CN111120514A - Air bearing comprising self-adaptive damper - Google Patents
Air bearing comprising self-adaptive damper Download PDFInfo
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- CN111120514A CN111120514A CN202010062941.3A CN202010062941A CN111120514A CN 111120514 A CN111120514 A CN 111120514A CN 202010062941 A CN202010062941 A CN 202010062941A CN 111120514 A CN111120514 A CN 111120514A
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- ring
- damper
- air bearing
- stator
- accommodating groove
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/08—Rigid support of bearing units; Housings, e.g. caps, covers for spindles
- F16C35/10—Rigid support of bearing units; Housings, e.g. caps, covers for spindles with sliding-contact bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
- F16C41/04—Preventing damage to bearings during storage or transport thereof or when otherwise out of use
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
- F16F15/073—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs using only leaf springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal
Abstract
The invention provides an air bearing comprising a self-adaptive damper, which is used for being arranged between a rotating shaft and a stator, wherein a hollow cylindrical middle connecting piece is sleeved between the air bearing and the stator, at least one first damper is arranged between the air bearing and the middle connecting piece, and at least one second damper is arranged between the middle connecting piece and the stator. The invention can solve the technical problems of collision and blocking between the bearing and the stator, how to adjust damping and eliminate resonance.
Description
Technical Field
The invention relates to the technical field of bearings, in particular to an air bearing comprising a self-adaptive damper.
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 above technical problems, an object of the present invention is to provide an air bearing including an adaptive damper, which can solve the technical problems of collision and seizure between the bearing and a stator, how to adjust damping, and how to eliminate resonance.
The technical scheme of the invention is as follows:
the utility model provides an air bearing who contains self-adaptation attenuator for install between pivot and stator, the cover is equipped with hollow tube-shape 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.
Further, the first damper or the second damper is one of an elastic O-ring, a hollow cylindrical rubber damper, and a metal damper.
Further, the first damper is an elastic O-shaped ring, and the second damper is a metal damper;
an annular air cavity is arranged on the outer wall of the air bearing, at least one accommodating groove is formed in the two sides of the annular air cavity respectively around the outer wall of the bearing, the O-shaped ring is arranged in the accommodating groove, and the O-shaped ring is annularly sleeved in the accommodating groove and is higher than the accommodating groove; the top of the O-ring supports the inner wall of the intermediate connector;
the metal damper comprises a foil, the foil comprises at least one boss and a support, and the boss and the support of the foil support the outer wall of the middle connector and the inner wall of the stator respectively.
Further, an axial limiting piece is arranged between the middle connecting piece and the stator;
the axial limiting part is a pin, one end of the pin is fixed on the outer wall of the middle connecting piece and penetrates through the foil, and the other end of the pin is arranged outside the stator and has a gap with the outer wall of the stator.
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, when the diameter of the rotating shaft is 20-30 mm, the diameter of the O-ring is 1.2-1.8 mm, the proportional relation between the inner diameter a of the O-ring and the outer diameter b of the accommodating groove is that a/b is 0.7-0.85, the radial compression amount of the O-ring is 0.25-0.35 mm, the width c of the accommodating groove is 1.7-1.8 mm, and the clearance d between the outer height of the accommodating groove and the stator is 0.1-0.35 mm.
Further, when the diameter of the rotating shaft is 30-50 mm, the linear diameter of the O-ring is 1.3-2 mm, the proportional relation between the inner diameter a of the O-ring and the diameter b of the accommodating groove is that a/b is 0.7-0.85, the radial compression amount of the O-ring is 0.25-0.35 mm, the width c of the accommodating groove is 1.7-1.8 mm, and the clearance d between the height of the outer side of the accommodating groove and the stator is 0.1-0.35 mm;
or, the wire diameter of the O-ring is 2mm, the proportional relation between the inner diameter a of the O-ring and the outer diameter b of the containing groove is that a/b is 0.6-0.85, the compression amount of the O-ring is 0.15-0.4 mm, the width c of the containing groove is 2.2-2.3 mm, and the clearance d between the height of the outer side of the containing groove and the stator is 0.1-0.5 mm.
Further, when the diameter of the rotating shaft is 36-50 mm, the linear diameter of the O-ring is 2-3.5 mm, the proportional relation between the inner diameter a of the O-ring and the outer diameter b of the accommodating groove is that a/b is 0.6-0.9, the radial compression amount of the O-ring is 0.2-0.5 mm, the width c of the accommodating groove is 2.7-2.9 mm, and the clearance d between the height of the outer side of the accommodating groove and the stator is 0.1-0.5 mm.
Further, the radial thickness of the O-shaped ring on one side of the annular air cavity is larger than that of the O-shaped ring on the other side of the annular air cavity.
Further, the outer diameter of the outer wall of the bearing on one side of the air bearing is larger than the outer diameter of the outer wall of the bearing on the other side of the air bearing, and correspondingly, the inner diameter and the outer diameter of the O-shaped ring and the accommodating groove on one side of the air bearing are larger than the inner diameter and the outer diameter of the O-shaped ring and the accommodating groove on the other side of the air bearing.
Furthermore, the O-shaped ring is made of rubber or metal rubber.
The invention has the beneficial effects that:
1. the air bearing structure of the invention can automatically match the fit clearance between the stator and the air bearing under the condition of not changing the structure and the size of the air bearing, and can solve the technical problems of collision, blocking, damping adjustment and resonance elimination between the bearing and the stator: for example, when the first damper is an O-ring, the distance between the air bearing and the hollow cylindrical pressing cylinder can be adjusted through deformation, and then the distance between the air bearing and the rotating shaft can be adjusted; the second attenuator can be through the distance between deformation adjustment hollow cylindrical pressure section of thick bamboo and the stator when metal attenuator, and then adjusts the distance between air bearing and the hollow cylindrical pressure section of thick bamboo, and then adjusts the distance between air bearing and the pivot.
2. The first damper can play a role in air sealing when being an O-ring, has a very large role in the hydrostatic bearing, can ensure that external air supply can enter the bearing through the throttling hole, and can keep certain air supply pressure from leaking.
3. The damper can absorb vibration energy through self deformation, and the proper damper can completely or mostly absorb rotor vibration and whirling motion (vibration caused by the rotor per se, such as vibration caused by a dynamic balance problem or critical rotating speed), so that the rotor can smoothly pass through the critical rotating speed or the requirement of dynamic balance grade is reduced, or the damper can play a role in damping when external interference vibration exists, so that collision between the rotor and a bearing is kept, and a protection effect is achieved.
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. In the invention, the rotor transmits force to the damper through the interaction of the force, and the damper absorbs the energy of rotor resonance through the deformation of the damper, so that the vibration energy is reduced, and the rotor is helped to rapidly pass through a resonance mode.
6. The damper of the invention is adopted to manufacture a floating platform (floating platform effect), so that the floating platform can not only translate along the direction coaxial with the stator and the rotor, but also can freely tilt. 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 diagram of a specific structure of the 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 scheme of the invention, the invention is further explained by combining the specific embodiment and the attached drawings of the specification.
As shown in fig. 1, an air bearing including an adaptive damper is provided according to 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 82 is arranged between the intermediate connecting piece 83 and the stator.
The first damper 81 or 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 nine 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 a metal damper, particularly a metal foil damper 5, and the second damper 82 is an O-ring 2: the metal foil damper 5 includes at least one boss and a support; the convex part and the supporting part 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 provided with an accommodating groove 12, and the O-shaped ring 2 is nested in the accommodating groove 12.
(4) 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.
(5) 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.
(6) The first damper 81 is a metal damper, in particular, a metal foil damper 5, and the second damper 82 is a hollow cylindrical rubber damper 4: the metal foil damper 5 comprises at least one convex part and a supporting part, and the convex part and the supporting part of the metal foil damper 5 respectively support the outer wall of the air bearing 1 and the inner wall of the middle connecting piece; the stator internal fixation has the bearing frame, the bearing frame both ends are protruding, the middle is sunken, hollow cylindrical rubber damper 4 nests in the middle depressed part of bearing frame.
(7) 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 83 and the inner wall of the stator, respectively.
(8) 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.
(9) The first damper 81 and the second damper 82 are metal dampers, in particular, metal foil dampers 5: the metal foil damper 5 of the first damper 81 includes at least one boss and support portion which support the outer wall of the air bearing and the inner wall of the intermediate connector 82, respectively; the metal foil damper 5 of the second damper 82 includes at least one protrusion and support portion which 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.
The embodiment of the invention also provides a self-adaptive elastic material damper structure, namely an O-shaped ring 2 structure.
Specifically, 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, and the O-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.
Fig. 2 shows an embodiment of the O-ring 2 of 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. The annular air chamber 11 communicates with the gap between the rotating shaft and the air bearing through an air hole (not shown in the figure).
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 of 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.
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 invention also provides a mode for adjusting the damping.
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 embodiments 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 invention also provides a self-adaptive metal damper structure.
As shown in fig. 8, the metal damper employs a metal foil damper 5.
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 and the metal damper on the air bearing 1, the metal damper is metal foil piece attenuator 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 a pin 7 is fixed on the outer wall of the hollow cylindrical pressing cylinder 6 and penetrates through the metal foil damper 5, and the other end of the pin is arranged outside the stator and has a gap with the outer wall of the stator.
The damper provided in the above embodiment of the present invention has the following features:
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 appreciated by a person skilled in the art that the scope of the invention as referred to in the present application is not limited to the embodiments with a specific combination of the above-mentioned features, but also covers other embodiments with any combination of the above-mentioned features or their equivalents without departing from the inventive concept. For example, the features described above have similar functions to (but are not limited to) those disclosed in this application.
Claims (11)
1. The utility model provides an air bearing for install between pivot and stator, its characterized in that, the cover is equipped with hollow tube-shape 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.
2. The air bearing including an adaptive damper according to claim 1, wherein the first damper or the second damper is one of an O-ring having elasticity, a hollow cylindrical rubber damper, and a metal damper.
3. The air bearing with the adaptive damper according to claim 1, wherein the first damper is an O-ring having elasticity, and the second damper is a metal damper;
an annular air cavity is arranged on the outer wall of the air bearing, at least one accommodating groove is formed in the two sides of the annular air cavity respectively around the outer wall of the bearing, the O-shaped ring is arranged in the accommodating groove, and the O-shaped ring is annularly sleeved in the accommodating groove and is higher than the accommodating groove; the top of the O-ring supports the inner wall of the intermediate connector;
the metal damper comprises a foil, the foil comprises at least one boss and a support, and the boss and the support of the foil support the outer wall of the middle connector and the inner wall of the stator respectively.
4. The air bearing with the adaptive damper according to claim 3, wherein an axial stopper is disposed between the intermediate connecting member and the stator;
the axial limiting part is a pin, one end of the pin is fixed on the outer wall of the middle connecting piece and penetrates through the foil, and the other end of the pin is arranged outside the stator and has a gap with the outer wall of the stator.
5. An air bearing including an adaptive damper according to claim 3, wherein the O-ring is circular or rectangular or trapezoidal or elliptical in cross-section when uncompressed.
6. The air bearing with an adaptive damper according to claim 3, wherein when the diameter of the rotating shaft is 20 to 30mm, the linear diameter of the O-ring is 1.2 to 1.8mm, the ratio of the inner diameter a of the O-ring to the outer diameter b of the accommodating groove is 0.7 to 0.85 as a/b, the radial compression amount of the O-ring is 0.25 to 0.35mm, the width c of the accommodating groove is 1.7 to 1.8mm, and the clearance d between the height of the outside of the accommodating groove and the stator is 0.1 to 0.35 mm.
7. The air bearing with the adaptive damper as claimed in claim 3, wherein when the diameter of the rotation shaft is 30-50 mm, the linear diameter of the O-ring is 1.3-2 mm, the proportional relationship between the inner diameter a of the O-ring and the diameter b of the accommodating groove is a/b of 0.7-0.85, the radial compression amount of the O-ring is 0.25-0.35 mm, the width c of the accommodating groove is 1.7-1.8 mm, and the clearance d between the height of the outer side of the accommodating groove and the stator is 0.1-0.35 mm;
or, the wire diameter of the O-ring is 2mm, the proportional relation between the inner diameter a of the O-ring and the outer diameter b of the containing groove is that a/b is 0.6-0.85, the compression amount of the O-ring is 0.15-0.4 mm, the width c of the containing groove is 2.2-2.3 mm, and the clearance d between the height of the outer side of the containing groove and the stator is 0.1-0.5 mm.
8. The air bearing with adaptive damper according to claim 3, wherein when the diameter of the rotation shaft is 36-50 mm, the linear diameter of the O-ring is 2-3.5 mm, the ratio of the inner diameter a of the O-ring to the outer diameter b of the accommodating groove is a/b of 0.6-0.9, the radial compression amount of the O-ring is 0.2-0.5 mm, the width c of the accommodating groove is 2.7-2.9 mm, and the clearance d between the outer height of the accommodating groove and the stator is 0.1-0.5 mm.
9. The air bearing including an adaptive damper according to claim 3, wherein a radial thickness of the O-ring on one side of the annular air chamber is greater than a radial thickness of the O-ring on the other side of the annular air chamber.
10. An air bearing with 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 inner diameter and the outer diameter of the O-ring and the accommodating groove on one side of the air bearing are larger than the inner diameter and the outer diameter of the O-ring and the accommodating groove on the other side of the air bearing.
11. The air bearing with adaptive damper according to claim 3, wherein the O-ring is made of rubber or metal rubber.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010062941.3A CN111120514A (en) | 2020-01-19 | 2020-01-19 | Air bearing comprising self-adaptive damper |
| PCT/CN2020/135900 WO2021143415A1 (en) | 2020-01-19 | 2020-12-11 | Air bearing comprising adaptive damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010062941.3A CN111120514A (en) | 2020-01-19 | 2020-01-19 | Air bearing comprising self-adaptive damper |
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| CN111120514A true CN111120514A (en) | 2020-05-08 |
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| CN202010062941.3A Pending CN111120514A (en) | 2020-01-19 | 2020-01-19 | Air bearing comprising self-adaptive damper |
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| CN (1) | CN111120514A (en) |
| WO (1) | WO2021143415A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111637149A (en) * | 2020-05-27 | 2020-09-08 | 西安交通大学 | Foil gas bearing with elastic damping structure |
| WO2021143415A1 (en) * | 2020-01-19 | 2021-07-22 | 至玥腾风科技集团有限公司 | Air bearing comprising adaptive damper |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP4037159A1 (en) | 2021-02-02 | 2022-08-03 | Black & Decker, Inc. | Circuit board assembly for compact brushless motor |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101497970B1 (en) * | 2014-08-01 | 2015-03-03 | 주식회사 부강테크 | Two-side air-foil bearing having multi-damper |
| EP3249786A1 (en) * | 2016-05-25 | 2017-11-29 | Celeroton AG | Electrical machine and rotor for an electrical machine |
| DE102016014315A1 (en) * | 2016-12-01 | 2018-06-07 | Anvis Deutschland Gmbh | Hydroelastic bearing |
| CN208858777U (en) * | 2018-09-30 | 2019-05-14 | 至玥腾风科技投资集团有限公司 | A kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system |
| CN111120514A (en) * | 2020-01-19 | 2020-05-08 | 至玥腾风科技集团有限公司 | Air bearing comprising self-adaptive damper |
-
2020
- 2020-01-19 CN CN202010062941.3A patent/CN111120514A/en active Pending
- 2020-12-11 WO PCT/CN2020/135900 patent/WO2021143415A1/en active Application Filing
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2021143415A1 (en) * | 2020-01-19 | 2021-07-22 | 至玥腾风科技集团有限公司 | Air bearing comprising adaptive damper |
| CN111637149A (en) * | 2020-05-27 | 2020-09-08 | 西安交通大学 | Foil gas bearing with elastic damping structure |
Also Published As
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| WO2021143415A1 (en) | 2021-07-22 |
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