. O-ring 2 with a wire diameter of 2.0mm can also be used. The ratio between the inner diameter a of the O-ring 2 and the outer diameter b of the accommodating groove 12 is a/b=0.6～0.85, and the compression amount of the O-ring 2 is 0.15～ 0.4mm, the value of the width c of the accommodating groove 12 is 2.2-2.3mm. The gap d between the outer height of the accommodating slot 12 and the stator is between 0.1 mm and 0.5 mm.

For the air bearing 1 with a diameter of 36-50mm of the rotating shaft 3, an O-ring 2 with a wire diameter of 2 to 3.5 can be used. The ratio between the inner diameter a of the O-ring 2 and the outer diameter b of the accommodating groove 12 is approximately a/b= 0.6-0.9, the radial compression of the O-ring 2 is 0.2-0.5mm, and the value of the width c of the accommodating groove 12 is 2.7-2.9mm. The gap d between the outer height of the accommodating slot 12 and the stator is between 0.1 mm and 0.5 mm.

Further, the embodiment of the present invention also provides a way to adjust the magnitude of the damping.

1. Change the number of O-rings

In some special occasions, such as the need to increase damping according to the rotor dynamics requirements, multiple O-rings 2 (see Figures 3 and 4) can be set at the relevant positions of the bearing (the number of O-rings 2 and the number of O-rings The damping provided by the ring 2 is positively correlated) to improve the damping characteristics of the bearing.

2. Change the O-ring diameter

(1) Increase in the radial thickness of the O-rings 2 on both sides: At the same time, increasing the outer diameter of the O-rings 2 on both sides can increase the compression of the O-rings 2 and improve their damping.

(2) Only increase the radial thickness of the single-sided O-ring 2: only increase the outer diameter of the single-sided O-ring 2, so that under the action of the stator of the same diameter, when the non-expanded side O-ring 2 is normally compressed, The expanded side O-ring 2 is compressed more than the non-expanded side, which can improve its damping.

(3) The radial thickness of the O-rings 2 on both sides remains the same: see Figure 6, increase the outer diameter of the single-sided support arm of the air bearing 1, and expand the inner and outer diameters of the single-sided O-ring 2 and the accommodating groove 12 In this way, under the action of the same diameter stator, when the non-expanded side O-ring 2 is normally compressed, the expanded side O-ring 2 is compressed more than the non-expanded side, which can improve the damping. On the contrary, the damping can be reduced.

3. Change the axial length of the O-ring

As the axial length of the O-ring 2 increases, the volume compressed between it and the stator also increases, which can improve its damping. When the axial length is large enough, the O-ring 2 will be transformed into a cylindrical ring, and a hollow cylindrical rubber damper 4 can be obtained:

As shown in Fig. 7, a ring of hollow cylindrical rubber damper 4 is arranged between the air bearing 1 and the air bearing seat. The thickness and material of the hollow cylindrical rubber damper 4 need to be designed according to the bearing performance. The hollow cylindrical rubber damper 4 can produce different stiffness and damping characteristics when different thicknesses and different materials are selected.

Preferably, this embodiment further includes 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-mentioned embodiment of the present invention, the material of the O-ring 2 or the hollow cylindrical rubber damper 4 is rubber or metal rubber. Specifically, the rubber can be selected from nitrile butadiene rubber, fluorine rubber, and silica gel, preferably fluorine rubber.

The embodiment of the present invention also provides an adaptive metal damper structure.

As shown in FIG. 8, the metal foil damper 5 is used as the metal damper.

Specifically, an annular air cavity 11 is provided on the outer wall of the air bearing 1, and at least one accommodating groove 12 is opened at both ends of the annular air cavity 11 around the outer wall of the bearing, and an O-ring 2 is arranged in the accommodating groove 12. The ring 2 is sleeved in the accommodating groove 12 and is higher than the accommodating groove 12; the stator is sleeved with a metal damper, the air bearing 1 is arranged in the metal damper, and the O-ring 2 on the air bearing 1 and There are gaps between the metal dampers, and the metal dampers are metal foil damper 5.

In this embodiment, the metal foil damper 5 includes at least one protruding portion 51 and a supporting portion 52.

Referring to Figure 8, the stator, the metal foil damper 5 and the hollow cylindrical pressure cylinder 6 are nested in order from the outside to the inside. The hollow cylindrical pressure cylinder 6 is provided with an air bearing 1, and the air bearing 1 is sleeved with a rotating shaft 3. An annular air cavity 11 is provided on the outer wall of the air bearing 1, and at least one accommodating groove 12 is opened at both ends of the annular air cavity 11 around the outer wall of the bearing. An O-ring 2 is arranged in the accommodating groove 12, and the O-ring 2 is arranged In the accommodating groove 12 and higher than the accommodating groove 12, the raised portion 51 and the supporting portion 52 of the metal foil damper 5 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 through deformation, thereby adjusting the distance between the air bearing 1 and the rotor 3; the metal foil damper 5 can be deformed The distance between the hollow cylindrical pressing cylinder 6 and the stator is adjusted, the distance between the air bearing 1 and the hollow cylindrical pressing cylinder 6 is adjusted, and the distance between the air bearing 1 and the rotor 3 is adjusted.

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

Preferably, the limiting method is pin connection to ensure that the metal foil damper 5 can be deformed in the radial direction while being axially limited, so as to function as a damper. Specifically, the pins 7 are uniformly distributed in a circle along a certain cross section. One end of the pin 7 is fixed on the outer wall of the hollow cylindrical pressure cylinder 6, passing through the metal foil damper 5, and the other end of the pin cap is arranged outside the stator, leaving a gap with the outer wall of the stator.

The damper provided in the above embodiment of the present invention has the following characteristics:

The damper of the above embodiment is applied to an air bearing 1. An air bearing 1 is sleeved on the rotating shaft 3, and a setting element is sleeved on the outside of the air bearing 1, and the air bearing 1 and the stator are damped by elastic material deformation/structural deformation.

Before the air bearing 1 is started, there is a gap between the part of the damper near the top of the stator and the stator, and the part at the bottom of the stator is in contact with the stator due to gravity, and is compressed and deformed.

Before the air bearing 1 is activated, there is a gap between the part of the damper near the top of the stator and the stator, and the part at the bottom of the stator is in contact with the stator due to the action of gravity and is compressed and deformed.

When the air bearing 1 is just started, the air between the air bearing 1 and the rotating shaft 3 is in a compressed state, and there is a pressure F1. Damper deformation force F2. When the resonance mode is about to be reached, the shaft 3 will approach the bearing, causing F1 to rise sharply, making F1>>F2. When F1>F2, the damper will deform, causing the bearing to "actively" move in the direction of the rotation shaft 3 and "dodge" the rotation shaft 3, avoiding collisions. The rotating shaft 3 transmits the force to the damper through the interaction of the force, and the damper absorbs the energy of the resonance of the rotating shaft 3 through its own deformation, so that the vibration energy is reduced, and the rotating shaft 3 can quickly pass through the resonance mode.

When the rotating shaft 3 vibrates, the damper can also play a role in absorbing the vibration energy of the rotating shaft 3. And when there is an eccentricity of the rotating shaft 3, since the bearing can move within a certain range, 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 will "actively" move a certain distance in the direction of movement of the rotating shaft 3, avoiding the collision with the rotating shaft 3. This cooperative characteristic is very helpful for the rotating shaft 3 to quickly pass through the resonance mode.

Figure 9 shows the vibration frequency under different damping. Among them, the abscissa RPM represents the rotation speed of the shaft 3, the ordinate AMP represents the amplitude, the curve C0 is in an undamped state, and the damping of the curves C1, C2, and C3 is from small to large. It can be seen that as the damping increases, the shaft 3 is the most stable when it passes the critical speed under the condition of C3.

The above description is only a preferred embodiment of the present application and an explanation of the applied technical principles. Those skilled in the art should understand that the scope of the invention involved in this application is not limited to the technical solution formed by the specific combination of the above technical features, and should also cover the above technical features without departing from the inventive concept. Or other technical solutions formed by any combination of its equivalent features. For example, the above-mentioned features have similar functions as those disclosed in this application (but not limited to).

Claims

An air bearing containing an adaptive damper for installation between a rotating shaft and a stator, characterized in that a hollow cylindrical intermediate connecting piece is sleeved between the air bearing and the stator, and the air bearing and the intermediate At least one first damper is arranged between the connecting pieces, and at least one second damper is arranged between the intermediate connecting piece and the stator.
The air bearing containing an adaptive damper according to claim 1, wherein the first damper or the second damper is an O-ring with elasticity, a hollow cylindrical rubber damper, or a metal damper. Kind of.
The air bearing containing an adaptive damper according to claim 1, wherein the first damper is an O-ring with elasticity, and the second damper is a metal damper;

An annular air cavity is provided on the outer wall of the air bearing, and at least one accommodating groove is opened around the outer wall of the bearing on both sides of the annular air cavity, and the O-ring is arranged in the accommodating groove. Sleeve in the accommodating groove and higher than the accommodating groove; the top of the O-ring supports the inner wall of the intermediate connector;

The metal damper includes a foil, the foil includes at least one protruding part and a supporting part, and the protruding part and the supporting part of the foil respectively support the outer wall of the intermediate connector and the inner wall of the stator.
The air bearing containing an adaptive damper according to claim 3, wherein an axial limiting member is provided between the intermediate connecting member and the stator;

The axial limiter is a pin, one end of the pin is fixed to the outer wall of the intermediate connecting member, passes through the foil, and the other end is arranged outside the stator with a gap between the pin and the outer wall of the stator.
The air bearing containing an adaptive damper according to claim 3, wherein the cross-section of the O-ring is circular, rectangular, trapezoidal, or elliptical when it is not compressed.
The air bearing comprising an adaptive damper according to claim 3, wherein when the diameter of the shaft is 20-30 mm, the diameter of the O-ring is 1.2-1.8 mm, and the inner diameter a of the O-ring is different from the housing diameter. The proportional relationship between the groove outer diameter b is a/b=0.7～0.85, the radial compression of the O-ring is 0.25～0.35mm, the value of the accommodating groove width c is 1.7～1.8mm, and the outside height of the accommodating groove The gap d between the stator and the stator is 0.1 to 0.35 mm.
The air bearing containing an adaptive damper according to claim 3, wherein when the diameter of the rotating shaft is 30-50 mm, the diameter of the O-ring is 1.3-2 mm, and the inner diameter a of the O-ring and the accommodating groove The proportional relationship between the diameter b is a/b=0.7～0.85, the radial compression of the O-ring is 0.25～0.35mm, the value of the accommodating groove width c is 1.7～1.8mm, and the outer height of the accommodating groove is the same as that of the stator The gap d between them is 0.1～0.35mm;

Or, the diameter of the O-ring is 2mm, the ratio between the inner diameter a of the O-ring and the outer diameter b of the accommodating groove is a/b=0.6～0.85, the compression of the O-ring is 0.15～0.4mm, The value of the slot width c is 2.2 to 2.3 mm, and the gap d between the outer height of the containing slot and the stator is 0.1 to 0.5 mm.
The air bearing containing an adaptive damper according to claim 3, wherein when the diameter of the rotating shaft is 36-50mm, the diameter of the O-ring is 2～3.5mm, and the inner diameter a of the O-ring is different from that of the housing. The proportional relationship between the groove outer diameter b is a/b=0.6～0.9, the radial compression of the O-ring is 0.2～0.5mm, the value of the accommodating groove width c is 2.7～2.9mm, and the outer height of the accommodating groove is equal to The gap d between the stators is 0.1 to 0.5 mm.
The air bearing containing an adaptive damper according to claim 3, wherein the radial thickness of the O-ring on one side of the annular air cavity is greater than the radial thickness of the O-ring on the other side of the annular air cavity.
The air bearing containing an adaptive damper according to claim 3, wherein the outer diameter of the outer bearing wall on one side of the air bearing is larger than the outer diameter of the outer bearing wall on the other side, and correspondingly, the outer diameter of the bearing outer wall on one side of the air bearing The inner and outer diameters of the O-ring and the accommodating groove are larger than the inner and outer diameters of the O-ring and the accommodating groove on the other side.
The air bearing containing an adaptive damper according to claim 3, wherein the O-ring is made of rubber or metal rubber.