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WO2016183786A1 - 一种混合式动压气体径向轴承 - Google Patents

一种混合式动压气体径向轴承 Download PDF

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Publication number
WO2016183786A1
WO2016183786A1 PCT/CN2015/079232 CN2015079232W WO2016183786A1 WO 2016183786 A1 WO2016183786 A1 WO 2016183786A1 CN 2015079232 W CN2015079232 W CN 2015079232W WO 2016183786 A1 WO2016183786 A1 WO 2016183786A1
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WO
WIPO (PCT)
Prior art keywords
foil
dynamic pressure
bearing
pressure gas
radial bearing
Prior art date
Application number
PCT/CN2015/079232
Other languages
English (en)
French (fr)
Inventor
罗立峰
Original Assignee
罗立峰
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 罗立峰 filed Critical 罗立峰
Priority to US15/575,617 priority Critical patent/US10228015B2/en
Priority to PT158921650T priority patent/PT3299643T/pt
Priority to DK15892165.0T priority patent/DK3299643T3/da
Priority to PCT/CN2015/079232 priority patent/WO2016183786A1/zh
Priority to HUE15892165A priority patent/HUE050433T2/hu
Priority to EP15892165.0A priority patent/EP3299643B1/en
Priority to ES15892165T priority patent/ES2762678T3/es
Priority to JP2018512458A priority patent/JP6767475B2/ja
Priority to KR1020177036489A priority patent/KR102030174B1/ko
Priority to EA201792553A priority patent/EA035325B1/ru
Priority to SG11201709526TA priority patent/SG11201709526TA/en
Priority to CN201510292865.4A priority patent/CN104895924A/zh
Priority to CN201510595572.3A priority patent/CN105202018B/zh
Priority to CN201520723625.0U priority patent/CN205350063U/zh
Priority to CN201610329207.2A priority patent/CN105889099B/zh
Priority to CN201620449971.9U priority patent/CN205858958U/zh
Priority to CN201620457921.5U priority patent/CN205858960U/zh
Priority to CN201620452859.0U priority patent/CN205858731U/zh
Priority to CN201620452807.3U priority patent/CN205864142U/zh
Priority to CN201610329245.8A priority patent/CN105889324B/zh
Priority to CN201610329290.3A priority patent/CN105889325B/zh
Priority to CN201610329279.7A priority patent/CN105888819B/zh
Priority to CN201610329342.7A priority patent/CN105888847B/zh
Priority to CN201620452766.8U priority patent/CN205858478U/zh
Priority to CN201620453233.1U priority patent/CN205858493U/zh
Priority to CN201620452873.0U priority patent/CN205858770U/zh
Priority to CN201610327792.2A priority patent/CN106026491B/zh
Priority to CN201620452803.5U priority patent/CN205858959U/zh
Priority to CN201610334011.2A priority patent/CN105889326B/zh
Priority to CN201610329170.3A priority patent/CN105889122A/zh
Priority to PCT/CN2016/082712 priority patent/WO2016184415A1/zh
Priority to TW105115475A priority patent/TWI676735B/zh
Priority to TW105115476A priority patent/TWI676734B/zh
Priority to TW105115466A priority patent/TWI694215B/zh
Priority to PCT/CN2016/082699 priority patent/WO2016184405A1/zh
Priority to PCT/CN2016/082714 priority patent/WO2016184417A1/zh
Priority to PCT/CN2016/082672 priority patent/WO2016184403A1/zh
Priority to PCT/CN2016/082708 priority patent/WO2016184411A1/zh
Priority to PCT/CN2016/082710 priority patent/WO2016184413A1/zh
Priority to TW105115474A priority patent/TWI699077B/zh
Priority to PCT/CN2016/082706 priority patent/WO2016184409A1/zh
Priority to PCT/CN2016/082703 priority patent/WO2016184407A1/zh
Publication of WO2016183786A1 publication Critical patent/WO2016183786A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/024—Sliding-contact bearings for exclusively rotary movement for radial load only with flexible leaves to create hydrodynamic wedge, e.g. radial foil bearings
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
    • F16C17/107—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one surface for radial load and at least one surface for axial load
    • 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
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1005—Construction relative to lubrication with gas, e.g. air, as lubricant
    • F16C33/101—Details of the bearing surface, e.g. means to generate pressure such as lobes or wedges
    • F16C33/1015—Pressure generating grooves

Definitions

  • This invention relates to a dynamic pressure gas radial bearing, and more particularly to a high-limit rotational speed rigid characteristic of a slotted dynamic pressure gas radial bearing and a high foil-type dynamic pressure gas radial bearing.
  • Hybrid hydrodynamic gas radial bearing with flexible characteristics of impact resistance and load capacity belongs to the technical field of gas bearings.
  • Gas bearings have the advantages of high speed, high precision, high temperature resistance, low friction loss and long life. After rapid development in recent decades, gas bearings have been widely used in high-speed bearings and high-precision bearings. At present, gas bearings have been developed in various types, mainly divided into dynamic pressure type and static pressure type.
  • the dynamic pressure gas bearing uses gas as a lubricant to form a gas film between the shaft and the bearing. It is a bearing form that does not directly contact the moving surface and the stationary surface. It has no pollution, low friction loss, wide temperature range, and stable operation. Long use time, high working speed and many other advantages. Due to the low friction loss and the absence of liquid lubricants, it is widely used in high-speed rotary applications, especially in ultra-high-speed applications where it is difficult to support with rolling bearings and where liquid lubricants are not easily used.
  • Dynamic pressure gas bearings are divided into dynamic pressure gas radial bearings, dynamic pressure gas thrust bearings and dynamic pressure gas radial thrust combined bearings according to the direction of load bearing.
  • the dynamic pressure gas radial bearing is formed by two working faces which are relatively moved to form a wedge-shaped space. When they move relative to each other, the gas is driven by its own viscous action and is compressed into the wedge-shaped gap, thereby generating dynamic pressure and supporting the load.
  • Gas dynamic pressure radial bearings of different structural forms have slightly different working processes due to structural differences. At present, several types of dynamic pressure gas radial bearing structures are commonly available: tiltable tile, trough and foil.
  • the tiltable tile type dynamic pressure gas radial bearing is an excellent dynamic pressure gas bearing with self-adjusting performance, can work safely in a smaller gas film gap, and is insensitive to thermal deformation and elastic deformation, and The machining accuracy is easy to guarantee, and it also has the outstanding advantages of “automatic tracking” for load changes. At present, it is mainly applied to large-scale high-speed rotating machinery and turbomachinery at home and abroad; however, its bearing structure is more complicated, the installation process is complicated, and it is more radial. Bearing requirements are high, which limits its application.
  • the foil type dynamic pressure gas radial bearing has elastic support, the bearing can obtain a certain bearing capacity and the ability to mitigate the impact vibration.
  • the foil bearing generally adopts a metal foil, not only the material manufacturing technology and the processing technology are used. There are still some technical problems, and the damping value of the bearing can not be greatly improved, resulting in insufficient rigidity of the bearing, the critical speed of the bearing is low, and it is easy to be unstable or even stuck during high-speed operation.
  • the slot type dynamic pressure gas radial bearing has good stability, and has certain stability even under no-load conditions. Moreover, at high speed, its static bearing capacity is larger than that of other types of bearings, and is currently used for small high-speed rotation. Mechanically, as a bearing in precision machinery such as gyroscopes and drums. However, since the slot type dynamic pressure gas radial bearing has high rigidity, its impact resistance is not good enough and the load capacity is not large enough to achieve high speed operation under a large load.
  • the technical problem to be solved by the present invention is to provide a rigid characteristic of a high limit rotational speed of a radial bearing of a slot type dynamic pressure gas, and a radial pressure of a foil type dynamic pressure gas.
  • a hybrid dynamic pressure gas radial bearing comprises: a bearing outer sleeve and an inner sleeve; and a foil-type elastic member disposed between the bearing outer sleeve and the inner sleeve, wherein the outer circumferential surface and the opposite end surfaces of the inner bearing sleeve have a regular shape
  • the groove pattern, and the groove pattern of one end face is mirror-symmetrical with the groove pattern of the other end face, and the axial contour line of the groove pattern of the outer circumferential surface and the radial contour line of the groove pattern of both end faces are both Form one-to-one correspondence and cross each other.
  • the axial high line in the groove pattern of the outer circumferential surface of the bearing inner sleeve corresponds to the radial high line in the groove pattern on both end faces, and mutually before the end face is chamfered Intersection;
  • the axial median line in the groove pattern of the outer circumferential surface corresponds to the radial median line in the groove pattern on both end faces, and intersects each other before the end face is chamfered;
  • the axially lower bit line in the pattern corresponds to the radially lower line in the groove pattern on both end faces, and is mutually overlapped before the end face is chamfered.
  • the trough pattern is in the shape of an impeller.
  • a wear-resistant coating is provided on the mating surface of the foil-type elastic member that cooperates with the outer circumferential surface of the bearing inner sleeve.
  • the gap between the foil-type elastic member and the inner sleeve of the bearing is 0.003 to 0.008 mm.
  • both ends of the foil-type elastic member are fixed to the inner circumferential wall of the bearing housing.
  • the foil-type elastic members are plural and evenly distributed along the inner circumferential wall of the bearing outer casing.
  • a card groove for fixing the foil-type elastic member is provided on the inner circumferential wall of the bearing housing.
  • the foil-type elastic member is subjected to surface heat treatment.
  • the foil-type elastic member is composed of a wave foil and a flat foil, and the curved convex top end of the wave foil is attached to the flat foil, and the wave-to-arch transition bottom edge of the wave foil and the bearing The inner circumferential wall of the outer casing fits.
  • the foil-type elastic member is composed of a wave foil and a flat foil, and the curved convex top end of the wave foil is adhered to the inner circumferential wall of the bearing outer sleeve, and the wave foil of the wave foil is interposed.
  • the transition bottom edge fits the flat foil.
  • the foil-type elastic member is composed of two flat foils, wherein a through hole is provided on the flat foil adjacent to the inner circumferential wall of the bearing outer casing.
  • a stop ring is provided at both ends of the bearing housing.
  • the outer circumference of the bearing housing has coaxial through holes and recessed holes, and the through holes are located in the coaxial recessed holes.
  • the present invention has the following significant advancements:
  • a foil-type elastic member is disposed between the bearing outer casing and the inner sleeve of the bearing, and the outer circumferential surface and the both end surfaces of the inner sleeve of the bearing have a groove pattern of a regular shape, and the axial direction of the groove pattern of the outer circumferential surface
  • the contour line forms a one-to-one correspondence with the radial contour lines of the groove patterns on both end faces and intersects each other, and the groove pattern of one end face forms a mirror symmetry with the groove pattern of the other end face, thereby obtaining a groove type motion Hybrid dynamic pressure gas radial bearing with high rigidity of the gas radial bearing and a flexible characteristic of the foil-type dynamic gas radial bearing with high impact resistance and load capacity;
  • the simple trough dynamic pressure gas radial bearing has double the impact resistance and load capacity at the same speed; compared with the existing simple foil dynamic pressure gas radial bearing, it has double under the same load.
  • the hybrid dynamic pressure gas radial bearing provided by the invention can achieve a limit speed of 160,000 rpm to 480,000 rpm under a load of 3 to 5 kg, and the existing dynamic pressure gas
  • the radial bearing can only achieve a load of 1 ⁇ 3kg, and the maximum speed can only reach 100,000 rpm to 180,000 rpm. It can be seen that the invention can realize the application of the dynamic pressure gas radial bearing in the ultra-high speed field under a large load, compared with The prior art has made significant progress, making the research of dynamic pressure gas radial bearing technology to a new level.
  • FIG. 1 is a schematic view showing a partially divided left-view three-dimensional structure of a hybrid dynamic pressure gas radial bearing according to Embodiment 1 of the present invention
  • Figure 2 is a partial enlarged view of A in Figure 1;
  • FIG. 3 is a partially divided right-view stereoscopic joint of a hybrid dynamic pressure gas radial bearing according to Embodiment 1 of the present invention.
  • Figure 4 is a partial enlarged view of B in Figure 3;
  • Figure 5 is a cross-sectional structural view showing a hybrid dynamic pressure gas radial bearing according to Embodiment 1 of the present invention.
  • Figure 6 is a partial enlarged view of C in Figure 5;
  • Figure 7 is a partial enlarged view of D in Figure 6;
  • FIG. 8 is a schematic cross-sectional structural view of a hybrid dynamic pressure gas radial bearing according to Embodiment 2 of the present invention.
  • Figure 9 is a schematic structural view of the wave foil of Figure 8.
  • Figure 10 is a cross-sectional structural view showing a hybrid dynamic pressure gas radial bearing according to Embodiment 3 of the present invention.
  • Figure 11 is a schematic view showing the structure of a flat foil provided with a through hole in Figure 10;
  • Figure 12 is a cross-sectional structural view showing a hybrid dynamic pressure gas radial bearing according to a fourth embodiment of the present invention.
  • bearing jacket 11, ring; 12, card slot; 13, through hole; 14, concave hole; 2, bearing inner sleeve; 21, groove pattern on the outer circumferential surface; 211, axial high position line 212, axial center line; 213, axial low line; 22, slot pattern on the left end; 221, radial high line; 222, radial center line; 223, radial low line; 23, right end Grooved pattern; 231, radial high line; 232, radial center line; 233, radial low line; 3, foil-type elastic member; 31, wave foil; 311, curved protrusion; Transition between the arches; 32, flat foil; 33, flat foil with through holes; 331, through holes in the flat foil; 34, wear-resistant coating.
  • a hybrid dynamic pressure gas radial bearing provided by the embodiment includes: a bearing outer casing 1 and a bearing inner sleeve 2, and an outer circumferential surface and left and right ends of the bearing inner sleeve 2
  • the grooves have regular groove patterns (21, 22 and 23 in the figure, the groove patterns in the embodiment are all impeller shapes), and the groove pattern 22 on the left end surface and the groove pattern 23 on the right end surface Form mirror symmetry.
  • the axial contour lines of the groove pattern 21 of the outer circumferential surface of the bearing inner sleeve 2 and the radial contour lines of the groove patterns (22 and 23) of the left and right end surfaces are formed.
  • One-to-one correspondence and mutual intersection that is, the axial high line 211 in the groove pattern 21 of the outer circumferential surface and the radial high line (221 and 231) in the groove patterns (22 and 23) of the left and right end faces are both Corresponding to each other and intersecting each other before the circumferential chamfer of the end face;
  • the axial center line 212 in the groove pattern 21 of the outer circumferential surface and the radial center line in the groove pattern (22 and 23) of the left and right end faces (222 and 232) are both corresponding to each other and overlap each other before the end face is chamfered;
  • the axial lower line 213 and the left and right end faces of the groove pattern 21 of the outer circumferential surface The radially lower bit lines (223 and 233) in the
  • the axial contour of the groove pattern 21 and the groove pattern of the left and right end faces of the outer circumferential surface of the bearing inner sleeve 2 are formed.
  • the radial contour lines of 23) form a one-to-one correspondence and cross each other, which can ensure that the pressurized gas generated by the groove patterns (22 and 23) of the impeller shapes at both end faces continuously circulate from the axial center to the outer circumferential surface.
  • the trough pattern 21 is formed in the groove passage so as to form a gas film required to support the high-speed running bearing more strongly, and the gas film is used as a lubricant for the dynamic pressure gas radial bearing, thereby realizing the hybrid type.
  • the dynamic pressure gas radial bearing can operate at high speed in the air floating state, ensuring high speed limit.
  • the hybrid dynamic pressure gas radial bearing provided in this embodiment further includes a foil-type elastic member 3 disposed between the bearing outer casing 1 and the inner sleeve 2. Since the foil-shaped elastic member 3 and the outer circumferential surface of the bearing inner sleeve 2 form a wedge-shaped space, when the bearing inner sleeve 2 rotates, the gas is driven by its own viscous action and is compressed into the wedge-shaped space to make the diameter The dynamic pressure is remarkably enhanced so as to double the supporting force; at the same time, due to the increase of the foil-type elastic member 3, under the elastic action, the bearing load capacity can be enhanced, the bearing impact resistance and the shaft vortex can be suppressed. The ability to move is significantly improved.
  • the foil-type elastic member 3 may be plural (three shown in FIG. 5), and both ends of each of the foil-shaped elastic members 3 are fixed to the inner circumferential wall of the bearing outer casing 1.
  • the foil-type elastic member 3 may be composed of a wave foil 31 and a flat foil 32, and the top end of the curved protrusion 311 of the wave foil 31 is in contact with the flat foil 32.
  • the inter-wave arch transition bottom edge 312 of the wave foil 31 is in contact with the inner circumferential wall of the bearing outer casing 1.
  • a card slot 12 for fixing both ends of the foil-type elastic member 3 is provided on the inner circumferential wall of the bearing outer casing 1, and the card slot 12 corresponds to the number of the foil-type elastic members 3, and is evenly distributed along the inner circumferential wall of the bearing outer casing 1. distributed.
  • a wear-resistant coating is provided on the mating face of the foil-type elastic member 3 (i.e., the inner surface of the flat foil 32 constituting the foil-type elastic member 3) which is engaged with the outer circumferential surface of the bearing inner sleeve 2.
  • the service life of the bearing is prolonged.
  • the retaining ring 11 when the retaining ring 11 is respectively disposed at both ends of the bearing outer casing 1, the self-sealing action between the end faces of the bearing inner sleeve 2 and the retaining ring 11 can be achieved under the driving of the high-speed rotating shaft, so that the trough pattern is continuous.
  • the generated dynamic pressure gas can be well sealed and stored in the entire matching clearance of the bearing, which fully ensures the lubrication of the high-speed running dynamic pressure gas radial bearing.
  • the foil-type elastic member 3 of the present invention is preferably subjected to surface heat treatment to better meet the performance requirements of high-speed operation; the fitting clearance of the foil-type elastic member 3 and the bearing inner sleeve 2 is preferably 0.003 to 0.008 mm. To further ensure the reliability and stability of the bearing at high speed.
  • the hybrid dynamic pressure gas radial bearing provided by this embodiment differs from Embodiment 1 only in that:
  • the foil-type elastic member 3 is composed of a wave foil 31 and a flat foil 32.
  • the top end of the curved protrusion 311 of the wave foil 31 is fitted to the inner circumferential wall of the bearing outer casing 1, and the wave arch of the wave foil 31
  • the intermediate transition bottom edge 312 is in conformity with the flat foil 32.
  • FIG. 9 is a schematic view showing the structure of the wave foil 31.
  • a hybrid dynamic pressure gas radial bearing provided by this embodiment differs from Embodiment 1 only in that the foil-type elastic member 3 is formed of a flat foil 32 and a through hole 331.
  • the flat foil 33 is composed.
  • a hybrid dynamic pressure gas radial bearing provided by this embodiment differs from Embodiment 1 only in that it has a coaxial through hole 13 and a recessed hole on the outer circumference of the bearing outer casing 1. 14.
  • the through hole 13 is located in the coaxial recess 14 .
  • the through holes 12 and the recessed holes 13 are provided for the convenience of installation and data acquisition of sensors (for example, temperature sensors, pressure sensors, rotational speed sensors, etc.) for on-line monitoring of the running state of the bearings.
  • composition of the foil-type elastic member 3 of the present invention is not limited to that described in the above embodiments, as long as the cooperation relationship between the elastic member and the inner jacket is sufficient to meet the substantive requirements of the present invention. .
  • the hybrid dynamic pressure gas radial bearing provided by the invention can achieve a limit speed of 160,000 rpm to 480,000 rpm under a load of 3 to 5 kg; and the existing dynamic pressure gas radial bearing can only achieve 1 to 3 kg.
  • the load can only reach a maximum speed of 100,000 rpm to 180,000 rpm. It can be seen that the invention can realize the application of the dynamic pressure gas radial bearing in the ultra-high speed field under a large load, and has made significant progress compared with the prior art, so that the research of the dynamic pressure gas radial bearing technology has taken a new step. .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Support Of The Bearing (AREA)
  • Sliding-Contact Bearings (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种混合式动压气体径向轴承，包括轴承外套（1）和轴承内套（2）以及设置在两者间的箔型弹性件（3）。轴承内套的外圆周面和两端面均具有规则形状的槽式花纹，两端面的槽式花纹镜像对称，外圆周面的槽式花纹（21）的轴向轮廓线与两端面槽式花纹的径向轮廓线一一对应且相互交接。该轴承既具有槽式动压气体径向轴承的高极限转速的刚性特征，又具有箔片式动压气体径向轴承的高抗冲击和载荷能力的柔性特征，适用于较大载荷下的超高速领域应用。

Description

一种混合式动压气体径向轴承 技术领域
本发明涉及一种动压气体径向轴承，具体说，是涉及一种既具有槽式动压气体径向轴承的高极限转速的刚性特征、又具有箔片式动压气体径向轴承的高抗冲击能力和载荷能力的柔性特征的混合式动压气体径向轴承，属于气体轴承技术领域。
背景技术
气体轴承具有速度高、精密度高、耐高温、摩擦损耗小、寿命长等优点，经过最近几十年的迅速发展，气体轴承已经在高速支承、高精密支承等领域取得了广泛应用。目前气体轴承已经发展出多种类型，主要分为动压型和静压型。
动压气体轴承是以气体作为润滑剂，在轴与轴承之间构成气膜，是移动面与静止面不直接接触的轴承形式，具有无污染、摩擦损失低、适应温度范围广、运转平稳、使用时间长、工作转速高等诸多优点。由于摩擦损失少，也不需要使用液体润滑油，因此在高速回转应用领域上被广泛使用，尤其是通常被使用在很难用滚动轴承支持的超高速应用领域以及不易使用液体润滑油处。
动压气体轴承按承受载荷的方向不同，又分为动压气体径向轴承、动压气体推力轴承和动压气体径向推力组合轴承。动压气体径向轴承是由相对移动的两个工作面形成楔形空间，当它们相对移动，气体因其自身的粘性作用被带动，并被压缩到楔形间隙内，由此产生动压力而支承载荷。不同结构形式的气体动压径向轴承由于结构上的差异，其工作过程略有不同。目前较为常见的几种动压气体径向轴承结构形式有：可倾瓦式、槽式和箔片式。
可倾瓦式动压气体径向轴承是一种性能优良的动压气体轴承，具有自调性能，能在更小的气膜间隙范围内安全工作，对热变形、弹性变形等不敏感，且加工精度易得到保证，还对载荷的变化具有“自动跟踪”的突出优点，目前国内外主要应用于大型高速旋转机械和透平机械；但其轴瓦结构比较复杂，安装工艺复杂，较一般径向轴承要求高，从而限制了其应用。
虽然箔片式动压气体径向轴承具有弹性支承，可使轴承相应获得一定的承载能力和缓和冲击振动的能力，但由于箔片轴承一般采用的是金属箔片，不仅材料制造技术和加工工艺技术上还存在一些难题，而且轴承的阻尼值不能很大提高，导致轴承的刚性不够，轴承的临界转速较低，在高速运转时容易失稳甚至卡死。
而槽式动压气体径向轴承具有较好的稳定性，即使在空载下也有一定的稳定性，况且，在高速下，其静态承载能力较其它形式的轴承大，目前多用于小型高速旋转机械上，如在陀螺仪和磁鼓之类的精密机械中作为轴承。但由于槽式动压气体径向轴承具有高刚性，因此其抗冲击能力不够好及载荷能力不够大，不能实现较大载荷下的高速运转。
如何实现既具有槽式动压气体径向轴承的高极限转速的刚性特征、又具有箔片式动压气体径向轴承的高抗冲击能力和载荷能力的柔性特征的混合式动压气体径向轴承，不仅是本领域研究人员一直渴望实现的目标，而且对实现动压气体径向轴承在较大载荷下的超高速领域的应用具有重要价值和深远意义。
发明内容
针对现有技术存在的上述问题和需求，本发明所要解决的技术问题就是提供一种既具有槽式动压气体径向轴承的高极限转速的刚性特征、又具有箔片式动压气体径向轴承的高抗冲击能力和载荷能力的柔性特征的混合式动压气体径向轴承，实现动压气体径向轴承在较大载荷下的超高速领域的应用。
为解决上述技术问题，本发明采用的技术方案如下：
一种混合式动压气体径向轴承，包括：轴承外套和内套及设置在轴承外套和内套之间的箔型弹性件，所述轴承内套的外圆周面和两端面均具有规则形状的槽式花纹，且一端面的槽式花纹与另一端面的槽式花纹形成镜像对称，以及外圆周面的槽式花纹的轴向轮廓线与两端面的槽式花纹的径向轮廓线均形成一一对应并相互交接。
作为一种实施方案，所述轴承内套的外圆周面的槽式花纹中的轴向高位线与两端面的槽式花纹中的径向高位线均相对应、并在端面圆周倒角前相互交接；外圆周面的槽式花纹中的轴向中位线与两端面的槽式花纹中的径向中位线均相对应、并在端面圆周倒角前相互交接；外圆周面的槽式花纹中的轴向低位线与两端面的槽式花纹中的径向低位线均相对应、并在端面圆周倒角前相互交接。
作为一种实施方案，所述的槽式花纹为叶轮形状。
作为一种优选方案，在与轴承内套的外圆周面相配合的箔型弹性件的配合面上设有耐磨涂层。
作为一种优选方案，所述的箔型弹性件与轴承内套的配合间隙为0.003～0.008mm。
作为一种优选方案，所述的箔型弹性件的两端均固定在轴承外套的内圆周壁上。
作为一种优选方案，所述的箔型弹性件为多个，且沿轴承外套的内圆周壁均匀分布。
作为进一步优选方案，在轴承外套的内圆周壁设有用于固定箔型弹性件的卡槽。
作为一种优选方案，所述的箔型弹性件经过表面热处理。
作为一种实施方案，所述的箔型弹性件由波箔和平箔组成，所述波箔的弧形凸起顶端与平箔相贴合，所述波箔的波拱间过渡底边与轴承外套的内圆周壁相贴合。
作为另一种实施方案，所述的箔型弹性件由波箔和平箔组成，所述波箔的弧形凸起顶端与轴承外套的内圆周壁相贴合，所述波箔的波拱间过渡底边与平箔相贴合。
作为又一种实施方案，所述的箔型弹性件由两个平箔组成，其中靠近轴承外套内圆周壁的平箔上设有通孔。
作为一种优选方案，在轴承外套的两端设有止环。
作为一种优选方案，轴承外套的外圆周上具有同轴的通孔和凹孔，所述的通孔位于同轴的凹孔内。
与现有技术相比，本发明具有如下显著性进步：
本发明通过在轴承外套和轴承内套之间设置箔型弹性件，并使轴承内套的外圆周面和两端面均具有规则形状的槽式花纹，且外圆周面的槽式花纹的轴向轮廓线与两端面的槽式花纹的径向轮廓线均形成一一对应并相互交接，并且一端面的槽式花纹与另一端面的槽式花纹形成镜像对称，从而得到了既具有槽式动压气体径向轴承的高极限转速的刚性特征、又具有箔片式动压气体径向轴承的高抗冲击能力和载荷能力的柔性特征的混合式动压气体径向轴承；相对于现有的单纯槽式动压气体径向轴承，具有在相同转速下成倍增加的抗冲击能力和载荷能力；而相对于现有的单纯箔片式动压气体径向轴承，具有在相同载荷下成倍增加的极限转速；经测试，本发明提供的混合式动压气体径向轴承可实现在3～5kg载荷下的极限转速可达160,000rpm～480,000rpm，而现有的动压气体径向轴承只能实现1～3kg的载荷，极限转速最高只能达到100,000rpm～180,000rpm；可见，本发明可实现动压气体径向轴承在较大载荷下的超高速领域的应用，相对于现有技术取得了显著性进步，使得动压气体径向轴承技术的研究跨上了新台阶。
附图说明
图1是本发明实施例1提供的一种混合式动压气体径向轴承的局部分割的左视立体结构示意图；
图2是图1中的A局部放大图；
图3是本发明实施例1提供的一种混合式动压气体径向轴承的局部分割的右视立体结 构示意图；
图4是图3中的B局部放大图；
图5是本发明实施例1提供的一种混合式动压气体径向轴承的剖面结构示意图；
图6是图5中的C局部放大图；
图7是图6中的D局部放大图；
图8是本发明实施例2提供的一种混合式动压气体径向轴承的剖面结构示意图；
图9是图8中波箔的结构示意图；
图10是本发明实施例3提供的一种混合式动压气体径向轴承的剖面结构示意图；
图11是图10中设有通孔的平箔的结构示意图；
图12是本发明实施例4提供的一种混合式动压气体径向轴承的剖面结构示意图。
图中：1、轴承外套；11、止环；12、卡槽；13、通孔；14、凹孔；2、轴承内套；21、外圆周面的槽式花纹；211、轴向高位线；212、轴向中位线；213、轴向低位线；22、左端面的槽式花纹；221、径向高位线；222、径向中位线；223、径向低位线；23、右端面的槽式花纹；231、径向高位线；232、径向中位线；233、径向低位线；3、箔型弹性件；31、波箔；311、弧形凸起；312、波拱间过渡底边；32、平箔；33、设有通孔的平箔；331、平箔上的通孔；34、耐磨涂层。
具体实施方式
下面结合附图及实施例对本发明的技术方案做进一步详细地说明。
实施例1
如图1和图3所示：本实施例提供的一种混合式动压气体径向轴承，包括：轴承外套1和轴承内套2，所述轴承内套2的外圆周面和左、右端面均具有规则形状的槽式花纹(如图中的21、22和23，本实施例中的槽式花纹均为叶轮形状)，且左端面的槽式花纹22与右端面的槽式花纹23形成镜像对称。
结合图1至图4所示：所述轴承内套2的外圆周面的槽式花纹21的轴向轮廓线与左、右端面的槽式花纹(22和23)的径向轮廓线均形成一一对应并相互交接，即：外圆周面的槽式花纹21中的轴向高位线211与左、右端面的槽式花纹(22和23)中的径向高位线(221和231)均相对应、并在端面圆周倒角前相互交接；外圆周面的槽式花纹21中的轴向中位线212与左、右端面的槽式花纹(22和23)中的径向中位线(222和232)均相对应、并在端面圆周倒角前相互交接；外圆周面的槽式花纹21中的轴向低位线213与左、右端面的 槽式花纹(22和23)中的径向低位线(223和233)均相对应、并在端面圆周倒角前相互交接。
通过使左端面的槽式花纹22与右端面的槽式花纹23形成镜像对称及轴承内套2的外圆周面的槽式花纹21的轴向轮廓线与左、右端面的槽式花纹(22和23)的径向轮廓线均形成一一对应并相互交接，可保证两端面的叶轮形状的槽式花纹(22和23)所产生的增压气体从轴心沿径向不断地往外圆周面的槽式花纹21形成的凹槽通道里输送，以致形成更强支撑高速运转轴承所需的气膜，而气膜即作为动压气体径向轴承的润滑剂，因此实现了所述的混合式动压气体径向轴承可在气浮状态下的高速稳定运转，保证了高极限转速。
如图5所示：本实施例提供的混合式动压气体径向轴承还包括设置在轴承外套1和内套2之间的箔型弹性件3。由于箔型弹性件3与轴承内套2的外圆周面间形成了楔形空间，因此，当轴承内套2转动时，气体因其自身的粘性作用被带动并被压缩到楔形空间内，使径向动压力得到显著增强以致可成倍增大支撑力；同时，由于增加了箔型弹性件3，在其弹性作用下，还可使轴承的载荷能力增强，使轴承的抗冲击能力和抑制轴涡动的能力显著提高。所述的箔型弹性件3可为多个(图5中示出了3个)，每个箔型弹性件3的两端均固定在轴承外套1的内圆周壁上。
结合图5和图6所示：所述的箔型弹性件3可采用波箔31和平箔32组成，所述波箔31的弧形凸起311的顶端与平箔32相贴合，所述波箔31的波拱间过渡底边312与轴承外套1的内圆周壁相贴合。在轴承外套1的内圆周壁设有用于固定箔型弹性件3两端的卡槽12，所述卡槽12与箔型弹性件3的数量相对应，且均沿轴承外套1的内圆周壁均匀分布。
如图7所示：在与轴承内套2的外圆周面相配合的箔型弹性件3的配合面(即：构成箔型弹性件3的平箔32的内表面)上设有耐磨涂层，以降低高速运转的轴承内套2对箔型弹性件3的磨损，延长轴承的使用寿命。
另外，当在轴承外套1的两端分别设置止环11时，可实现在高速回转轴的带动下，使轴承内套2的两端面与止环11间产生自密封作用，使槽式花纹连续产生的动压气体能完好地密闭保存在轴承的整个配合间隙中，充分保证高速运转的动压气体径向轴承的润滑需要。
本发明所述的箔型弹性件3优选均经过表面热处理，以更好地满足高速运转的性能要求；所述的箔型弹性件3与轴承内套2的配合间隙优选为0.003～0.008mm，以进一步确保轴承高速运转的可靠性和稳定性。
实施例2
如图8所示，本实施例提供的一种混合式动压气体径向轴承与实施例1的区别仅在于： 所述的箔型弹性件3由波箔31和平箔32组成，所述波箔31的弧形凸起311的顶端与轴承外套1的内圆周壁相贴合，所述波箔31的波拱间过渡底边312与平箔32相贴合。
图9所示为所述波箔31的结构示意图。
实施例3
如图10和11所示，本实施例提供的一种混合式动压气体径向轴承与实施例1的区别仅在于：所述的箔型弹性件3由平箔32和设有通孔331的平箔33组成。
实施例4
如图12所示，本实施例提供的一种混合式动压气体径向轴承与实施例1的区别仅在于：在所述轴承外套1的外圆周上具有同轴的通孔13和凹孔14，所述的通孔13位于同轴的凹孔14内。所设置的通孔12和凹孔13是为了方便用于在线监测所述轴承运行状态的传感器(例如：温度传感器、压力传感器、转速传感器等)的安装和数据采集。
另外需要说明的是：本发明所述的箔型弹性件3的组成结构不仅限于上述实施例中所述，只要保证其与内外套之间的配合关系满足本发明所述的实质性要求即可。
经测试：本发明提供的混合式动压气体径向轴承可实现在3～5kg载荷下的极限转速可达160,000rpm～480,000rpm；而现有的动压气体径向轴承只能实现1～3kg的载荷，极限转速最高只能达到100,000rpm～180,000rpm。可见，本发明可实现动压气体径向轴承在较大载荷下的超高速领域的应用，相对于现有技术取得了显著性进步，使得动压气体径向轴承技术的研究跨上了新台阶。
最后有必要在此指出的是：以上内容只用于对本发明所述技术方案做进一步详细说明，不能理解为对本发明保护范围的限制，本领域的技术人员根据本发明的上述内容作出的一些非本质的改进和调整均属于本发明的保护范围。

Claims (13)

  1. 一种混合式动压气体径向轴承，其特征在于：包括轴承外套和内套及设置在轴承外套和内套之间的箔型弹性件，所述轴承内套的外圆周面和两端面均具有规则形状的槽式花纹，且一端面的槽式花纹与另一端面的槽式花纹形成镜像对称，以及外圆周面的槽式花纹的轴向轮廓线与两端面的槽式花纹的径向轮廓线均形成一一对应并相互交接。
  2. 根据权利要求1所述的混合式动压气体径向轴承，其特征在于：外圆周面的槽式花纹中的轴向高位线与两端面的槽式花纹中的径向高位线均相对应、并在端面圆周倒角前相互交接；外圆周面的槽式花纹中的轴向中位线与两端面的槽式花纹中的径向中位线均相对应、并在端面圆周倒角前相互交接；外圆周面的槽式花纹中的轴向低位线与两端面的槽式花纹中的径向低位线均相对应、并在端面圆周倒角前相互交接。
  3. 根据权利要求1所述的混合式动压气体径向轴承，其特征在于：在与轴承内套的外圆周面相配合的箔型弹性件的配合面上设有耐磨涂层。
  4. 根据权利要求1或3所述的混合式动压气体径向轴承，其特征在于：所述的箔型弹性件与轴承内套的配合间隙为0.003～0.008mm。
  5. 根据权利要求1所述的混合式动压气体径向轴承，其特征在于：所述的箔型弹性件的两端均固定在轴承外套的内圆周壁上。
  6. 根据权利要求1或5所述的混合式动压气体径向轴承，其特征在于：所述的箔型弹性件为多个，且沿轴承外套的内圆周壁均匀分布。
  7. 根据权利要求1或5所述的混合式动压气体径向轴承，其特征在于：在轴承外套的内圆周壁设有用于固定箔型弹性件的卡槽。
  8. 根据权利要求1所述的混合式动压气体径向轴承，其特征在于：所述的箔型弹性件经过表面热处理。
  9. 根据权利要求1或8所述的混合式动压气体径向轴承，其特征在于：所述的箔型弹性件由波箔和平箔组成，所述波箔的弧形凸起顶端与平箔相贴合，所述波箔的波拱间过渡底边与轴承外套的内圆周壁相贴合。
  10. 根据权利要求1或8所述的混合式动压气体径向轴承，其特征在于：所述的箔型弹性件由波箔和平箔组成，所述波箔的弧形凸起顶端与轴承外套的内圆周壁相贴合，所述波箔的波拱间过渡底边与平箔相贴合。
  11. 根据权利要求1或8所述的混合式动压气体径向轴承，其特征在于：所述的箔型弹性件由两个平箔组成，其中靠近轴承外套内圆周壁的平箔上设有通孔。
  12. 根据权利要求1所述的混合式动压气体径向轴承，其特征在于：在轴承外套的两 端设有止环。
  13. 根据权利要求12所述的混合式动压气体径向轴承，其特征在于：所述轴承外套的外圆周上具有同轴的通孔和凹孔，所述的通孔位于同轴的凹孔内。
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US15/575,617 US10228015B2 (en) 2015-05-19 2015-05-19 Hybrid dynamic pressure gas radial bearing
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DK15892165.0T DK3299643T3 (en) 2015-05-19 2015-05-19 Mixed-type dynamic pressure gas radial bearing
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CN201510595572.3A CN105202018B (zh) 2015-05-19 2015-09-18 一种混合式动压气体径向轴承
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