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WO2006018916A1 - Palier fluide à pression dynamique - Google Patents

Palier fluide à pression dynamique Download PDF

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Publication number
WO2006018916A1
WO2006018916A1 PCT/JP2005/003314 JP2005003314W WO2006018916A1 WO 2006018916 A1 WO2006018916 A1 WO 2006018916A1 JP 2005003314 W JP2005003314 W JP 2005003314W WO 2006018916 A1 WO2006018916 A1 WO 2006018916A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
spring
foil
slit
spring oil
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2005/003314
Other languages
English (en)
Japanese (ja)
Inventor
Hisao Wada
Hideo Kaido
Tooru Nishida
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kawasaki Heavy Industries Ltd
Kawasaki Motors Ltd
Original Assignee
Kawasaki Heavy Industries Ltd
Kawasaki Jukogyo KK
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 Kawasaki Heavy Industries Ltd, Kawasaki Jukogyo KK filed Critical Kawasaki Heavy Industries Ltd
Publication of WO2006018916A1 publication Critical patent/WO2006018916A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/02—Sliding-contact 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
    • F16C43/00—Assembling bearings
    • F16C43/02—Assembling sliding-contact 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/20—Application independent of particular apparatuses related to type of movement
    • F16C2300/22—High-speed rotation
    • 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

Definitions

  • the present invention relates to a hydrodynamic bearing for a high-speed rotating shaft, and more particularly to a hydrodynamic foil bearing.
  • hydrodynamic bearings There are two types of hydrodynamic bearings: static pressure type and dynamic pressure type.
  • the dynamic pressure type bearing that generates pressure by rotating the shaft using ambient air is less expensive than the static pressure type that is externally pressurized by a compressor or the like. It is advantageous in terms of weight reduction, maintenance, etc., and is oil-free
  • a foil type hydrodynamic bearing is composed of a top oil that forms a gas film with a shaft, a spring oil that elastically supports the oil, and a housing that holds them.
  • spring bearings for oil bearings such as bump type and leaf type.
  • FIG. 30 is a side sectional view showing an example of a bump oil air bearing.
  • a bump oil air bearing that uses a bump type spring oil, as disclosed in Patent Document 1, etc. is a bump oil in which a thin metal plate is formed in a corrugated plate shape between a housing in which a rotating shaft is inserted and the rotating shaft. And a flat metal thin plate with a top lubricant coated with a solid lubricant inside, and the rotating shaft is hydrodynamically supported by a thin fluid film formed between the rotating shaft and the top oil, The top oil is supported by the inertia through the bump oil!
  • Bump fill air bearings are equipped with a self-adjusting mechanism for the rotating shaft by means of the bump fill panel function, so the requirements for the work accuracy of the bearing are not strict, but the bump foil needs to be molded into a complex shape, so press High precision molding process is required, and the process is complicated and difficult to manufacture and assemble.
  • FIG. 31 is a side sectional view showing an example of a leaf oil air bearing.
  • Leaf-foil bearings that use leaf-type spring-foil oil are placed one on top of the other so that multiple leaf-foils can slide together on the inner periphery of the bearing housing, and there is a gap to draw air inside.
  • the rotating shaft is supported at a distance, and the leaf oil is deformed to fit the rotating shaft in accordance with the axial load action of the rotating shaft to form an appropriate air layer. Yes.
  • the leaf oil also needs to be molded into a certain shape, which requires time and effort for molding, and also requires time and effort for the bearing.
  • Patent Document 2 discloses an air bearing in which an assembly process is omitted by forming a spring oil from a single plate cover.
  • the disclosed spring bearing oil has a rectangular elastic plate cut into one side at an appropriate interval along the long axis to form a multiple support plate, one end of which is provided in the notch inside the housing. It is fixed along the inside of the housing and fixed to the fixed mechanism, and the support plate is in contact with the top oil surrounding the rotating shaft and is supported by the spring action.
  • the spring oil used in the disclosed hydrodynamic foil bearing also needs to be molded to maintain the posture of the raised support plate.
  • a spring foil is accommodated in a three-layer structure in a bearing housing so that the innermost layer has a substantially quadrangular shape, the intermediate layer has a heptagonal shape, and the outermost layer has a substantially hexagonal shape.
  • An oil journal bearing is disclosed.
  • the triple-winding spring oil is formed with a groove across the width of the flat spring oil, and the portion of the groove bent between the grooves is used as an elastic beam.
  • the top oil is screwed at one end to the inner cylindrical surface of the housing together with the bump oil or the spring oil.
  • the other end is a free end that can be moved in the circumferential direction.
  • the rotating shaft rotates in the direction from the free end direction to the fixed end direction so that air is wound between the rotating shaft and the bump fluid to form an air layer.
  • the top oil wraps around the rotating shaft! Because the air layer cannot be formed, the rotation direction is limited to one direction.
  • the conventional top oil fixing method requires a special work for fixing to the inner surface of the housing, and has the problem of limiting the rotation direction of the rotating shaft to one side.
  • Patent Document 1 Japanese Patent Laid-Open No. 2002-0661645
  • Patent Document 2 JP 2002-364643 A
  • Patent Document 3 Japanese Utility Model Publication No. 6-76716
  • the problem to be solved by the present invention is to provide a foil type hydrodynamic bearing having excellent bearing performance using a spring foil that is easier to manufacture and excellent in mass productivity.
  • a second problem to be solved by the present invention is to provide a peristaltic fluid bearing having no restriction in the rotational direction by using a top oil fixing structure that is easy to mount.
  • the hydrodynamic bearing of the present invention is mounted with a spring oil formed of a thin flat plate having a plurality of slits on the inner wall of the bearing housing, and the top is placed inside the spring fill.
  • This is a foil type bearing in which the oil is arranged and the rotating shaft is arranged inside the top oil, and the spring oil is bent at a position with small rigidity and has many elastic beams that are in contact with the inner side of the inner wall. A rectangular cross section is formed, and the rotating shaft is elastically supported by this elastic beam.
  • a slit is provided in the spring oil formed of a thin flat plate to give a strength difference in bending rigidity depending on the location.
  • this spring oil is attached to the inner wall of the bearing housing, it is bent at a slit position with a small rigidity.
  • a large number of elastic beams are formed between adjacent slits in contact with the inner wall, forming a polygonal cross section. This elastic beam can support the top foil in inertia.
  • the rotating shaft is wrapped in top oil, and a gas such as air is inserted between the rotating shaft and the top oil as it rotates to form a gas layer, and the rotating shaft is supported hydrodynamically. In particular, high-speed rotation can be performed smoothly. As the rotation speed of the rotating shaft increases, the thickness of the gas layer increases and the top oil is pressed against the inner wall of the bearing housing to increase the elastic force of the spring oil. It starts to rotate.
  • the slit can be provided in a direction substantially parallel to the rotation axis when the spring oil is inserted into the bearing housing, and the flange can be bent to form a node at the slit position.
  • the difference in bending stiffness between elastic beams is caused by the difference in the length of the oil part sandwiched between the slits.
  • the length of the elastic beam can be changed by setting the slits at unequal pitches.
  • the bending rigidity is weak at the long elastic beam, the inner diameter of the bearing is reduced because the distance between the inner wall of the housing and the top foil is increased.
  • the bending rigidity increases at the short beam section, and the inner diameter of the bearing increases because the top oil approaches the inner wall of the housing. Therefore, when the load is small or the vibration is small, the spring with the small inner diameter supports the shaft, and when the load is large or the vibration is large, the shaft is supported even at the large inner diameter. It will have a support structure with a unique panel characteristic.
  • Slits having different lengths may be alternately arranged.
  • the part with the long slit is broken, and the part with the short slit is hard to break. Therefore, the long slit is initially refracted and contacts the wall of the housing, and the short slit does not break. Therefore, the rotation of the rotating shaft with the small inner diameter of the cylinder made by the top oil is small.
  • the spring oil is refracted even at the short slit position, and the top oil force S approaches the inner wall of the housing, the inner diameter increases, the length of the elastic beam decreases, and the rigidity of the spring oil increases. . In this way, it is possible to obtain a bearing that exhibits characteristics such that when the load is small, the rigidity of the spring foil is low and the rigidity becomes high when the load at which the top oil is easily opened increases.
  • the length of the beam formed between the slits of the spring oil is made equal, and the width of the slit is reduced. It may be changed. Since the slit portion does not generate support rigidity for elastically supporting the rotating shaft, the rigidity distribution can be designed relatively easily in order to provide an appropriate difference in support rigidity for each location in the circumferential direction of the housing. By providing a difference in the circumferential direction of the rigidity of the foil bearing, elliptical motion can be generated on the rotating shaft, and vibration can be suppressed.
  • the slits parallel to the rotation axis may be arranged at equal intervals so that the rigidity of the elastic beams is almost equal to each other!
  • the slit may be formed by force from the side end of the oil toward the center line. If the slit is opened at the side end, the rigidity is reduced at the side of the oil, and it is possible to prevent the rotation shaft from hitting one side.
  • the slit can have a shape in which the flat plate force is separated from the remaining sides excluding the bottom, such as two sides of the triangle and three sides of the rectangle.
  • this spring oil is installed along the top oil, the tongue that extends tangentially at the position of each slit reaches the inner wall of the bearing housing to become a panel, and supports the top oil.
  • the rigidity may be changed by making the slit into a thick cut shape so that the distance to the ridgeline of the adjacent slit varies depending on the distance of the edge of the flat plate.
  • the cut-off shape is a shape in which a triangle or semicircular shape protrudes into the slit, the effective width of the beam is small and the rigidity is weak while the protruding portion becomes a fulcrum, but the rotation speed increases and the top oil is transferred to the housing. Stiffness increases as it approaches.
  • the slit shape is semicircular, the length of the elastic beam is initially large and the short beam acts as the top oil spreads. It exhibits the characteristics that the rigidity is strengthened.
  • a part of the slits may be provided in parallel to the side end line of the flat plate of the spring oil.
  • Spring oil can be formed from one end of one thin plate, and solid lubricant can be applied to the other end which is left to the extent that it surrounds the rotating shaft.
  • the top oil is also a force that is always placed inside the spring oil.
  • the slit portion of the spring oil can be provided with multiple slits at high density. Although the slit portion is refracted and comes into contact with the inner wall of the housing, if a plurality of slits are provided at high density, a large number of ridge lines along the inner wall share the pressing force, so that the contact surface pressure can be reduced.
  • the spring oil may be wound around the top oil in multiple layers.
  • the inner spring-foil slit should be aligned with the center of the outer spring-foil beam.
  • the rigidity increases as the top oil spreads, so that the low-speed rotational force can be supported with an appropriate rigidity up to the high-speed rotation.
  • the slit of the spring oil is rounded at the end so as to relieve the stress generated at the end.
  • the slit can be manufactured by etching.
  • etching method it is possible to accurately and easily form slits with extremely fine dimensions as in the case of a printed circuit board.
  • the bearing housing may be formed such that the cross section of the inner hole is polygonal, and the spring foil slit is positioned at the apex of the polygon. When such apex exists, it becomes easier to fix the spring oil. In addition, if the apex angle of the inner hole section polygon of the bearing housing is positioned in the middle of the beam formed between the slits of the spring oil, the sectional area of the space formed by the housing wall and the spring oil is set. As the flow rate increases, a large amount of cooling fluid circulates and the range of high-speed rotation in which the bearing can be used is expanded.
  • a stop wall rising from the inner wall surface is formed at each of the two locations on the inner wall of the housing where both ends of the top oil come into contact, and the two top oils formed by the elastic flat plate cover are stopped. It is preferably inserted and fixed so as to stretch between the walls.
  • stop The angle of the wall surface is preferably in the range of 60 ° force and 90 ° with respect to the inner wall surface.
  • a clasp is attached to the side surface of the stop wall to prevent it more reliably. It can be set or fixed on the side of the housing with an ear at the end of the top oil.
  • both ends of the top oil are fixed to the housing, and air can be introduced between the top oil and the rotating shaft from any fixed portion, so the rotating shaft can be rotated in either direction. Also, the performance as a fluid bearing can be exhibited.
  • the inlet (leading) side of the bearing in the rotational direction can be deeper than the outlet (trading) side to facilitate air introduction.
  • the flying performance and the load capacity can be adjusted.
  • the top oil at unequal pitches bearing dynamic characteristics with high vibration stability can be obtained.
  • the present invention provides a spring oil having a thin flat plate force provided with a plurality of slits used in a foil type hydrodynamic bearing.
  • a stop wall having an angle of approximately 60 ° force 90 ° with respect to the inner wall surface is formed at the position of the inner wall of the housing where both ends of the top oil come into contact, and a digging having a triangular cross section is formed on the front surface of the stop wall.
  • a top foil mechanism that can be used for hydrodynamic bearings that use various foils that are fixed by extending and inserting the top oil between the surfaces of the stop wall. Provide a stop mechanism.
  • the hydrodynamic foil bearing of the present invention it is possible to manufacture a spring-foil oil more easily and accurately than before and easily incorporate it into the bearing. However, the adjustment fee according to the demand is increased, and the stability at high speed is also improved.
  • the rotating shaft can rotate in any direction.
  • FIG. 1 is a cross-sectional view of a dynamic pressure gas bearing according to a first embodiment of the present invention.
  • FIG. 2 is a slit layout diagram of spring oil used in the dynamic pressure gas bearing of the first embodiment.
  • FIG. 3 is a drawing for explaining end processing of a slit of spring oil.
  • FIG. 4 is a plan view schematically showing the state of a slit of spring oil constituting the feature of the second embodiment of the present invention.
  • FIG. 5 is a cross-sectional view of a dynamic pressure gas bearing according to a second embodiment.
  • FIG. 6 is a plan view schematically showing the state of a slit of spring oil constituting the feature of the third embodiment of the present invention.
  • FIG. 7 is a plan view of a spring oil used in a dynamic pressure gas bearing according to a fourth embodiment of the present invention.
  • FIG. 8 is a drawing for explaining a state in which spring oil is incorporated in a dynamic pressure gas bearing of a fourth embodiment.
  • FIG. 9 is a plan view of a spring oil used in a dynamic pressure gas bearing according to a fifth embodiment of the present invention.
  • FIG. 10 is a drawing for explaining the state of incorporation of spring oil in the dynamic pressure gas bearing of the fifth embodiment.
  • FIG. 11 is a plan view of a spring oil used in a dynamic pressure gas bearing according to a sixth embodiment of the present invention.
  • FIG. 12 is a drawing for explaining the state of incorporation of spring oil in the dynamic pressure gas bearing of the sixth embodiment.
  • FIG. 13 is a plan view of a spring oil used in a dynamic pressure gas bearing according to a seventh embodiment of the present invention.
  • FIG. 14 is a plan view of a spring oil used in a dynamic pressure gas bearing according to an eighth embodiment of the present invention.
  • FIG. 16 is a plan view of a spring oil used in the dynamic pressure gas bearing of the ninth embodiment. [17] FIG. 17 is a perspective view illustrating a spring oil locking mechanism.
  • FIG. 18 is a perspective view illustrating a spring oil locking mechanism with a drop-off prevention mechanism added thereto.
  • FIG. 19 is a perspective view for explaining another mechanism in which a spring oil locking mechanism is added with another drop-off prevention mechanism.
  • FIG. 20 A sectional view showing a state in which the locking mechanism of the ninth embodiment is applied to a bump foil bearing device.
  • FIG. 22 is a cross-sectional view of a dynamic pressure gas bearing according to a tenth embodiment of the present invention.
  • FIG. 23 is a plan view of a spring oil used in the dynamic pressure gas bearing of the tenth embodiment.
  • FIG. 24 is a drawing showing another shape example of the tongue formed on the spring oil.
  • FIG. 25 is a drawing showing still another example of the shape of the tongue formed on the spring oil.
  • FIG. 26 is a plan view of a spring oil used in a dynamic pressure gas bearing according to an eleventh embodiment of the present invention.
  • FIG. 30 is a cross-sectional view showing an example of a conventional dynamic pressure gas bearing.
  • FIG. 31 is a cross-sectional view showing another example of a conventional dynamic pressure gas bearing.
  • FIG. 1 is a cross-sectional view of a dynamic pressure gas bearing according to one embodiment of the present invention
  • FIG. 2 is a slit layout diagram of a spring oil used therefor.
  • the spring oil 12 is arranged so as to contact the inner wall of the cylindrical housing 11, and the top oil 13 is fixed to the inner wall of the nose housing with the top oil 13 fixed to the inner wall.
  • the rotating shaft 14 is accommodated through an air layer 15 in a cylindrical shape that is formed so as to make one round along the inner wall.
  • the spring oil 12 is a thin elastic metal plate having a thickness of several hundreds of meters, and as shown in FIG. 2, slits 16 having the same shape are arranged in parallel to the winding direction of the oil. Slit 16 force S Since the metal part is small at a certain position and its rigidity is weak, when it is loaded into the dynamic pressure gas bearing 1, it is bent at the slit position as shown in Fig. 1, and the spring oil 12 is partially vacant. It becomes a cylinder with a polygonal cross section.
  • the spring oil 12 having a polygonal cross section is usually formed by bending at the position of the slit 16, contacting the inner wall of the wing, and the portion sandwiched by the slit 16 is an elastic beam.
  • the top top oil 13 in the inside is supported by inertia.
  • the rigidity of the long elastic beam A formed between them becomes small, and the rigidity of the short elastic beam B existing at a short distance becomes large.
  • the rigidity of the spring oil 12 can be adjusted by the position of the slit, so that the desired elasticity along the circumference of the bearing can be provided with the desired elasticity.
  • the top oil 13 is a thin 100 ⁇ m-thick elastic metal plate treated with a solid lubricant to reduce the coefficient of friction with the rotating shaft 14, and one end is fixed to the inner wall of the housing 11. The other end is a free end.
  • the rotary shaft 14 is rotated in the direction of the free end of the top oil 13 as shown by the arrow in FIG.
  • air is drawn between the rotating shaft 14 and the top oil 13
  • An air layer 15 is formed.
  • the air layer 15 significantly reduces the rotational friction of the rotating shaft 14 and enables smooth rotation.
  • the bearing is supported with relatively weak rigidity at the start of rotation, and is supported with strong rigidity that resists strong stress at high speed rotation, and the bearing has stepwise rigidity suitable for the rotation speed. A device can be obtained.
  • the support rigidity and the rigidity distribution in the circumferential direction of the housing can be easily adjusted.
  • the end of the slit 16 is rounded to reduce the stress.
  • the hydrodynamic gas bearing of this embodiment is manufactured and manufactured without the need for molding calorie using a press machine or the like by simply opening a slit in the spring oil as compared to a conventional oil-type gas bearing or leaf-type gas bearing. Easy to assemble.
  • the spring oil can be processed by using an etching technique used for manufacturing printed circuit boards, etc. If the etching technique is used, the accuracy is high and mass production is easy.
  • FIG. 4 and FIG. 5 are drawings for explaining another embodiment of the present invention
  • FIG. 4 is a plan view schematically showing the state of the slit of the spring oil constituting the feature of this embodiment. is there.
  • Fig. 5 is a cross-sectional view of the dynamic pressure gas bearing of the present embodiment, where (a) is the state at the beginning of rotation, (b) is the state in the middle of high speed, and (c) is the state during high speed rotation. Indicates.
  • slits having different lengths are alternately arranged. It has been.
  • the part where the slit 22 is long has a small remaining flat plate width, so the rigidity is weak and the foil is easily broken.
  • the part with the short slit 23 is harder to break.
  • a dynamic pressure gas bearing incorporating spring oil in which slits of different lengths are alternately arranged has a small load! /
  • the rigidity of the spring oil is low and the top oil opens. It is possible to obtain a bearing that exhibits favorable characteristics that rigidity increases with an easy load.
  • Fig. 6 is a plan view of a spring oil with a slit cut from the side end and a central portion remaining.
  • the dynamic pressure gas bearing of the present embodiment incorporates a spring foil 31 in which a plurality of slits 32 are formed so as to leave a central band with a constant width at the center of the foil by cutting the end force on the oil side. Is. Since the spring oil is separated at the side of the bearing in this way, the elastic beams move relative to each other, so that the rigidity at the side is weak compared to the internal rigidity, and when the rotating shaft tilts, It is possible to avoid contact with one piece.
  • FIG. 7 is a plan view of the spring oil used in the dynamic pressure gas bearing of the fourth embodiment
  • FIG. 8 is a drawing for explaining the state of incorporation of the spring oil of FIG.
  • the spring oil used in this example is a single elastic material.
  • This is a flat plate 33 in which a spring oil 34 part and a top oil 35 part are formed together.
  • the spring oil 34 part has slits in place, and the top oil 35 part has a solid lubricant on the surface.
  • the spring oil 34 is formed with 4 slits and incorporated into the bearing, the spring oil partial force square is formed. However, more slits may be formed, That's not good.
  • the dynamic pressure gas bearing 3 of the present embodiment shown in FIG. 8 is obtained by rounding a portion 35 of the elastic flat plate 33 to which a solid lubricant is applied to form a top oil and further forming a portion 34 having slits at each slit position. It is refracted into a polygonal spring oil and inserted into the inner wall 36 of the nosing.
  • the foil 37 may be prevented from shifting by the rotation of the rotating shaft by extending and fixing the end 37 of the spring oil to the inner wall 36 of the nosing.
  • the dynamic pressure gas bearing of this embodiment integrates the spring oil and the top oil, the number of parts constituting the bearing can be reduced, and the production can be rationalized.
  • FIG. 9 is a plan view of the spring oil used in the dynamic pressure gas bearing of the fifth embodiment
  • FIG. 10 is a view for explaining the state of incorporation of the spring oil of FIG.
  • the spring oil 41 used in this embodiment is provided with a plurality of slits 43 adjacent to and parallel to a slit portion 42 formed with an elastic beam in between.
  • the spring oil 41 is loaded into the housing inner wall 44, as shown in FIG. This reduces the pressure and reduces the wear on the inner wall 44 of the housing.
  • FIG. 11 is a plan view of the spring oil used in the dynamic pressure gas bearing of the sixth embodiment
  • FIG. 12 is a drawing for explaining the state of incorporation of the spring oil of FIG.
  • the spring oil 47 used in this embodiment is placed in a portion that becomes an elastic beam by being sandwiched between vertical slits 48 formed in the width direction of the spring foil 47.
  • a plurality of lateral slits 49 are formed in parallel to the side edges.
  • the spring oil 47 When the spring oil 47 is charged into the inner wall 46 of the housing, it is refracted while contacting the inner wall 46 at the position of the vertical slit 48 to form a tubular spring oil having a polygonal cross section. As shown in FIG. 12, the spring oil 47 is brought into surface contact with the surface of the top oil 50 at the positions of the plurality of lateral slits 49 to reduce the contact pressure.
  • FIG. 13 is a drawing of a spring oil used in the dynamic pressure gas bearing of the seventh embodiment.
  • the spring oil 51 used in this embodiment forms slits 52, 53, 54 of the same length at appropriate intervals, and the length of the elastic beam formed between adjacent slits is selected. In addition to adjusting the rigidity of the beam, the width of the slit is selected to adjust the distribution of the elastic beam.
  • the elastic beam is formed between the slit end lines, there is no panel that elastically supports the rotating shaft in the wide slits 53 and 54, so the spring can be selected by selecting the slit width appropriately.
  • the elastic distribution of the oil 51 can be adjusted.
  • FIG. 14 is a plan view of the spring oil used in the dynamic pressure gas bearing of the eighth embodiment.
  • the spring oil 56 used in this embodiment is formed in the width direction of the spring oil 56.
  • a plurality of horizontal slits 58 are formed parallel to the side edges of the spring oil 56 at the portion sandwiched between the vertical slits 57 to be divided into appropriate widths and assembled into the housing
  • the support rigidity is changed in the axial direction of the rotary shaft. For example, side If a lateral slit 58 parallel to the end is formed near the side end to increase the rigidity at the center of the bearing and decrease the rigidity at the ends of both sides, it is possible to prevent the rotation shaft from hitting one side.
  • FIG. 15 is a cross-sectional view schematically showing the dynamic pressure gas bearing of the ninth embodiment
  • FIG. 16 is a plan view of the spring oil used in this embodiment
  • FIG. 17 shows the locking mechanism of the spring oil. It is a perspective view to explain.
  • the dynamic pressure gas bearing 6 of the present embodiment is a gas bearing incorporating spring oil 62 in which slits of the same shape are arranged at equal intervals.
  • the spring oil 62 and the top oil 63 are fitted inside the bearing housing 61, and the rotating shaft 64 is inserted into a cylinder formed by the top oil 63.
  • the spring oil 62 When the spring oil 62 is rolled into a cylindrical shape having a diameter smaller than that of the housing 61, and is loosened after being placed in the cylinder of the housing, the spring oil 62 spreads by the panel force of the oil and adheres closely to the inner wall. At this time, the position of the slit 67 formed in the spring oil 62 becomes a polygonal cylindrical shape in contact with the inner wall as a ridgeline, and an elastic beam is formed between adjacent ridgelines.
  • top oil 63 When the top oil 63 is also rolled into a cylindrical shape having a diameter smaller than that of the housing 61 and inserted into the spring oil 62 to be loosened, the spring oil 62 is pressed and spread from the inside by its own panel force.
  • the length of the top oil 63 is such that it almost reaches the end face of the locking mechanism 66 after making one round inside the housing 61. Both ends of the top oil 63 are fixed to the inner wall of the housing 61 by a locking mechanism 66 as shown in FIG.
  • the spring oil 62 is formed of a thin, elastic metal flat plate having a thickness of several hundred ⁇ m.
  • the spring oil 62 is formed in a rectangular shape and has a longitudinal direction and a lateral direction.
  • the short direction of the spring oil 62 is a direction that is substantially parallel to the axis of the rotary shaft when mounted in the housing 61.
  • a plurality of slits 67 having the same shape are arranged at equal intervals in the longitudinal direction of the spring oil 62, and the slit 67 has a length in the longitudinal direction (slit length) of the slit in the short direction of the spring oil 62,
  • the spring foil 62 has a slit width (slit width) in the longitudinal direction.
  • the slit 67 When the spring oil 62 is bent, the slit 67 receives the bending deformation. It is distributed between the bending deformation and the bending deformation received by the elastic beam formed between the slit 67 and the adjacent slit 67.
  • the smaller the slit length of the slit 67 with respect to the length of the spring oil 62 in the short direction the more the elastic beam has a planar shape. The bending deformation of Nguf oil 62 tends to be handled by both the slit 67 and the elastic beam.
  • the size of the gap between the inner wall of the top oil 63 and the outer wall of the cylindrical shaft 14 is an important factor governing the performance of the foil type hydrodynamic bearing. Therefore, it is important to manage the accuracy of the gap to a value higher than a predetermined value when manufacturing a foil type hydrodynamic fluid bearing.
  • the spring oil 62 and top oil 63 are unavoidable for the plate material used! /, And there is a plate thickness error, etc., so manufacturing error is expected in the production of foil type hydrodynamic fluid bearings. In the above, it is required to manage the accuracy of the gap to a value greater than a predetermined value. This allows foil type hydrodynamic bearings to function as designed within an acceptable range.
  • the spring-type hydraulic fluid bearing 62 must be made of a slit 67 in order to function as designed within an allowable range. It is preferable that most of the bending deformation of the spring oil 62 is handled by the slit 67 so that the elastic beam is bent in a V shape in a straight line in a cross-sectional view and the elastic beam is planar. It has been found.
  • the elastic beam of the bending deformation of the spring oil 62 is preferably 15% or less. If the bending ratio of the elastic beam is greater than 15%, the variation of the bending deformation of the elastic beam due to the plate thickness error, etc. increases, and the inner wall of the top oil 63 inscribed in the elastic beam that has been bent and deformed by the spring oil 62 And the size of the gap between the outer wall of the cylindrical shaft 14 fluctuates. Oil type hydrodynamic bearings will not function as designed.
  • the slit length ratio is 60%, the bending ratio of the elastic beam is 27%, and the slit length ratio is When it is 70%, the bending ratio of the elastic beam is 21%, when the slit length ratio is 80%, the bending ratio of the elastic beam is 18%, and when the slit length ratio is 80%, the bending ratio of the elastic beam is When the slit length ratio is 90%, the elastic beam bending ratio is 8%, and when the slit length ratio is 95%, the elastic beam bending ratio is 1% or less. It was. It was also found that when the slit length ratio exceeds 90%, the slit 67 is too long and the strength of the spring oil 62 cannot be secured.
  • the slit length ratio is 80% or more and 90% or less, and it is further desirable that the slit length ratio is 80% or more and 85% or less. Is done.
  • the elastic beam has an arc shape in cross-sectional view and the elastic beam has a cylindrical surface shape.Therefore, the gap between the inner wall of the top wall 63 and the outer wall of the cylindrical shaft 14 is reduced. The size of the gap will deviate from the expected tolerance.
  • the slit length ratio is greater than 90%, the strength of the spring oil 62 cannot be secured, and when the slit length ratio is less than 85%, the strength of the spring oil 62 is securely secured. be able to.
  • the groove width (slit width) of the slit 67 is 1.0 or more times the thickness of the elastic metal plate forming the spring oil 62, or 1.0 times the thickness of the elastic metal plate. It is preferably not smaller.
  • the upper limit of the groove width of the slit 67 is determined so that the bending ratio of the elastic beam is 15% or less in consideration of the size of the gap between the slits 67 and the like. If the groove width of the slit 67 is smaller than 1.0 times the thickness of the elastic metal plate, the spring oil 62 will not bend into a V shape at the slit 67 when the spring oil 62 is bent and deformed. Therefore, the elastic beam is less likely to be straight when viewed in cross section, and the bending ratio of the elastic beam is greater than 15%.
  • the locking mechanism 66 is formed by forming a pair of triangular grooves 69 on the inner wall of the housing 61 back to back. It is. A ridge 70 left uncut between a pair of triangular grooves 69 is formed, and both sides of the ridge 70 become almost vertical stop walls 68! /.
  • the end portion of the top oil 63 falls into the triangular groove 69 and is pressed against the inner wall of the housing 61 by the bunker that tries to loosen the oil itself. In order to prevent it from coming off more reliably, it is preferable that both edges of the top oil 63 hit against the stop wall 68 and stop. /.
  • the top surface of the ridge 70 is the same as the inner surface of the top oil 63 when viewed from the viewpoint of the function of the force that is the same height as the inner surface of the housing 61 due to the convenience of the manufacturing process formed by digging the inner wall of the housing 61. You may protrude to the same Cf standing. The higher the peak 70 is, the more difficult it is for the top oil 63 to come off.
  • the bottom surface of the triangular groove 69 is formed as a surface in contact with the cross-sectional circle of the inner wall of the housing 61, and an end portion extending in a tangential direction from the cylindrical shape formed by the top oil 63 extends along the bottom surface. It is preferable that the edge hits the stop wall 68 and stops. By making the cylindrical force smoothly transition to the flat surface when the top foil 63 fits in the triangular groove 69, it can be prevented from bulging in the transition region. If there is a bulging portion, the top oil 63 comes into contact with the rotating shaft 64, which causes rotation failure, frictional heat generation, wear, etc., which is not preferable.
  • top oil 63 is not free end because both ends are constrained by friction with the inner wall of housing 61. Since the air introduction opening is provided between the puff oil 63 and the rotating shaft 64, unlike the bearing of the first embodiment, the air layer 65 is generated even if the rotating shaft 64 rotates in either the left or right direction. Is possible.
  • the air layer 65 develops and the top oil 63 is pressed against the inner wall of the housing 61. Therefore, the elastic beam of the spring oil 62 is deformed during high-speed rotation, and the rotating shaft 64 is supported by strong rigidity. Will come to be.
  • the triangular groove 69 is made to have an appropriate depth so that the supply of air is facilitated so that the air layer 65 is generated and generated smoothly.
  • the locking mechanism 66 has a very simple structure as compared with the conventional method in which one end of the top oil is fixed to the inner wall of the housing by screws or welding, and has a special structure for locking to the top oil 63.
  • the assembly force can also be saved without the need for machining.
  • it is easy to disassemble the bearing device, and it is easy to modify it in accordance with maintenance and change of conditions.
  • the spring oil 62 can be sufficiently supported by being covered with the top oil 63 and pressed, but it is supported in the same way as the top oil 63 using the locking mechanism 66, and the top oil 63 is supported from above. Then, when assembling the bearing device, spring oil 6
  • top oil 63 can be inserted after 2 is fixed.
  • FIGS. 18 and 19 are perspective views showing a state in which a mechanism for reliably preventing the top oil 63 from falling off is added. In both cases, the top oil 63 is prevented from moving off the inner wall of the bearing housing 61 in the axial direction.
  • the stopper 71 is screwed to the side end of the peak 70 of the locking mechanism to restrict the movement of the top oil 63 in the width direction.
  • the upper edge of the stopper 71 is lowered from the upper surface of the peak 70 so that the movement of the rotating shaft is not hindered.
  • FIG. 19 shows an example in which a flange 72 that holds the edge of the housing 61 is provided at the end of the top oil 63. Even if the top oil 63 moves in the axial direction due to some force action, the heel 72 is blocked by the edge and cannot move. In either case, the top oil 63 can be reliably prevented from falling off by attaching a simple mechanism.
  • FIG. 20 is a cross-sectional view showing a state in which the locking mechanism 66 of the present embodiment is applied to the dynamic pressure gas bearing 7 using the bump oil 73.
  • the locking mechanism 66 of the present embodiment is not limited to the case where the spring oil of the present invention is used, and as shown in FIG. Needless to say, it can also be used in a bearing device using fufu oil.
  • locking mechanism 66 needs to be arranged in the bearing housing 61, and a plurality of locking mechanisms are installed at equal intervals, and the support rigidity is adjusted. As shown, locking mechanisms may be placed at appropriate intervals to cause unequal support rigidity, for example, to suppress vibrations, or to respond to changes in starting load and rotating load. .
  • FIG. 22 is a cross-sectional view schematically showing a dynamic pressure gas bearing of the tenth embodiment
  • FIG. 23 is a plan view of a spring oil used in this embodiment.
  • the dynamic pressure gas bearing 8 of this embodiment uses a spring oil 82 as shown in FIG.
  • the spring oil 82 is formed by arranging the tongs 86 formed with slits on three sides of the rectangle on the entire surface.In the figure, three rows of tongs 86 of the same shape are arranged in the width direction. Of course, there are 15 rows! /, But it is not limited to these arrangements.
  • the spring oil 82 is inserted inside the bearing housing 81, and the top oil 83 having a cylindrical shape is fixed to the inner wall by the locking mechanism 84, and the rotary shaft 85 is inserted into the top oil 83, and the bearing 8 Is configured.
  • the tongue 86 extends tangentially from the curved surface of the spring oil 82 and hits the inner wall of the housing 81 to act as a panel. Then, a support rigidity is given to the rotary shaft 85 through the top oil 83.
  • the tongue 86 not only exhibits a panel action, but also slides on the inner wall surface of the housing 81 when pressed, and thus has the ability to suppress vibration by friction damping during high-speed rotation.
  • the tongue 86 is simply formed by cutting the spring oil 82, and unlike the leaf oil, it does not need to be plastically deformed. The incision can be made easily and with high precision by etching in the same manner as the slit of the spring oil used in Example 1 or the like.
  • FIG. 24 and FIG. 25 are drawings showing an example in which the shape of the tongue formed on the spring oil 82 is changed.
  • the spring oil 82 in FIG. 24 is an example in which the width of the rectangular tongue is changed in the axial direction.
  • the central tongue 87 is formed wider, and the width of the tongues 88 at both ends is smaller than the central one.
  • the spring oil 82 in FIG. 25 has a triangular tongue formed by slitting two sides of the triangle, and the central tongue 89 has a larger triangle than the tongue 90 at both ends.
  • the triangular tongs 89 and 90 support the more the high-speed rotation, as the effective support position of the tongs widens toward the base side of the tongue as the distance between the flange 82 and the housing 81 becomes shorter. It has a characteristic that the rigidity increases rapidly.
  • the tongue 90 since the tongue 90 is short in the portion close to the end of the bearing and cannot be strongly pressed against the housing 81, it has a function of preventing the one piece contact where the supporting rigidity is weak.
  • FIG. 26 is a plan view of the spring oil used in the dynamic pressure gas bearing of the eleventh embodiment.
  • the spring oil used in this embodiment has a slit portion with a wide cut-off shape, and is adjacent to the spring oil.
  • the distance force to the ridgeline of the slit to be changed varies depending on the distance of the end force of the oil flat plate, so that the rigidity is changed.
  • the protruding shape in the slit gradually contacts the inner wall of the housing step by step, finally increasing the support rigidity and finally rotating at high speed. Since the elastic beam is pressed against the wall, it becomes extremely strong and rigid, and the change in rigidity accompanying rotation is large.
  • the slit shape is a wide slit 93 such as a semicircular shape, a bow shape or a trapezoidal shape
  • the end of the wide slit 93 is the inner wall of the housing while the top oil does not spread.
  • a force with which a long span beam is formed as a fulcrum in contact with the surface and a relatively weak rigidity is given. Since the elastic beam does not act at the center, there is a stiffness distribution in the axial direction.
  • the center position of the slit comes into contact with the inner wall of the housing, and the short span beam becomes effective and the rigidity increases, and the rigidity changes with rotation.
  • the rigidity distribution and the change state vary depending on the shape of the slit.
  • FIG. 27 is a cross-sectional view schematically showing a dynamic pressure gas bearing of a twelfth embodiment.
  • the dynamic pressure gas bearing 9 of this embodiment uses a double spring oil.
  • a polygonal spring oil 96 is inserted into the housing 95, a polygonal spring oil 97 having the same number of angles is inserted inside, and a top oil 98 is further inserted.
  • the angular force of the inner spring oil 97 is preferably arranged so that it hits the central portion of the elastic spring 96 of the outer spring oil 96.
  • the inner and outer spring foils are built on one elastic metal plate and rolled into a double and set in the housing. You may do it. Further, one end of the spring oil may be fixed to the inner wall of the knowing. Needless to say, the spring oil is not limited to double, but may have a multiple structure with an appropriate number of spring foil layers.
  • the bearing is manufactured so that it can be supported with moderate rigidity up to high speed rotation. can do.
  • FIG. 28 is a cross-sectional view showing a dynamic pressure gas bearing in which a plurality of spring oils are arranged so as to overlap each other and the vibrations of the oils are rubbed together to attenuate the vibration of the bearings. It is.
  • spring oils 100 are arranged so that one end is fixed to the inner wall 99 of the nosing at equal intervals, and overlap each other half, and the top oil 101 is inserted therein.
  • the top oil 101 acts on the spring oil 100 and slides to each other, so that a frictional resistance is generated and the vibration can be attenuated.
  • FIG. 29 is a cross-sectional view schematically showing a dynamic pressure gas bearing of the fourteenth embodiment.
  • the dynamic pressure gas bearing of the present embodiment was assembled so that the inner hole cross section of the bearing housing 102 was formed into a polygon, and the slit of the spring oil 103 was positioned at the ridgeline 105 formed at the apex of the polygon. Is.
  • the number of ridge lines in the polygonal cylinder formed by the inner bore of the Uzing 102 is twice the number of ridge lines of the polygon cylinder formed by the spring oil 103, and the elastic beam formed by the spring oil 103 makes the ridge line of the housing 1 It is preferable to place them one by one.
  • each of the above embodiments a gas bearing that can be used in the air is taken up.
  • each of the above structures can be used in oil or water as it is. Since fluid bearings using oil or water are used at a relatively low temperature, a thin flat plate can be formed of a polymer material such as tetrafluoroethylene instead of metal.

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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)

Abstract

L’invention se rapporte à un palier à gaz de type feuille capable de fournir d’excellentes performances de palier en utilisant une feuille à ressort de fabrication facile et dotée d’une excellente productivité et un palier à gaz à pression dynamique capable d’éliminer une restriction dans une direction de pivotement en utilisant une structure supérieure de fixation en ressort pouvant être facilement installée. La feuille à ressort (12) formée d’une plaque élastique mince et plate comportant une pluralité de fentes (16) est ajustée à la paroi intérieure d’un corps de palier (11), une feuille supérieure (13) est disposée sur l’intérieur de la feuille à ressort et un arbre de rotation (14) est disposé sur l’intérieur de la feuille supérieure. La feuille à ressort (12) est pliée pour s’adapter aux positions des fentes (16) afin de former un grand nombre de faisceaux élastiques en contact avec l’intérieur de la paroi intérieure et l’arbre de rotation (14) est soutenu élastiquement par les faisceaux élastiques.
PCT/JP2005/003314 2004-08-17 2005-02-28 Palier fluide à pression dynamique Ceased WO2006018916A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004-237380 2004-08-17
JP2004237380A JP3636328B1 (ja) 2004-08-17 2004-08-17 動圧流体軸受

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WO2006018916A1 true WO2006018916A1 (fr) 2006-02-23

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JP (1) JP3636328B1 (fr)
KR (1) KR100807889B1 (fr)
CN (1) CN100510443C (fr)
WO (1) WO2006018916A1 (fr)

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EP3597945A4 (fr) * 2017-03-15 2021-01-13 IHI Corporation Palier à feuilles radiales
WO2019172378A1 (fr) * 2018-03-07 2019-09-12 株式会社Ihi Palier à feuille radiale
CN111788399A (zh) * 2018-03-07 2020-10-16 株式会社Ihi 径向箔轴承
EP3763956A4 (fr) * 2018-03-07 2021-12-15 Ihi Corporation Palier à feuille radiale
EP3763955A4 (fr) * 2018-03-07 2021-12-15 Ihi Corporation Palier radial à feuilles
US11306772B2 (en) 2018-03-07 2022-04-19 Ihi Corporation Radial foil bearing
CN111577755A (zh) * 2020-06-29 2020-08-25 青岛科技大学 一种主动控制动压力的动压轴承

Also Published As

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JP3636328B1 (ja) 2005-04-06
CN1898476A (zh) 2007-01-17
KR20060037254A (ko) 2006-05-03
CN100510443C (zh) 2009-07-08
KR100807889B1 (ko) 2008-02-27

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