WO2011070621A1 - すべり軸受装置および圧縮機 - Google Patents
すべり軸受装置および圧縮機 Download PDFInfo
- Publication number
- WO2011070621A1 WO2011070621A1 PCT/JP2009/006764 JP2009006764W WO2011070621A1 WO 2011070621 A1 WO2011070621 A1 WO 2011070621A1 JP 2009006764 W JP2009006764 W JP 2009006764W WO 2011070621 A1 WO2011070621 A1 WO 2011070621A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- bearing
- sliding
- shaft
- slide
- resin
- Prior art date
Links
Images
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
- 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
- F16C33/20—Sliding surface consisting mainly of plastics
- F16C33/201—Composition of the plastic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1005—Construction relative to lubrication with gas, e.g. air, as lubricant
- F16C33/101—Details of the bearing surface, e.g. means to generate pressure such as lobes or wedges
-
- 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
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/107—Grooves for generating pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/046—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/20—Thermoplastic resins
- F16C2208/36—Polyarylene ether ketones [PAEK], e.g. PEK, PEEK
-
- 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
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/20—Thermoplastic resins
- F16C2208/52—Polyphenylene sulphide [PPS]
-
- 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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/42—Groove sizes
-
- 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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/54—Surface roughness
-
- 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
- F16C2360/00—Engines or pumps
- F16C2360/42—Pumps with cylinders or pistons
-
- 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
- F16C2360/00—Engines or pumps
- F16C2360/44—Centrifugal pumps
-
- 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
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/02—Shafts; Axles
Definitions
- the present invention relates to a sliding bearing device that can slide with a small friction coefficient without using lubricating oil, and more particularly to a bearing device in which a sliding portion is made of resin and metal.
- the present invention also relates to a compressor using this plain bearing device.
- resin materials are generally excellent in self-lubricating properties, they are practically used as sliding materials for sliding bearing devices used in environments where lubricants such as lubricating oil and grease cannot be used.
- lubricants such as lubricating oil and grease cannot be used.
- fiber materials typified by glass fibers and carbon fibers
- solid lubricants typified by graphite, polytetrafluoroethylene (PTFE), molybdenum disulfide, etc. are mixed with the resin to form a resin composite material.
- PTFE polytetrafluoroethylene
- Non-Patent Document 1 and Non-Patent Document 2 include a sliding part configuration that frictions a resin composite material in a dry gas atmosphere and its Frictional properties are shown.
- the sliding member described in Patent Document 1 is formed by mixing carbon fiber and graphite powder in a thermosetting resin and hot pressing, and has low friction and low wear particularly in a high-pressure dry gas atmosphere. It has been shown to be.
- Non-Patent Document 1 and Non-Patent Document 2 are experimental reports in which a resin composite material and stainless steel are rubbed in various gas atmospheres such as air and dry nitrogen, and carbon-based particles such as carbon powder, carbon nanotube, and carbon fiber. It is shown that when a polyether ether ketone (PEEK) resin composite material mixed with is rubbed in a dry gas atmosphere, the friction coefficient is reduced to about 0.05.
- PEEK polyether ether ketone
- the friction coefficient reduction effect varies depending on the sliding quality such as the processing quality of the sliding parts and the load, and a friction coefficient of 0.1 or less can be stably obtained. Conditions are often limited. Also, at the initial stage of friction, the friction coefficient is as high as 0.2 to 0.3, for example. Even if the familiarity progresses and the friction coefficient finally decreases, it may take a considerable amount of time depending on the conditions. is there. Therefore, when applied to general machine products such as a compressor and a plain bearing device, a device that can obtain a friction coefficient reduction effect more stably and quickly is desired.
- the present invention has been made in view of the above-mentioned problems, and it is a technical problem to be solved in the sliding bearing device and the compressor to stably achieve a low friction state from the earliest possible stage of the initial friction. It is.
- the plain bearing device has the following features.
- a sliding bearing device comprising: a bearing; a shaft supported by the bearing with sliding sliding; and a gas supply unit that supplies dry gas to a bearing sliding portion on which the bearing and the shaft slide.
- the bearing has at least a sliding surface made of a resin composite material in which a carbon material is mixed with a resin, and the shaft is made of metal and has a groove extending in a direction different from the sliding direction on the sliding surface.
- a slide bearing device comprising a bearing, a shaft supported by the bearing with sliding sliding, and a gas supply unit that supplies dry gas to a bearing sliding portion on which the bearing and the shaft slide.
- the bearing has at least a sliding surface made of a resin composite material in which a carbon material is mixed with a resin, the shaft is made of metal, and a plurality of grooves extending in a direction different from the sliding direction on the sliding surface Has a set of
- each of the plurality of grooves extends in an arbitrary direction.
- a slide bearing device comprising a bearing, a shaft supported by the bearing with sliding sliding, and a gas supply unit that supplies dry gas to a bearing sliding portion on which the bearing and the shaft slide.
- the bearing has at least a sliding surface made of a resin composite material in which a carbon material is mixed with a resin, the shaft is made of metal, and has a set of a plurality of recesses on the sliding surface.
- the shaft has an arithmetic mean roughness of the sliding surface roughness of 0.2 ⁇ m or more.
- the compressor according to the present invention has the following features.
- a compressor having a slide bearing, a drive shaft that is supported by the slide bearing and rotationally driven, and a compression unit that is connected to the drive shaft and compresses fluid, and is composed of a resin composite material in which a carbon material is mixed with a resin.
- the sliding bearing includes a gas supply unit that supplies dry gas to a bearing sliding part on which the sliding bearing and the driving shaft slide, and the driving shaft has a sliding surface in a direction different from the sliding direction. It has a groove extending in the direction.
- the compressor is composed of a resin composite material in which a carbon material is mixed with a resin.
- the sliding bearing, and a gas supply portion that supplies dry gas to a bearing sliding portion in which the sliding bearing and the driving shaft slide, and the driving shaft has a sliding direction on a sliding surface. It has a set of a plurality of grooves extending in different directions.
- each of the plurality of grooves preferably extends in an arbitrary direction.
- the compressor is composed of a resin composite material in which a carbon material is mixed with a resin.
- the sliding bearing, and a gas supply portion for supplying dry gas to a bearing sliding portion on which the sliding bearing and the driving shaft slide, wherein the driving shaft has a plurality of recesses on a sliding surface. Have a set.
- the drive shaft has an arithmetic mean roughness of the sliding surface roughness of 0.2 ⁇ m or more.
- the present invention it is possible to provide a sliding bearing device in which familiar wear between the bearing and the shaft in the initial sliding is promoted, and the friction coefficient can be reduced early after the start of use.
- the drive energy of various mechanical devices including compressors can be reduced. It can be reduced stably.
- no lubricating oil or grease is used, the consumption of resources can be reduced and the environmental load can be reduced.
- Example 2 of this invention it is a graph which shows the relationship between the roughness of the sliding surface of the cylindrical shaft which arises by shot blasting, and a friction coefficient. It is a figure which shows the bearing part of the centrifugal compressor by Example 3 of this invention. It is an enlarged view of the bearing part of the centrifugal compressor by Example 3 of this invention.
- the gas supply part is formed by providing a gap between the seal and the shaft, and a part of the gas compressed by the compressor is supplied to the bearing sliding part.
- FIG. In the centrifugal compressor by Example 3 of this invention, it is an enlarged view of the bearing part which formed the gas supply part by providing a clearance gap between a seal
- the present inventor has made it possible to stably achieve a low friction state having a friction coefficient of 0.1 or less from the early stage of the initial stage of friction in a sliding bearing device including a bearing made of a resin composite material and a metal shaft.
- a surface layer in which fine wear powder of the bearing made of the resin composite material is dispersed on the surface of the sliding portion with the shaft is formed while sliding with the dry gas supplied, and the metal shaft. It has been found that when a transfer surface layer of a resin sliding material is formed on the surface of the resin and both surface layers are stably held, a stable low friction state is obtained.
- the present inventor considered that both surface layers are formed by wear powder due to the wear of the resin composite material in the early stage of sliding, and thought to actively use the wear. Therefore, the present inventor appropriately promotes the wear-out by supplying dry gas to the sliding part and optimizing the contact state through many experiments and researches based on such considerations, and excessively.
- the present invention has been completed by discovering that the friction coefficient can be reduced quickly and effectively by forming a surface shape that does not cause any damage on the metal shaft.
- the sliding bearing device includes a bearing made of a resin composite material in which a carbon material is mixed with a resin, a metal shaft supported by the bearing while sliding, and the bearing and the shaft slide.
- a dry gas supply unit that supplies dry gas to a moving part (hereinafter referred to as a “bearing sliding part”), and a sliding direction within a surface range (sliding surface) that rubs against the bearing against the shaft
- the bearing should just be comprised by the resin composite material at least the surface (sliding surface) which frictions with an axis
- the sliding between the bearing and the shaft may be any one of rotation, swing, and reciprocation.
- the form of the bearing portion may be, for example, a cylindrical end face type, a cylindrical plane type, a pin-disk type, a journal type, a reciprocating type, a partial bearing thereof, or a composite bearing combining these.
- the resin material of the bearing portion is a resin composite material in which a fibrous, spherical, flake-like, particulate, or granular carbon material and a resin are mixed.
- One type of carbon material may be used from the above shape, or a plurality of types may be used.
- About resin at least 1 type or more is used among thermoplastic resins.
- the thermoplastic resin include polyamide, polyphthalamide, polyamide imide, polyacetal, polyphenylene sulfide, polyether imide, ultra high molecular weight polyethylene, polyether ether ketone, and the like.
- the dry gas supplied to the bearing sliding portion may be a gas containing oxygen.
- the dry gas containing oxygen dry air having a humidity of ⁇ 50 ° C. or less in terms of dew point temperature can be given.
- the dry gas supplied to the bearing sliding portion may be a gas not containing oxygen.
- the dry gas not containing oxygen include inert gas such as nitrogen and argon, hydrogen gas and hydrocarbon gas.
- the grooves formed on the surface of the sliding portion (sliding surface) of the shaft may be a perpendicular shape orthogonal to the sliding direction, a lattice shape where two or more grooves intersect, a free curve shape, a wavy shape, etc. It is necessary to have a portion extending in a direction different from the sliding direction within the surface range that frictions with the bearing. Even if a set of many short grooves not oriented in the sliding direction is formed on the surface of the sliding portion of the shaft, or a set of many concave portions is formed by a processing means such as shot blasting, the above-mentioned The same effect as the groove can be obtained.
- the surface roughness of the sliding portion of the shaft has an arithmetic average roughness (Ra) of 0.2 ⁇ m or more, but is preferably 0.8 ⁇ m or more.
- FIG. 1 shows a journal-type plain bearing device as an embodiment of the present invention.
- a bearing 1 having a resin sliding portion 2 is press-fitted into a casing 3, and a shaft 4a is rotatably supported.
- the casing 3 has a structure for applying a load to the bearing 1.
- a rotation driving motor (not shown) is connected to one end of the shaft 4a.
- the bearing sliding portion is a portion where the resin sliding portion 2 of the bearing 1 and the shaft 4a slide, and is also simply referred to as “sliding portion”.
- the material of the resin sliding portion 2 of the bearing 1 is a resin composite material obtained by mixing 30% by weight of carbon fiber with polyetheretherketone (PEEK), which is a thermoplastic resin.
- the shaft 4a is made of stainless steel.
- the bearing 1 is covered with a protective cover 5, and a vent hole 6 is provided at the top of the protective cover 5.
- the gas bearing unit 7 is provided in the plain bearing device so as to penetrate the protective cover 5.
- the gas supply unit 7 introduces dry gas into the protective cover 5 as indicated by a gas flow 8. As shown by the gas flow 8, the dry gas travels from the gas supply part 7 to the bearing sliding part where the bearing 1 and the shaft 4 a move relative to each other while friction occurs.
- the shaft 4a has a cylindrical shape, and the surface is processed and molded while being rotated in the circumferential direction using a lathe, so that a machining mark 9 is formed in the circumferential direction. Since the shaft 4a rotates and slides in the circumferential direction, the machining marks 9 are oriented in a direction substantially equal to the sliding direction of the shaft 4a. At this time, when the roughness of the sliding surface of the shaft 4a was measured, the arithmetic average roughness (Ra) was 0.8 ⁇ m. Further, the shaft 4a has a groove 10 which is 0.15 mm wide and 0.03 mm deep and extends in a direction orthogonal to the sliding direction by cutting in the surface range where the shaft 1 slides. That is, the groove 10 is substantially orthogonal to the machining mark 9.
- Nitrogen as a dry gas was continuously supplied into the protective cover 5 through the gas supply unit 7 at a flow rate of 20 L / min, and the relative humidity near the bearing 1 was controlled to be less than 2%.
- the dry gas is supplied to the end of the sliding portion between the bearing 1 and the shaft 4a, between the bearing 1 and the shaft 4a (sliding portion gap), and through the groove 10 to the sliding portion and the vicinity thereof. 1 and the entire sliding part of the shaft 4a.
- FIG. 2 is a diagram showing a plain bearing device including a shaft 4b having no groove.
- the same reference numerals as those in FIG. 1 denote the same or common elements as those in FIG.
- the slide bearing device shown in FIG. 2 has the same structure and shape as the slide bearing device shown in FIG. 1, except that the groove 10 is not formed on the shaft 4b.
- the friction coefficient was measured with an average contact surface pressure of 8 MPa.
- sliding started at a friction coefficient of about 0.25 at the beginning of sliding, and the sliding was repeated 1000 times.
- the friction coefficient was 0.2 or more.
- the friction coefficient after repeating the sliding 1000 times was reduced to 0.07.
- the groove 10 only needs to pass on the sliding surface between the bearing 1 and the shaft 4a within the operating range of the plain bearing device, and the effect can be obtained if at least one groove 10 exists on the shaft 4a.
- the groove 10 passes through the sliding surface throughout the operation corresponding to the sliding operation range and the contact range. It is desirable to increase the number of grooves 10.
- FIG. 3 shows a cylindrical planar slide bearing device according to the present invention.
- the plain bearing device shown in FIG. 3 has a structure in which a planar bearing 22 contacts and slides on the outer peripheral surface of a metal cylindrical shaft 21.
- the planar bearing 22 is attached to the cantilever 23, and when the weight 24 is hung on the cantilever 23, the planar bearing 22 is pressed against the outer peripheral surface of the cylindrical shaft 21.
- the cylindrical shaft 21 is made of stainless steel.
- the planar bearing 22 is made of a polyether ether ketone (PEEK) resin composite material in which 30% by weight of carbon fibers are mixed.
- PEEK polyether ether ketone
- a rotation driving motor (not shown) is connected to one end of the cylindrical shaft 21, and the cylindrical shaft 21 is rotated along the circumferential direction by the motor and slides on the planar bearing 22. .
- the periphery of the sliding portion (bearing sliding portion) between the cylindrical shaft 21 and the planar bearing 22 is covered with the protective cover 5.
- the dry gas is introduced into the inside of the protective cover 5 from the gas supply part 7 penetrating the protective cover 5 and supplied to the bearing sliding part where the planar bearing 22 and the cylindrical shaft 21 are in contact with each other.
- the friction coefficient during operation from the initial sliding was measured in time series. Nitrogen was continuously supplied as a dry gas at a flow rate of 20 L / min, and the relative humidity near the planar bearing 22 was controlled to be less than 2%.
- FIG. 4 and 5 show the cylindrical shaft used in Example 2.
- FIG. 4 and 5 Since the cylindrical shafts 21a and 21b are formed by machining their surfaces while rotating in the circumferential direction using a lathe, machining marks 9 are formed in the circumferential direction. At this time, when the surface roughness of the outer peripheral surfaces of the cylindrical shafts 21a and 21b was measured, the arithmetic average roughness (Ra) was 0.8 ⁇ m. Furthermore, the grooves 10 were formed on the circumferential surface only for the cylindrical shaft 21a shown in FIG.
- the groove 10 has a width of 0.15 mm and a depth extending in a direction orthogonal to the rotation direction of the cylindrical shaft 21a indicated by the arrow, that is, in a direction orthogonal to the sliding direction, in the surface range where the cylindrical shaft 21a slides with the planar bearing 22.
- a groove 10 having a thickness of 0.03 mm is formed by cutting.
- the cylindrical shafts 21a and 21b shown in FIG. 4 and FIG. 5 were incorporated in the slide bearing device shown in FIG. 3, and the coefficient of friction was measured. The result is shown in FIG. Whichever cylindrical shaft was used, the friction coefficient at the initial stage of sliding was about 0.25, which was equivalent.
- FIG. 7 shows another example of a cylindrical shaft having a groove.
- the cylindrical shaft 21c shown in FIG. 7 is formed by machining the surface while rotating in the circumferential direction using a lathe, and then the sliding direction of the cylindrical shaft 21c (see FIG.
- the groove 10 having a width of 0.15 mm and a depth of 0.03 mm is formed by cutting in a direction different from both the axial direction and the axial direction.
- the cylindrical shaft 21c shown in FIG. 7 was incorporated in the slide bearing device shown in FIG. 3, and the friction coefficient was measured under the same conditions as those described above. Also in this case, the friction coefficient decreased with repeated sliding, and the friction coefficient when the sliding repeated 2000 times showed 0.07.
- the groove 10 can be used even in a machine in which the cylindrical shaft operates in the axial direction in addition to the rotational direction. The effect of can be stably obtained, and the friction coefficient can be reduced.
- FIG. 8 shows another example of a cylindrical shaft having a groove.
- the cylindrical shaft 21d shown in FIG. 8 is formed with short grooves 10 having a random distribution in directionality and dispersed on the surface.
- the groove 10 extends in an arbitrary direction but is not oriented in the sliding direction, and has a structure in which the groove 10 passes through the sliding surface of the planar bearing 22 by a sliding operation. If it is, the length and arrangement
- the cylindrical shaft 21d shown in FIG. 8 was incorporated in the slide bearing device shown in FIG. 3 and slid to measure the friction coefficient.
- the coefficient of friction was about 0.25 at the initial stage of sliding, but decreased to 0.08 when the sliding was repeated 2000 times.
- the grooves 10 as a set of grooves having no fixed orientation, the effect of the grooves can be stably obtained even in the sliding bearing device in which the operation in all directions occurs.
- the inventor has applied the surface pressure distribution to the contact state between the shaft and the bearing as the first effect in the effect of reducing the friction coefficient by forming the groove 10 by repeating many experiments and analysis observations. It is important to promote wear and surface layer formation resulting therefrom, and as a second action, it is important not to excessively expand the wear of the resin composite material bearing by supplying dry gas to the sliding portion through the groove 10. Reached knowledge. Although the second action is reduced by making the grooves 10 shorter and discontinuous, the friction reduction effect can be exhibited by the first action.
- FIG. 9 shows a cylindrical shaft 21e having a large number of fine recesses dispersed on the surface.
- the recess was formed by processing the outer peripheral surface of the cylindrical shaft 21e by shot blasting. When the surface roughness of the outer peripheral surface was measured, the arithmetic average roughness (Ra) was 0.8 ⁇ m.
- the cylindrical shaft 21e was incorporated in the slide bearing device shown in FIG. 3, and slid under the same conditions as those performed on the cylindrical shafts 21a and 21b, and the friction coefficient was measured.
- FIG. 10 also shows the measurement result (FIG. 6) of the friction coefficient of the cylindrical shaft 21b in order to examine the effect of shot blasting.
- the friction coefficient of the cylindrical shaft 21e was about 0.25 at the beginning of sliding, but decreased with repeated sliding, and the friction coefficient when the repeated sliding was 2000 times decreased to about 0.1. did.
- the effect of reducing the coefficient of friction due to repeated sliding was obtained, there was also the effect that the second action was weakened, and compared with the case where the cylindrical shaft 21a (shaft with the groove 10) shown in FIG. 4 was used. It was also a gradual decrease.
- the present inventor for example, in the cylindrical shaft 21e formed with a set of fine concave portions on the surface by the shot blasting surface shown in FIG. 9 or the like, due to the surface roughness and the surface pressure applied to the sliding surface It was found that the effect of reducing the friction coefficient is particularly different.
- the outer peripheral surfaces were processed by shot blasting so that each surface roughness was different in the same manner as the cylindrical shaft 21e shown in FIG.
- Each of these cylindrical shafts 21 was incorporated in the slide bearing device shown in FIG. 3 and slid under the same conditions as those performed on the cylindrical shafts 21a and 21b.
- the coefficient of friction was about 0.25 when any cylindrical shaft 21 was used in the early stage of sliding, but the degree of reduction varied with the cylindrical shaft 21 as sliding was repeated.
- FIG. 11 shows the relationship between the coefficient of friction measured when the sliding was performed 2000 times and the roughness of the sliding surface of the cylindrical shaft 21.
- the roughness of the sliding surface of the cylindrical shaft 21 was expressed by arithmetic average roughness (Ra).
- Ra arithmetic average roughness
- a set of fine recesses was formed on the surface of the cylindrical shaft 21 by shot blasting, but the arithmetic average roughness (Ra) of the set of recesses formed on the sliding surface was 0.2 ⁇ m. If it is above, a processing method will not be restricted to this. For example, a similar set of fine recesses can be formed by laser processing, etching processing, or the like.
- the gas supplied from the gas supply unit 7 will be described.
- the friction coefficient is about 0.25 even when the groove 10 exists. Met.
- dry gas such as dry nitrogen and dry argon is similarly supplied at a flow rate of 20 L / min
- the friction coefficient decreases from about 0.25 at the initial stage to 0.1 or less as the sliding is repeated. did.
- Even when dry air containing oxygen was used as the dry gas the friction coefficient decreased from about 0.25 at the initial stage to 0.15, and a certain effect was obtained.
- use of deoxygenated gas has a higher effect of reducing the friction coefficient.
- the deoxygenated gas examples include inert gases such as nitrogen and argon, hydrogen gas, hydrocarbon gas, and the like. Also, in a state where liquid nitrogen vaporized gas is supplied instead of dry air and the supply amount is controlled so that the temperature in the protective cover 5 becomes ⁇ 100 ° C., the friction coefficient is 0.05, which is The coefficient of friction was lower than when dry nitrogen was supplied.
- the cylindrical shafts 21a, 21c, 21d, and 21e described in this embodiment may be used as the shaft of the journal-type plain bearing device described in the first embodiment.
- FIG. 12 is a view showing a bearing portion of the centrifugal compressor
- FIG. 13 is an enlarged view of a bearing portion of the centrifugal compressor.
- the centrifugal compressor 51 of this embodiment passes through a flow path 54 provided in the casing 53 by rotating an impeller 52 attached to a main shaft (not shown) by a driving device (not shown).
- the gas supplied to the impeller 52 is compressed by the rotation of the impeller 52.
- the compressed gas passes through a discharge port (not shown) and is supplied to the outside.
- the main shaft that rotates the impeller 52 is not shown in FIG. 12, but is provided below the impeller 52.
- the centrifugal compressor 51 is provided with a plurality of vanes 55 for controlling the flow rate of the gas in a flow path 54 that guides the gas to the impeller 52.
- the vane 55 is swung by a gear mechanism that includes a first gear 57, a second gear 60, and a third gear 59.
- the first gear 57 is a drive gear fixed to a drive shaft 56 connected to a drive mechanism (not shown).
- the third gear 59 is a vane gear fixed to a vane shaft 58 connected to the vane 55.
- the second gear 60 is a ring gear that is interposed between the first gear 57 and the third gear 59 and transmits the rotation from the first gear 57 (drive gear) to the third gear 59. .
- the first gear 57, the second gear 60, and the third gear 59 are accommodated in the casing 53.
- the first gear 57 and the third gear 59 are provided on a drive shaft 56 and a vane shaft 58, respectively, by a bearing 62 and a bearing 64 of polyphenylene sulfide (PPS) resin containing carbon fiber fixed in the casing 53. It is supported rotatably.
- PPS polyphenylene sulfide
- a groove 10 extending in a direction different from the rotation direction of the vane shaft 58 is formed on the surface of the vane shaft 58 in a range where the vane shaft 58 slides with the bearing 64. ing.
- a groove 10 extending in a direction different from the rotation direction of the drive shaft 56 is formed on the surface of the drive shaft 56 (not shown).
- the vane shaft 58 is provided with a seal 65 on the flow path 54 side to prevent the inflow of gas from the flow path 54.
- a contact type seal is used as the seal 65, but a non-contact type labyrinth seal may be used.
- a gas supply unit 61 is connected to each of the bearings 62 and 64, and a gas supply unit 73 including a cylinder is connected to the gas supply unit 61.
- the gas supply device 73 supplies nitrogen having a dew point temperature of ⁇ 50 ° C. or lower at a pressure of about 0.02 MPa.
- the supplied nitrogen is recovered from a communication hole 63 communicating with the outside in which a check valve (not shown) is provided in a part of the casing 53 including the gear mechanism, and is dehumidified in the gas supply device 73.
- inert gas such as high-pressure air or argon dehumidified and dedusted may be supplied, or a gas production apparatus may be used instead of the cylinder.
- the recovered nitrogen is returned to the gas supply device 73 via the dust removing device 71 and the pump 72, circulated and supplied to the bearing 64.
- the predetermined operation of the centrifugal compressor was performed in such a state that nitrogen was circulated and supplied to the bearing.
- the temperature of the gas flowing through the flow path 54 can be set widely from ⁇ 160 ° C. to 60 ° C. depending on the gas type.
- the torque of the drive shaft 56 can be reduced as compared with the case where no dry gas is allowed to flow without using grease or a solid lubricant under various temperature conditions.
- the method of supplying the dry gas to the bearing sliding portion may be air in which the gas to be compressed by the compressor is dehumidified, or In the case of a dry gas typified by an inert gas such as nitrogen or argon, or a hydrogen gas or hydrocarbon gas, the same torque reduction effect can be obtained even if the gas flow path to be compressed is used as a supply source. Is obtained.
- a passage communicating from the flow path 54 to the bearing sliding portion is provided, or a gap is formed between the vane shaft 58 and the seal 65 as shown in FIG.
- the gas supply portion 61 is formed to communicate with the circumference of each bearing from the flow path 54, and from there through the gap between the vane shaft 58 and the bearing 64 and the gap between the drive shaft 56 and the bearing 62, It is good also as a structure where gas is supplied to a bearing sliding part.
- FIG. 15 shows an enlarged view of a bearing portion formed by the structure shown in FIG.
- Example 2 As a comparative example regarding the material of the bearing, the same measurement as described in Example 2 was performed using a bearing made of polyetheretherketone (PEEK) resin not mixed with a carbon material. As a result, the coefficient of friction continues to be maintained at 0.3 or more from the beginning of sliding, and even if sliding is repeated 2000 times, a decrease equivalent to that when the present invention is applied cannot be obtained, and becomes 0.1 or less. There was no.
- PEEK polyetheretherketone
- the grooves formed on the surfaces of the vane shaft 58 and the drive shaft 56 are grooves extending in a direction orthogonal to the sliding direction described in the first and second embodiments (FIG. 4), and are different from the rotational direction and the axial direction. It may be a groove that extends (FIG. 7) or a groove that faces in any direction (FIG. 8). Furthermore, many fine recesses (FIG. 9) may be formed on the surfaces of the vane shaft 58 and the drive shaft 56 instead of the grooves.
- polyether ether ketone PEEK
- PPS polyphenylene sulfide
- polyamide polyphthalamide
- polyamideimide polyacetal
- polyetherimide ultrahigh molecular weight polyethylene and the like.
- carbon fiber is shown in the present embodiment. May be used. In particular, by adding a carbon material containing graphite, friction tends to be stably reduced earlier.
- a single form of carbon material may be added to the resin, but a plurality of forms of carbon material may be mixed depending on the application.
- a plurality of forms of carbon materials characteristics that are difficult to obtain with a single form of carbon materials can be obtained.
- a resin composite material that is a mixture of carbon fiber and graphite-like carbon material and mixed with resin it is possible to obtain an early and significant effect of reducing friction while maintaining strength against load. There is.
- a slide is used using a bearing made of a resin composite material in which a carbon material is mixed with a resin in a single form or a plurality of forms (fibrous, spherical, flake shaped, particulate, granular, etc.).
- a sliding bearing device or a compressor having a low friction sliding part without using oil, grease, solid lubricant or the like.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Sliding-Contact Bearings (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
Claims (10)
- 軸受と、すべり摺動を伴いながら前記軸受に支持される軸と、前記軸受と前記軸とが摺動する軸受摺動部に乾燥気体を供給する気体供給部とを備えるすべり軸受装置において、
前記軸受は、少なくとも摺動表面が、炭素材料が樹脂に混合した樹脂複合材料で構成され、
前記軸は、金属製であり、摺動表面に摺動方向と異なる方向に延伸する溝を有することを特徴とするすべり軸受装置。
- 軸受と、すべり摺動を伴いながら前記軸受に支持される軸と、前記軸受と前記軸とが摺動する軸受摺動部に乾燥気体を供給する気体供給部とを備えるすべり軸受装置において、
前記軸受は、少なくとも摺動表面が、炭素材料が樹脂に混合した樹脂複合材料で構成され、
前記軸は、金属製であり、摺動表面に摺動方向と異なる方向に延伸する複数の溝の集合を有することを特徴とするすべり軸受装置。 - 請求項2記載のすべり軸受装置において、
前記複数の溝は、それぞれが任意の方向に延伸するすべり軸受装置。 - 軸受と、すべり摺動を伴いながら前記軸受に支持される軸と、前記軸受と前記軸とが摺動する軸受摺動部に乾燥気体を供給する気体供給部とを備えるすべり軸受装置において、
前記軸受は、少なくとも摺動表面が、炭素材料が樹脂に混合した樹脂複合材料で構成され、
前記軸は、金属製であり、摺動表面に複数の凹部の集合を有することを特徴とするすべり軸受装置。 - 請求項1から4のいずれか1項記載のすべり軸受装置において、
前記軸は、前記摺動表面の粗さが算術平均粗さで0.2μm以上であるすべり軸受装置。 - すべり軸受と、前記すべり軸受に支持され回転駆動する駆動軸と、前記駆動軸に接続され流体を圧縮する圧縮部とを有する圧縮機において、
炭素材料が樹脂に混合した樹脂複合材料で構成される前記すべり軸受と、
前記すべり軸受と前記駆動軸とが摺動する軸受摺動部に、乾燥気体を供給する気体供給部とを備え、
前記駆動軸は、摺動表面に摺動方向と異なる方向に延伸する溝を有することを特徴とする圧縮機。 - すべり軸受と、前記すべり軸受に支持され回転駆動する駆動軸と、前記駆動軸に接続され流体を圧縮する圧縮部とを有する圧縮機において、
炭素材料が樹脂に混合した樹脂複合材料で構成される前記すべり軸受と、
前記すべり軸受と前記駆動軸とが摺動する軸受摺動部に、乾燥気体を供給する気体供給部とを備え、
前記駆動軸は、摺動表面に摺動方向と異なる方向に延伸する複数の溝の集合を有することを特徴とする圧縮機。 - 請求項7記載の圧縮機において、
前記複数の溝は、それぞれが任意の方向に延伸する圧縮機。 - すべり軸受と、前記すべり軸受に支持され回転駆動する駆動軸と、前記駆動軸に接続され流体を圧縮する圧縮部とを有する圧縮機において、
炭素材料が樹脂に混合した樹脂複合材料で構成される前記すべり軸受と、
前記すべり軸受と前記駆動軸とが摺動する軸受摺動部に、乾燥気体を供給する気体供給部とを備え、
前記駆動軸は、摺動表面に複数の凹部の集合を有することを特徴とする圧縮機。 - 請求項5から9のいずれか1項記載の圧縮機において、
前記駆動軸は、前記摺動表面の粗さが算術平均粗さで0.2μm以上である圧縮機。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2009/006764 WO2011070621A1 (ja) | 2009-12-10 | 2009-12-10 | すべり軸受装置および圧縮機 |
EP09852018.2A EP2511548A4 (en) | 2009-12-10 | 2009-12-10 | SMOOTH BEARING DEVICE AND COMPRESSOR |
CN200980160812.XA CN102472321B (zh) | 2009-12-10 | 2009-12-10 | 滑动轴承装置及压缩机 |
US13/388,585 US9255606B2 (en) | 2009-12-10 | 2009-12-10 | Slide bearing device and compressor |
JP2011544983A JP5502108B2 (ja) | 2009-12-10 | 2009-12-10 | すべり軸受装置および圧縮機 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2009/006764 WO2011070621A1 (ja) | 2009-12-10 | 2009-12-10 | すべり軸受装置および圧縮機 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011070621A1 true WO2011070621A1 (ja) | 2011-06-16 |
Family
ID=44145193
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2009/006764 WO2011070621A1 (ja) | 2009-12-10 | 2009-12-10 | すべり軸受装置および圧縮機 |
Country Status (5)
Country | Link |
---|---|
US (1) | US9255606B2 (ja) |
EP (1) | EP2511548A4 (ja) |
JP (1) | JP5502108B2 (ja) |
CN (1) | CN102472321B (ja) |
WO (1) | WO2011070621A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012212136A (ja) * | 2011-03-24 | 2012-11-01 | Mitsubishi Chemicals Corp | 感光体ドラムに装着される部材、端部部材、軸受け、感光体ドラムユニット、プロセスカートリッジ、及び画像形成装置 |
EP2674359A1 (en) * | 2012-06-13 | 2013-12-18 | Claverham Limited | Dry lubricated rotary actuator for in blade rotor control |
JP2017219200A (ja) * | 2016-06-01 | 2017-12-14 | 東洋製罐グループホールディングス株式会社 | 摺動性構造体及びその製造方法 |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5914383B2 (ja) * | 2013-02-22 | 2016-05-11 | 大豊工業株式会社 | すべり軸受 |
JP2018071787A (ja) * | 2016-10-24 | 2018-05-10 | Ntn株式会社 | 滑り軸受 |
CN110985528B (zh) * | 2019-12-30 | 2021-08-20 | 江苏毅合捷汽车科技股份有限公司 | 一种空气轴颈轴承 |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11279413A (ja) | 1998-03-27 | 1999-10-12 | Toyo Tanso Kk | ドライガス用摺動部材 |
JP2006038211A (ja) * | 2004-07-22 | 2006-02-09 | Nippon Densan Corp | 流体動圧軸受、この流体動圧軸受を備えたスピンドルモータ及びこのスピンドルモータを備えた記録ディスク駆動装置 |
JP2007100722A (ja) * | 2005-09-30 | 2007-04-19 | 和男 ▲吉▼川 | 軸受構造 |
JP2008082356A (ja) * | 2006-09-26 | 2008-04-10 | Oiles Ind Co Ltd | 静圧気体軸受 |
JP2009133418A (ja) * | 2007-11-30 | 2009-06-18 | Origin Electric Co Ltd | 転がり軸受 |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3955860A (en) * | 1949-02-07 | 1976-05-11 | The United States Of America As Represented By The United States Energy Research And Development Administration | Journal bearing |
US3150822A (en) * | 1961-02-09 | 1964-09-29 | Commissariat Energie Atomique | Sealing and centering device for rotary shaft |
GB1417244A (en) * | 1973-01-19 | 1975-12-10 | Nat Res Dev | Temperature compensating ceramic/metal bearing assemblies |
EP0661470A3 (en) * | 1993-12-27 | 1996-08-14 | Starlite Ind | Smooth and hanging contact bearing. |
CN2209238Y (zh) | 1994-04-08 | 1995-10-04 | 北京科阳气体液化技术联合公司 | π形槽动静压混合式气体轴承 |
US6502991B2 (en) * | 2001-03-14 | 2003-01-07 | The Timken Company | Rotary fluid bearing coatings and coining and processes for manufacturing the same |
KR100612615B1 (ko) | 2003-05-16 | 2006-08-17 | 한국과학기술원 | 하이브리드 복합재료 저널베어링 구조 및 그러한 구조를갖는 저널베어링의 제조방법 |
JP2005045924A (ja) | 2003-07-22 | 2005-02-17 | Nippon Densan Corp | スピンドルモータ、このスピンドルモータに適用されるロータの製造方法、及びこのスピンドルモータを備えたハードディスク駆動装置 |
CN1776234A (zh) | 2005-12-15 | 2006-05-24 | 上海交通大学 | 半内冷式离心压缩机 |
DE102006037821A1 (de) * | 2006-08-12 | 2008-02-14 | Atlas Copco Energas Gmbh | Turbomaschine |
JP4876112B2 (ja) * | 2008-09-30 | 2012-02-15 | 株式会社日立製作所 | すべり軸受装置 |
-
2009
- 2009-12-10 JP JP2011544983A patent/JP5502108B2/ja not_active Expired - Fee Related
- 2009-12-10 US US13/388,585 patent/US9255606B2/en not_active Expired - Fee Related
- 2009-12-10 WO PCT/JP2009/006764 patent/WO2011070621A1/ja active Application Filing
- 2009-12-10 CN CN200980160812.XA patent/CN102472321B/zh not_active Expired - Fee Related
- 2009-12-10 EP EP09852018.2A patent/EP2511548A4/en not_active Withdrawn
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11279413A (ja) | 1998-03-27 | 1999-10-12 | Toyo Tanso Kk | ドライガス用摺動部材 |
JP2006038211A (ja) * | 2004-07-22 | 2006-02-09 | Nippon Densan Corp | 流体動圧軸受、この流体動圧軸受を備えたスピンドルモータ及びこのスピンドルモータを備えた記録ディスク駆動装置 |
JP2007100722A (ja) * | 2005-09-30 | 2007-04-19 | 和男 ▲吉▼川 | 軸受構造 |
JP2008082356A (ja) * | 2006-09-26 | 2008-04-10 | Oiles Ind Co Ltd | 静圧気体軸受 |
JP2009133418A (ja) * | 2007-11-30 | 2009-06-18 | Origin Electric Co Ltd | 転がり軸受 |
Non-Patent Citations (3)
Title |
---|
N. L. MCCOOK; M. A. HAMILTON; D. L. BURRIS; W. G. SAWYER: "Tribological results of PEEK nanocomposites in dry sliding against 440C in various gas environments", vol. 262, 2007, ELSEVIER, WEAR, pages: 1511 - 1515 |
See also references of EP2511548A4 * |
T. OYAMADA ET AL.: "Friction and wear of PEEK reinforced with carbon fibers in nitrogen at normal and cryogenic temperature", CONFERENCE PROCEEDINGS OF STLE ANNUAL MEETING, SOCIETY OF TRIBOLOGIST & LUBRICATION ENGINEERS, 2009 |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012212136A (ja) * | 2011-03-24 | 2012-11-01 | Mitsubishi Chemicals Corp | 感光体ドラムに装着される部材、端部部材、軸受け、感光体ドラムユニット、プロセスカートリッジ、及び画像形成装置 |
EP2674359A1 (en) * | 2012-06-13 | 2013-12-18 | Claverham Limited | Dry lubricated rotary actuator for in blade rotor control |
US9440738B2 (en) | 2012-06-13 | 2016-09-13 | Claverham Ltd. | Dry lubricated rotary actuator for in blade rotor control |
JP2017219200A (ja) * | 2016-06-01 | 2017-12-14 | 東洋製罐グループホールディングス株式会社 | 摺動性構造体及びその製造方法 |
JP7444532B2 (ja) | 2016-06-01 | 2024-03-06 | 東洋製罐グループホールディングス株式会社 | 摺動性構造体及びその製造方法 |
Also Published As
Publication number | Publication date |
---|---|
US20120288368A1 (en) | 2012-11-15 |
EP2511548A1 (en) | 2012-10-17 |
CN102472321A (zh) | 2012-05-23 |
CN102472321B (zh) | 2015-06-03 |
US9255606B2 (en) | 2016-02-09 |
EP2511548A4 (en) | 2016-11-23 |
JPWO2011070621A1 (ja) | 2013-04-22 |
JP5502108B2 (ja) | 2014-05-28 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5502108B2 (ja) | すべり軸受装置および圧縮機 | |
JP5635352B2 (ja) | 複合滑り軸受 | |
JP5753756B2 (ja) | スクロールコンプレッサ | |
CN101415963B (zh) | 滑动轴承 | |
JP5925553B2 (ja) | 可変容量型アキシャルピストンポンプのクレイドルガイドおよび可変容量型アキシャルピストンポンプ | |
CN109702199A (zh) | 一种高熵合金基自润滑含油轴承材料 | |
WO2014147221A2 (de) | Trockenlauffähiger polymergleitwerkstoff und trockenlauffähige gleitringdichtung | |
KR20110018287A (ko) | 유체 주입식 스크루 압축기 요소 | |
JP7149252B2 (ja) | 摺動部材用樹脂材料および摺動部材 | |
JP4876112B2 (ja) | すべり軸受装置 | |
KR20150139952A (ko) | 사판식 컴프레서의 반구 슈 및 사판식 컴프레서 | |
EP3543322B1 (en) | Sliding member | |
JP4619302B2 (ja) | すべり軸受及びその製造方法 | |
Yan et al. | Tribological behaviors of MoS 2/SiCH film composite lubrication system | |
Nilsson et al. | Static/dynamic friction and wear of some selected polymeric materials for conformal tribo-pairs under boundary lubrication conditions | |
JP2009222208A (ja) | 軸受および軸受を有するポンプ | |
JP2014142070A (ja) | 複合滑り軸受 | |
EP3543295B1 (en) | Resin composition and sliding member | |
JP2008309259A (ja) | 転がり軸受 | |
JP2014134290A (ja) | 複合滑り軸受の製造方法 | |
WO2017183669A1 (ja) | 斜板式コンプレッサの半球シューおよび斜板式コンプレッサ | |
CN209539816U (zh) | 双摩擦面的端面滑动轴承 | |
Alisin | Increasing wear resistance of the hinge guide compressor in aircraft engine | |
TRAJKOVSKI et al. | POLYMERS FOR SUSTAINABLE HYDRAULIC VALVES TESTED IN WATER, GLYCEROL-WATER MIXTURE AND HYDRAULIC OIL | |
JP2016070367A (ja) | 耐熱性焼結含油軸受 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 200980160812.X Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 09852018 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2011544983 Country of ref document: JP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13388585 Country of ref document: US |
|
REEP | Request for entry into the european phase |
Ref document number: 2009852018 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2009852018 Country of ref document: EP |
|
NENP | Non-entry into the national phase |
Ref country code: DE |