WO2011122210A1 - 転がり軸受装置 - Google Patents
転がり軸受装置 Download PDFInfo
- Publication number
- WO2011122210A1 WO2011122210A1 PCT/JP2011/054695 JP2011054695W WO2011122210A1 WO 2011122210 A1 WO2011122210 A1 WO 2011122210A1 JP 2011054695 W JP2011054695 W JP 2011054695W WO 2011122210 A1 WO2011122210 A1 WO 2011122210A1
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- WO
- WIPO (PCT)
- Prior art keywords
- oil
- retaining member
- inner ring
- bearing device
- peripheral surface
- Prior art date
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Classifications
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
- F16C33/6607—Retaining the grease in or near the bearing
- F16C33/6611—Retaining the grease in or near the bearing in a porous or resinous body, e.g. a cage impregnated with the grease
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/664—Retaining the liquid in or near the bearing
- F16C33/6648—Retaining the liquid in or near the bearing in a porous or resinous body, e.g. a cage impregnated with the liquid
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
- F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
- F16C19/543—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact in O-arrangement
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
- F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
- F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
- F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner ring
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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
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
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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
- F16C2326/00—Articles relating to transporting
- F16C2326/47—Cosmonautic vehicles, i.e. bearings adapted for use in outer-space
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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
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
- F16C25/08—Ball or roller bearings self-adjusting
- F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
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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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/303—Parts of ball or roller bearings of hybrid bearings, e.g. rolling bearings with steel races and ceramic rolling elements
Definitions
- the present invention relates to a rolling bearing device used in an environment where a normal fluid lubricant (for example, grease) cannot be applied, and more particularly to a rolling bearing device having an inner ring spacer.
- a normal fluid lubricant for example, grease
- Double row angular contact ball bearings are used as bearing devices used in low-temperature and high-speed rotation environments such as rocket engine liquid fuel turbo pumps, and in rolling environments such as space equipment. There is a case.
- This bearing device has a structure in which angular ball bearings are arranged in a double row on the outer peripheral surface of the main shaft, which is a rotating shaft, and the inner ring is positioned between the double row angular ball bearings for axial positioning of the inner ring and the outer ring.
- a spacer and an outer ring spacer are incorporated.
- the former oil-lubricated rolling bearing device is provided with an oil sump for storing lubricating oil in the inner ring spacer, for example.
- the latter solid-lubricated rolling bearing device includes, for example, a cylindrical rolling element spacer made of a material having self-lubricating property between adjacent rolling elements of a plurality of rolling elements arranged between an inner ring and an outer ring. Lubricant powder that rubs and scatters from the surface of the rolling element spacer that contacts the rolling element during rotation is supplied into the bearing (see Patent Document 2).
- the inner ring spacer is constituted by two members, a cylindrical inner spacer and an outer spacer, and an oil sump chamber for accommodating lubricating oil is formed between the two members.
- the lubricating oil sealed in the oil sump chamber is scattered from the spacer end surface side contacting the inner ring to the inner ring side by centrifugal force when the bearing rotates, and flows into the bearing.
- Such an oil lubrication structure increases the absolute amount of lubricant that contributes to lubrication during rotation of the bearing because the lubricating oil sealed in the oil reservoir in the inner ring spacer increases the life of the rolling bearing device, and , Improve safety.
- the solid-lubricated rolling bearing device increases the absolute amount of lubricant that contributes to lubrication during bearing rotation by increasing the number of rolling element spacers having self-lubricating properties that are arranged with the rolling elements inside the bearing. Can be easily done.
- a structure in which a rolling element spacer only having a function as a solid lubricant supply source is additionally arranged inside the bearing is not preferable in terms of an increase in the number of bearing components.
- An object of the present invention is to provide a rolling bearing device that can increase the absolute amount of lubricant that contributes to lubrication during bearing rotation without increasing the number of parts.
- the present invention provides a stationary outer ring, a rotating inner ring, a plurality of rolling elements interposed between the inner ring raceway surface and the outer ring raceway surface, and a cage for holding the rolling elements.
- the inner ring spacer is made of a porous material of metal or resin, and has lubricating oil in the holes.
- An oil retaining member is provided, and lubricating oil is supplied into the bearing from the oil retaining member by a centrifugal force when the bearing rotates.
- the oil retaining member made of a metal or resin porous body has a large number of minute pores communicating with each other.
- the lubricating oil is retained in the numerous holes of the oil retaining member.
- the lubricating oil impregnated in the oil retaining member scatters to the outer diameter side by centrifugal force acting on the oil retaining member that rotates together with the shaft when the bearing rotates, and is supplied into the bearing for oil lubrication.
- the spacer which is an indispensable component for the bearing function, is utilized as a supply source of the lubricating oil, so that the number of components does not increase significantly.
- the oil retaining member is a porous body and has a large amount of lubricating oil inside, and it is possible to easily respond to the demand for an increase in the amount of lubricating oil by increasing the thickness of the oil retaining member. It is. In order to meet this demand, it is not necessary to reduce the thickness of the constituent members of the spacer as in the prior art, and the strength and the machinability are improved. Since the oil retaining member made of a porous material can be manufactured by molding, it can be manufactured accurately and at low cost even if the oil retaining member becomes thin.
- the surface of the oil retaining member is provided with an oil supply port having a surface opening ratio larger than that of the other portion, and the oil supply port is opened to the outer peripheral surface of the inner ring spacer via the oil supply passage. It is desirable to seal the outer peripheral surface of the inner ring spacer except for. As a result, a large amount of lubricating oil retained in the oil retaining member is not supplied into the bearing from the entire outer peripheral surface of the inner ring spacer at once, but only a small amount of lubricating oil that oozes out from the oil retaining port of the oil retaining member. Contributes to lubrication inside the bearing device through the oil supply passage. Therefore, it becomes possible to supply lubricating oil stably for a long period of time.
- the inner ring spacer is provided with a spacer cover that has a contact portion with the end surface of the inner ring and covers the outer peripheral surface of the oil retaining member, the oil supply passage is opened to the inner peripheral surface and the outer peripheral surface of the spacer cover, and the oil supply It is desirable that the inner diameter side opening of the passage is opposed to the oil supply port of the oil retaining member. As a result, the original function of positioning the inner ring in the axial direction can be maintained, and the lubricating oil can be stably supplied to the bearing device by the oil retaining member.
- the oil supply passage can be formed at low cost.
- the inner ring spacer can be provided with a first oil sump that holds lubricating oil adjacent to the oil retaining member and whose outer diameter side is sealed with a spacer cover (see FIGS. 5 to 9).
- a first oil sump that holds lubricating oil adjacent to the oil retaining member and whose outer diameter side is sealed with a spacer cover.
- a first oil sump is provided between the outer peripheral surface of the sleeve member and the inner peripheral surface of the spacer cover. It can also be formed (FIG. 9).
- the linear expansion coefficient of the spacer cover is made equal to the linear expansion coefficient of the oil retaining member, an oil reservoir is formed between the inner peripheral surface of the spacer cover and the outer peripheral surface of the oil retaining member even in a low temperature or high temperature atmosphere. Such a gap is not formed. Therefore, it is possible to prevent a situation in which the lubricating oil is excessively supplied to the oil supply passage at a time.
- the oil retaining member and the spacer cover are formed of the same material, for example, an iron-based or stainless-based sintered metal, etc., the linear expansion coefficient of the oil retaining member and the spacer cover becomes equal within the operating temperature range. The formation of the gap can be prevented more reliably.
- the oil retaining member and the spacer cover constitute the inner ring spacer.
- the oil retaining member (only) can also constitute the inner ring spacer (see FIG. 4).
- the outer peripheral surface of the oil retaining member is sealed except for the oil supply port, so that excessive supply of oil from the entire outer peripheral surface is prevented, while only an appropriate amount of lubricating oil oozing out from the oil supply port is provided in the bearing device. It becomes possible to supply inside.
- the sealing of the outer peripheral surface can be performed by machining such as grinding.
- the lubricating oil that has oozed out into the chamfered portion can be reliably supplied to the inside of the bearing device through the oil supply passage. . If the area of the chamfered portion is too small, the amount of lubricating oil that oozes out is reduced, resulting in poor lubrication. Therefore, the dimension of the chamfered portion is preferably C0.5 or more.
- the inner ring and the oil retaining member are fitted to the outer peripheral surface of the shaft having a hollow portion, and the hollow portion of the shaft is used as a third oil reservoir that holds lubricating oil, and the inner diameter side of the shaft opens to the third oil reservoir.
- shaft which the outer diameter side opposes the inner peripheral surface of an oil retaining member can also be provided (refer FIG. 8). In this case, an oil reservoir with a larger volume can be secured, and the bearing life can be further increased.
- the porosity inside the oil retaining member it is desirable to set the porosity inside the oil retaining member to 10% to 30%. If the porosity is less than 10%, the amount of impregnated oil is insufficient, and if it exceeds 30%, the material strength is insufficient.
- a solid lubricating film such as PTFE for reducing initial friction on at least one of the inner ring raceway surface, the outer ring raceway surface and the rolling element surface.
- a solid lubricating film such as PTFE on the surface of the cage.
- the present invention can be applied to a liquid fuel turbo pump of a rocket engine or a rolling bearing device used in a vacuum environment of space equipment.
- the absolute amount of lubricating oil that contributes to lubrication can be increased without increasing the number of bearing components and without reducing the thickness of the inner ring spacer. Can be improved. At this time, the strength of the spacer is not insufficient, and the spacer can be easily manufactured.
- FIG. 6 is a partial perspective view of the inner ring spacer shown in FIG. 5. It is sectional drawing which shows the rolling bearing apparatus integrated in the axis
- the rolling bearing device shown in FIG. 1 is applied to a liquid fuel turbo pump bearing of a rocket engine used in a low-temperature and high-speed rotation environment, and includes a double-row angular ball bearing 1.
- Each angular ball bearing 1 includes a pair of inner rings 2 fitted and fixed to a rotating shaft (20: see FIGS. 7 and 8) and a pair of outer rings fitted and fixed to the inner peripheral surface of an outer ring spacer 10. 3.
- a plurality of rolling elements 4 are arranged with contact angles between the raceway surface 2a of the inner ring 2 and the raceway surface 3a of the outer ring 3, and the cage 5 holds the rolling elements 4 at equal intervals in the circumferential direction.
- An inner ring spacer 6 is installed between the pair of inner rings 2.
- the inner ring spacer 6 has a cylindrical shape, and both end surfaces are in contact with the inner end surfaces of the double-row inner rings 2 and 2 to position the inner ring 2 in the axial direction.
- the inner ring 2 and the inner ring spacer 6 fitted to the shaft rotate integrally with the shaft.
- the inner ring 2 has a form in which a shoulder portion on the inner side of the bearing that is not in angular contact with the rolling element 4 is cut off. Therefore, the surface of the rolling element 4 faces the outer peripheral surface of the inner ring spacer 6 inside the bearing device.
- a protruding portion 10a protruding in the inner diameter direction is provided at the center portion of the outer ring spacer 10, and an elastic member for applying a bearing preload between both end surfaces of the protruding portion 10a and the end surfaces of both outer rings 3, for example, A disc spring 11 is arranged.
- seal members On both sides in the axial direction of the bearing device, scattering of lubricant to the outside of the bearing is prevented by seal members (not shown).
- the outer diameter end of the seal member is fitted into the attachment groove 12 on the inner peripheral surface of the shoulder portion of the outer ring 1.
- a non-contact seal is formed between the lip provided at the inner diameter end of the seal member and the seal groove 13 formed on the outer peripheral surface of the shoulder portion of the inner ring 2.
- the sealing member can be omitted.
- Fluid lubricant such as grease cannot be sealed in the internal space of the bearing device due to problems such as grease evaporation.
- any one or more or all of the surfaces of the inner ring raceway surface 2a, the outer ring raceway surface 3a, and the rolling element 4 are made of PTFE or the like.
- a solid lubricating film is formed.
- a solid lubricating film made of PTFE or the like is formed on the entire surface including the pocket inner surface of the cage 5.
- the inner ring 2, the outer ring 3, and the rolling element 4 can be formed of stainless steel, for example, martensitic stainless steel.
- the rolling element 4 can also be formed with a ceramic. If the rolling element 4 is made of ceramic, the centrifugal force acting on the rolling element during rotation of the bearing is reduced, and the contact surface pressure of the outer ring can be reduced, so that the life of the bearing can be extended.
- the cage 5 is made of resin, and is formed of a composite material in which glass fiber or carbon fiber is added to PEEK or the like, for example.
- the cage 5 can be formed of a metal material such as carburized steel, aluminum alloy, stainless steel, or copper alloy.
- the inner ring spacer 6 includes two members, a cylindrical oil retaining member 7 and a cylindrical spacer cover 8 fitted to the outer peripheral surface 7 b of the oil retaining member 7. .
- the oil retaining member 7 is made of a porous body of metal or resin and has a large number of minute pores communicating with each other. By impregnating the oil retaining member 7 with the lubricating oil, the lubricating oil is held in each hole.
- the oil retaining member 7 is made of, for example, a sintered metal.
- the sintered metal is obtained by molding metal powder with a mold (powder molding) and then sintering at a predetermined temperature.
- the molding conditions such as the pressing pressure are set so that the porosity inside the sintered metal after sintering is in the range of 10 to 30%, preferably about 20%. If it is less than 10%, the oil content of the lubricating oil is insufficient, and if it exceeds 30%, the strength is insufficient.
- chamfered portions 7d are molded at outer diameter ends of both end surfaces of the molded body.
- the taper angle of the chamfered portion 7d after sintering is about 45 degrees, and the dimension is C0.5 or more.
- the sintered metal iron-based, copper-based, iron-copper-based, stainless-based, and tungsten-based materials are known, and any of these can be used, but in order to minimize the linear expansion coefficient of the oil retaining member 7, It is preferable to use an iron-based or stainless-based sintered metal.
- the oil retaining member 7 is obtained by subjecting the inner peripheral surface 7a, the outer peripheral surface 7b, and the both end surfaces 7c of the sintered metal after sintering to machining such as turning as finishing and finishing to a specified dimension. At this time, machining is not performed on the chamfered portion 7d, and a surface (molded surface) formed by a mold at the time of powder molding is left as it is. By machining, the surface openings of the inner peripheral surface 7a, outer peripheral surface 7b, and both end surfaces 7c of the oil retaining member 7 are crushed, and the surface opening ratio is reduced to less than 10%.
- the surface porosity of the chamfered portion 7d is maintained at the porosity (10% to 30%) inside the sintered metal after sintering, and the other surface of the oil retaining member 7, for example, the inner peripheral surface 7a. It becomes larger than the surface area ratio of the outer peripheral surface 7b and the both end surfaces 7c. As long as the surface opening ratio becomes larger than the other surface of the oil retaining member 7, the chamfered portion 7d may be subjected to machining such as turning to adjust the surface opening ratio.
- the oil retaining member 7 after machining is impregnated with lubricating oil.
- lubricating oil a synthetic oil having good lubricity even at a low temperature ( ⁇ 50 ° C. or lower), for example, a fluorinated oil is used.
- the impregnation of the lubricating oil may be performed in a state where the oil retaining member 7 is incorporated in the inner periphery of the spacer cover 8 or in a state where the oil retaining member 7 alone is not assembled into the inner periphery of the spacer cover 8. Also good.
- the spacer cover 8 is formed in a cylindrical shape from a solid (no void) resin or metal material.
- the axial length L2 of the spacer cover 8 satisfies the relationship of L1 ⁇ L2 with respect to the axial length L1 of the oil retaining member 7.
- recesses 8 a are formed by cutting out partial circumferential regions thereof.
- the recesses 8a are intermittently formed at a plurality of locations in the circumferential direction. Therefore, a plurality of recesses 8a and a projection 8b between adjacent recesses 8a are alternately formed on both end faces of the spacer cover 8. Has been.
- Both convex portions 8 b on both end surfaces serve as contact portions that contact the end surface of the inner ring 2.
- the step X (see FIG. 3) between the concave portion 8a and the convex portion 8b is desirably the same as the chamfer dimension C or smaller than the chamfer dimension C.
- the inner ring spacer 6 composed of the oil retaining member 7 and the spacer cover 8 is interposed between the pair of inner rings 2, and the end surfaces of the convex portions 8 b formed on both end surfaces 7 c of the oil retaining member 7 and both end surfaces of the spacer cover 8. Is brought into contact with the end face of the inner ring 2.
- both inner rings 2 are positioned in the axial direction, and the non-contact portion between the inner ring 2 and the spacer cover 8, that is, between the inner surface of the spacer cover 8 and the inner surface of the recess 8 a and the end surface of the inner ring 2,
- An oil supply passage S is formed which opens to the outer peripheral surface and whose inner diameter side opening faces the chamfered portion 7d of the oil retaining member 7 in the radial direction.
- the lubricating oil impregnated in the oil retaining member 7 oozes out from the surface of the chamfered portion 7d and moves to the outer diameter side through the oil supply passage S. Scatter.
- the scattered lubricating oil reaches the surface of the rolling element 4 facing the radial direction of the oil supply passage S, and further transfers to the inner ring raceway surface 2a and the outer ring raceway surface 3a to lubricate the inside of the bearing.
- the surface opening ratio of the chamfered portion 7d of the oil retaining member 7 is larger than that of the other surface of the oil retaining member 7, so that the lubricating oil oozes out from the chamfered portion 7 smoothly. . Therefore, the chamfered portion 7 d functions as an oil supply port of the oil retaining member 7.
- the inner ring spacer 6 which is an indispensable part for the bearing function is used as a supply source of lubricating oil, the number of parts does not increase significantly.
- the oil retaining member 7 is a porous body and has a large amount of lubricating oil inside, and in response to a request for an increase in the amount of lubricating oil, it is easy to increase the thickness of the oil retaining member 7. It is possible. In order to meet this demand, it is not necessary to reduce the thickness of the spacer as in the prior art. Therefore, it is possible to improve the bearing life while avoiding a decrease in strength of the inner ring spacer 6 and an increase in processing cost. By increasing the thickness of the oil retaining member, the strength and the machinability become better.
- the outer peripheral surface 7a of the oil retaining member 7 is covered with the spacer cover 8 and the outer peripheral surface of the inner ring spacer 6 is kept in a sealed state, the outer peripheral surface 7a of the oil retaining member 7 A large amount of lubricating oil is not supplied to the inside of the bearing device at a time from the whole, and only a small amount of lubricating oil that oozes sequentially from the chamfered portion 7d can contribute to lubrication. Therefore, an appropriate amount of lubricating oil can be supplied stably for a long period of time, and the bearing life can be further improved.
- the supply amount and supply time of the lubricating oil to the inside of the bearing can be freely changed, and the optimum according to the application of the bearing device. It becomes possible to easily obtain a lubrication state.
- the oil retaining member 7 may be thinned by configuring the inner ring spacer 6 with two members, the oil retaining member 7 can be manufactured by molding even in such a case, so that the oil retaining member 7 can be manufactured at a low cost with high accuracy. The oil member 7 is obtained.
- the rolling bearing device of this embodiment is used in a range from a low temperature atmosphere of ⁇ 50 ° C. or lower to a high temperature atmosphere of 150 ° C.
- a low temperature atmosphere of ⁇ 50 ° C. or lower if used in such a wide range of ambient temperatures, if the difference between the linear expansion coefficient of the oil retaining member 7 and the linear expansion coefficient of the spacer cover 8 is large, the outer peripheral surface 7b of the oil retaining member 7 and the spacer cover 8 A gap is formed between the inner peripheral surface.
- Such a gap becomes an oil reservoir, which is not preferable because a large amount of lubricating oil is supplied from the oil supply passage S at a time.
- the oil retaining member 7 has a linear expansion coefficient equivalent to the linear expansion coefficient of the spacer cover 8 so that this kind of gap is not formed over the entire temperature range when used in the above wide ambient temperature. It is desirable to form with material (for example, the material of the same material). Therefore, when the oil retaining member 7 is formed of a sintered metal such as iron or stainless steel as described above, the spacer cover 8 can also be formed of the same kind of sintered metal. Thereby, not only the oil retaining member 7 but also the linear expansion coefficient of the spacer cover 8 can be reduced, so that the formation of the gap can be prevented more reliably. In this case, in order to prevent oil leakage from the outer peripheral surface of the spacer cover 8, it is preferable to perform a sealing process on the entire outer peripheral surface of the spacer cover 8.
- FIG. 4 shows an example, in which the inner ring spacer 6 is formed only by the oil retaining member 7 made of oil-impregnated sintered metal. Also in this case, the inner peripheral surface 7a ', the outer peripheral surface 7b', and the both end surfaces 7c 'of the oil retaining member 7 are machined, while the chamfered portion 7d' is not machined and remains as a molding surface.
- the outer peripheral surface 7b 'excluding the chamfered portion 7d' is carefully machined to seal the surface openings (reducing the surface opening ratio to near 0%).
- the outer peripheral surface of the inner ring spacer 6 is hermetically sealed, and oil scattering from the outer peripheral surface 7 b ′ of the oil retaining member 7 is reduced.
- the chamfered portion 7d ′ serves as an oil supply port
- a gap between the chamfered portion 7d ′ and the end surface of the inner ring 2 serves as an oil supply passage S, and lubricating oil is supplied from the oil supply passage S to the inside of the bearing device.
- the outer peripheral surface 7 b ′ of the oil retaining member 7 excluding the chamfered portion 7 d ′ may be covered with a resin film.
- the inner ring spacer 6 is composed of only the oil retaining member 7, the number of parts can be further reduced. Further, by making the oil retaining member 7 the size of the oil retaining member 7 and the spacer cover 8 shown in FIG. 1, the lubricating oil contained in the oil retaining member 7 by the volume of the spacer cover 8 is obtained. The amount can be increased, and the durability life of the bearing device can be further improved. Further, there is no gap due to the difference in linear expansion coefficient between the oil retaining member 7 and the spacer cover 8, and the room for selecting the material of the oil retaining member 7 is expanded.
- the oil retaining member 7 can also be formed of a known porous resin.
- the resin material of this kind of porous resin those made of polyolefin resin, polyamide resin, polyacetal resin, fluorine resin, polyether ether ketone resin, polyethylene terephthalate resin, polyethylene terephthalate resin, biodegradable resin, etc. can be used. is there. After molding these porous resins (after machining the outer peripheral surface, inner peripheral surface, and both end surfaces if necessary), the oil retaining member 7 can be obtained by impregnating the lubricating oil.
- the chamfered portions 7d and 7d 'are used as they are on the molding surface that is not machined, and the oil supply port with a larger surface opening ratio than other parts is used, so that the required amount of lubricating oil can be supplied smoothly into the bearing. It becomes possible to do.
- FIG. 5 and 6 show another embodiment of the present invention.
- a first oil sump 23 whose outer diameter side is sealed by the spacer cover 8 is provided adjacent to the oil retaining member 7.
- an annular first groove is formed between the outer peripheral surface of the oil retaining member 7 and the inner peripheral surface of the spacer cover 8 by forming an annular groove 7e on the outer peripheral surface 7b of the oil retaining member 7.
- Lubricating oil is stored in the first oil reservoir 31 at the stage of assembly of the bearing device (for example, after the spacer cover 8 is fitted to the outer periphery of the oil retaining member 7).
- the first oil sump 31 can be formed not only in a ring shape, but also in one place or a plurality of places in the circumferential direction.
- the bottom surface and the side surface of the groove 7e need to have a large surface opening ratio so that the lubricating oil is smoothly absorbed by the oil retaining member 7. Therefore, it is desirable to leave these surfaces as molded surfaces.
- these surfaces may be subjected to machining such as turning. However, grinding is not preferable because the surface area ratio becomes excessively small. Since the basic configuration of the rolling bearing device shown in FIGS. 5 and 6 is the same as that of the embodiment shown in FIG. 1 except for the shape of the oil retaining member 7, the same members are denoted by the same reference numerals and redundant description is given. Omitted.
- the chamfered portions 7 d provided at both ends of the oil retaining member 7 are formed surfaces and function as an oil filler port. Therefore, the lubricating oil that has oozed out into the chamfered portion 7d is supplied to the internal space of the bearing device via the oil supply passage S by centrifugal force. Since the lubricating oil retained by the first oil reservoir 31 is sequentially replenished to the oil retaining member 7, the total amount of oil retained by the inner ring spacer 6 increases, and the bearing life can be increased.
- FIG. 7 shows a state where the rolling bearing device shown in FIG.
- a second oil reservoir 32 is provided on the outer peripheral surface of the shaft 20 facing the inner peripheral surface of the oil retaining member 7.
- the second oil reservoir 32 can be formed in an annular shape, or can be provided at one or a plurality of locations in the circumferential direction.
- FIG. 8 shows a state in which the rolling bearing device shown in FIG.
- the shaft 20 is provided with a hollow portion 21 that opens at one end thereof, and is provided with a radial through-hole 22 whose inner diameter side opens into the hollow portion 21.
- the outer diameter side of the through hole 22 opens to the outer peripheral surface of the shaft 20 facing the inner peripheral surface of the oil retaining member 7.
- Lubricating oil is stored in the hollow portion 21 when the bearing device is assembled, and the opening of the hollow portion 21 is sealed with a lid member 24 via a seal 23 such as an O-ring.
- the through hole 22 can be provided at one place or a plurality of places in the circumferential direction.
- the hollow portion 21 serves as the third oil reservoir 33, and the lubricating oil is supplied from the third oil reservoir 33 to the oil retaining member 7 through the through hole 22, thereby further increasing the bearing life. be able to.
- FIGS. 7 and 8 exemplify the case where the bearing device shown in FIG. 5 is mounted on the shaft 20, the respective configurations shown in FIGS. 7 and 8 are the same for the bearing device shown in FIGS. Can be applied to.
- FIG. 9 shows another embodiment of the present invention.
- the inner ring spacer 6 is fitted and fixed to the oil retaining member 7, the spacer cover 8, and the outer periphery of the shaft.
- a sleeve member 9 having a small diameter portion 9a.
- the oil retaining member 7 is fitted to the small diameter portion 9 a of the sleeve member 9, and the spacer cover 8 is fitted to the outer peripheral surface 7 b of the oil retaining member 7.
- the outer peripheral surface 7 b of the oil retaining member 7 has a larger diameter than the outer peripheral surface of the sleeve member 9. Therefore, a gap is formed between the inner peripheral surface of the spacer cover 8 and the outer peripheral surface of the sleeve member 9. .
- the first oil reservoir 31 is formed as in the embodiment shown in FIG.
- the oil retaining member 7 has a chamfered portion 7d at its outer diameter side end.
- the chamfered portion 7d is a molding surface having a large surface opening ratio as in the above-described embodiment, and functions as a fuel filler opening. Therefore, the lubricating oil oozes smoothly from the chamfered portion 7d, and the oozing lubricating oil is supplied into the bearing device via the oil supply passage S during the bearing operation.
- a first oil reservoir 31 is disposed adjacent to the oil retaining member 7, and the lubricating oil held in the first oil reservoir 31 is replenished to the oil retaining member 7 sequentially. Therefore, the total amount of oil held by the inner ring spacer 6 can be increased, and the bearing life is increased.
- the sleeve member 9 can be formed of a solid resin (without voids) or a metal material, or can be formed of a porous resin or metal material.
- the rolling bearing device described above is not only a liquid fuel turbo pump of a rocket engine, but also as a bearing device that can be used under conditions where grease cannot be used, for example, a bearing device that rotates at high speeds at low temperatures, or in a vacuum such as a space environment. It can be used widely.
- the angular ball bearing was illustrated as a bearing format, this invention is applicable also to the rolling bearing apparatus which uses another bearing format (for example, deep groove ball bearing).
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
2 内輪
2a 内輪軌道面
3 外輪
3a 外輪軌道面
4 転動体
5 保持器
6 内輪間座
7 保油部材
7d 面取り部(給油口)
8 間座カバー
9 スリーブ部材
20 軸
31 第1の油溜り
32 第2の油溜り
33 第3の油溜り
S 給油路
Claims (19)
- 固定側の外輪と、回転側の内輪と、内輪軌道面と外輪軌道面との間に介在する複数の転動体と、転動体を保持する保持器と、内輪の端面に接触して該内輪の軸方向位置決めを行う内輪間座とを有する転がり軸受装置において、
内輪間座に、金属もしくは樹脂の多孔質体からなり、空孔に潤滑油を保有した保油部材を設け、軸受回転時の遠心力で保油部材から軸受内部に潤滑油を供給することを特徴とする転がり軸受装置。 - 保油部材表面に他所よりも表面開孔率の大きい給油口を設け、この給油口を、給油路を介して内輪間座の外周面に開口させると共に、該開口部を除く内輪間座の外周面を密閉状態にした請求項1記載の転がり軸受装置。
- 内輪間座に、内輪端面との接触部を有し、かつ保油部材の外周面を被覆する間座カバーを設け、給油路を間座カバーの内周面と外周面に開口させ、かつ給油路の内径側開口を保油部材の給油口に対向させた請求項2記載の転がり軸受装置。
- 間座カバーの端面の円周方向一部領域に内輪端面と接触する接触部を設け、円周方向の他の領域を内輪の端面と非接触にし、この非接触部で給油路を形成した請求項3記載の転がり軸受装置。
- 内輪間座に、保油部材に隣接して潤滑油を保有し、かつ外径側が間座カバーで密閉された第1の油溜りを設けた請求項3または4記載の転がり軸受装置。
- 第1の油溜りを、間座カバーの内周面と保油部材の外周面との間に形成した請求項5記載の転がり軸受装置。
- 保油部材の内周に、軸の外周面に嵌合するスリーブ部材を配置し、第1の油溜りを、スリーブ部材の外周面と間座カバーの内周面との間に形成した請求項5記載の転がり軸受装置。
- 間座カバーの線膨張係数を保油部材の線膨張係数と同等にした請求項3~7何れか1項に記載の転がり軸受装置。
- 内輪間座を保油部材で形成した請求項1または2記載の転がり軸受装置。
- 前記保油部材の外径端に面取り部を設け、この面取り部を給油口とした請求項2~9何れか1項に記載の転がり軸受装置。
- 前記面取り部の寸法をC0.5以上にした請求項10記載の転がり軸受装置。
- 保油部材を型成形し、給油口を成形面とした請求項2~11何れか1項に記載の転がり軸受装置。
- 内輪および保油部材を軸の外周面に嵌合し、軸の外周面と保油部材の内周面との間に、潤滑油を保有する第2の油溜りを設けた請求項1~6、8~12何れか1項に記載の転がり軸受装置。
- 内輪および保油部材を、中空部を有する軸の外周面に嵌合し、軸の中空部を、潤滑油を保有する第3の油溜りとし、軸に、内径側が第3の油溜りに開口し、外径側が保油部材の内周面と対向する軸の外周面に開口した貫通孔を設けた請求項1~6、8~13何れか1項に記載の転がり軸受装置。
- 前記保油部材内部の空孔率を10%~30%にした請求項1~14何れか1項に記載の転がり軸受装置。
- 内輪軌道面、外輪軌道面、および、前記転動体の表面のうち、少なくとも一つの表面に、固体潤滑被膜を形成した請求項1~15何れか1項に記載の転がり軸受装置。
- 保持器の表面に固体潤滑被膜を形成した請求項1~16何れか1項に記載の転がり軸受装置。
- 前記転動体をセラミックで形成した請求項16または17に記載の転がり軸受装置。
- ロケットエンジンの液体燃料用ターボポンプ、または、真空環境で使用する宇宙用機器に装備された請求項1~18何れか1項に記載の転がり軸受装置。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11762450.2A EP2554865B1 (en) | 2010-03-30 | 2011-03-02 | Rolling bearing device |
US13/583,092 US8746982B2 (en) | 2010-03-30 | 2011-03-02 | Rolling bearing device |
CN201180016221.2A CN102822545B (zh) | 2010-03-30 | 2011-03-02 | 滚动轴承装置 |
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JP2010-078969 | 2010-03-30 | ||
JP2010078969 | 2010-03-30 | ||
JP2010-227652 | 2010-10-07 | ||
JP2010227652A JP5752385B2 (ja) | 2010-03-30 | 2010-10-07 | 転がり軸受装置 |
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WO2011122210A1 true WO2011122210A1 (ja) | 2011-10-06 |
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Application Number | Title | Priority Date | Filing Date |
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PCT/JP2011/054695 WO2011122210A1 (ja) | 2010-03-30 | 2011-03-02 | 転がり軸受装置 |
Country Status (5)
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US (1) | US8746982B2 (ja) |
EP (1) | EP2554865B1 (ja) |
JP (1) | JP5752385B2 (ja) |
CN (1) | CN102822545B (ja) |
WO (1) | WO2011122210A1 (ja) |
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Also Published As
Publication number | Publication date |
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CN102822545A (zh) | 2012-12-12 |
US20120328225A1 (en) | 2012-12-27 |
EP2554865A4 (en) | 2013-12-11 |
EP2554865B1 (en) | 2016-08-03 |
JP2011226632A (ja) | 2011-11-10 |
EP2554865A1 (en) | 2013-02-06 |
CN102822545B (zh) | 2015-09-23 |
US8746982B2 (en) | 2014-06-10 |
JP5752385B2 (ja) | 2015-07-22 |
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