WO2017164325A1 - Palier à rouleaux sphérique à double rangée - Google Patents

Palier à rouleaux sphérique à double rangée Download PDF

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Publication number
WO2017164325A1
WO2017164325A1 PCT/JP2017/011775 JP2017011775W WO2017164325A1 WO 2017164325 A1 WO2017164325 A1 WO 2017164325A1 JP 2017011775 W JP2017011775 W JP 2017011775W WO 2017164325 A1 WO2017164325 A1 WO 2017164325A1
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WO
WIPO (PCT)
Prior art keywords
rollers
roller
rows
roller bearing
row
Prior art date
Application number
PCT/JP2017/011775
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English (en)
Japanese (ja)
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WO2017164325A8 (fr
Inventor
貴志 山本
一将 ▲瀬▼古
井上　靖之
径生 堀
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2017045679A external-priority patent/JP6873754B2/ja
Priority claimed from JP2017048527A external-priority patent/JP6871767B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to ES17770365T priority Critical patent/ES2959734T3/es
Priority to CN201780019166.XA priority patent/CN108884867B/zh
Priority to EP17770365.9A priority patent/EP3434918B1/fr
Publication of WO2017164325A1 publication Critical patent/WO2017164325A1/fr
Publication of WO2017164325A8 publication Critical patent/WO2017164325A8/fr
Priority to US16/138,504 priority patent/US10655674B2/en

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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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting

Definitions

  • the present invention relates to a double-row self-aligning roller bearing applied to an application in which an uneven load is applied to two rows of rollers arranged in the bearing width direction, for example, a bearing that supports a main shaft of a wind power generator or an industrial machine. .
  • an axial load caused by wind force acts on the bearing that supports the main shaft of the wind power generator.
  • the main shaft supporting bearing is a double-row self-aligning roller bearing 41 as shown in FIG. 10, of the two rows of rollers 44 and 45 interposed between the inner ring 42 and the outer ring 43, the axial load Fa is mainly used. Only one row of rollers 45 on the rear side receives the axial load Fa. That is, one row of rollers 45 receives both a radial load and an axial load, while the other row of rollers 44 receives only a radial load.
  • the roller 45 in the row receiving the axial load has a larger contact surface pressure than the roller 44 in the row receiving only the radial load, and the surface damage and wear of the rolling surface of the roller 45 and the raceway surface 43a of the outer ring 43 are increased. Is likely to occur and the rolling life is short. Therefore, the actual life of the entire bearing is determined by the rolling life of the row of rollers 45 that receive the axial load.
  • the lengths L1 and L2 of the two rows of rollers 54 and 55 interposed between the inner ring 52 and the outer ring 53 are made different from each other as in the double row self-aligning roller bearing 51 shown in FIG.
  • the load capacity of the rollers 55 in the row that receives the axial load be larger than the load capacity of the rollers 54 in the row that hardly receive the axial load (Patent Document 1).
  • the contact angles ⁇ 1 and ⁇ 2 of the two rows of rollers 64 and 65 interposed between the inner ring 62 and the outer ring 63 are made different from each other, so that the contact angle ⁇ 2
  • Patent Document 2 A proposal has been made that a large axial load can be received by the roller 65 having a large diameter.
  • the contact angles ⁇ 1, ⁇ 2 of the two rows of rollers 64, 65 can be made different from each other by making the lengths L1, L2 of the two rows of rollers 54, 55 different from each other as shown in FIG. Also by making them different from each other, it is possible to increase the load capacity of the rollers 55 and 65 in the row receiving the axial load, thereby improving the actual life of the entire bearing.
  • the bearing dimensional standard ISO standard; JIS B 1512
  • the load capacity of the rollers 55 and 65 of the row subjected to the axial load is adequate by using only one of the above two methods. It is difficult to increase to a reasonable value.
  • the inner diameter, the outer diameter, and the bearing width are determined with respect to the nominal number according to the dimensional standard, if the length L2 of the roller 55 in the row receiving the axial load in FIG. The standard value is exceeded. If the contact angle ⁇ 2 of the roller 65 in the row receiving the axial load in FIG. 12 is excessively increased, the inner diameter d exceeds the standard value.
  • the object of the present invention is suitable for use in applications in which axial loads and radial loads are received, and loads having different sizes act on two rows of rollers arranged in the axial direction, and within the limits of dimensional standards, It is an object of the present invention to provide a double row self-aligning roller bearing capable of sufficiently increasing the load capacity of the rollers in the row.
  • rollers are interposed in two rows side by side in the bearing width direction between the inner ring and the outer ring, and the raceway surface of the outer ring is spherical,
  • the two rows of rollers have a cross-sectional shape in which the outer peripheral surface is along the raceway surface of the outer ring.
  • the two rows of rollers have different lengths, and the length of the longer rollers is 39% or more of the bearing width.
  • the ratio of the contact angle of the short roller to the long roller is in the range of 1: 2 to 1: 4.
  • the longer roller has a larger load capacity than the shorter roller. Further, since the contact angle of the long roller is larger than that of the short roller, the long roller can bear a large axial load. By making the contact angle of the long roller larger than the contact angle of the short roller, the contact angle of the short roller is reduced and the radial load capacity of the short roller is reduced. improves.
  • each double-row spherical roller bearing is used as a spindle support bearing for a wind turbine generator.
  • the contact surface pressure of the rollers in both rows at that time was analyzed with an axial load and a radial load. As a result, it was found that when the contact angle ratio was 1: 3, the contact surface pressures of both rows of rollers were most even.
  • the assumed axial load and radial load refer to an axial load and a radial load when the average wind power generator is operating most normally in consideration of various conditions such as power generation capacity and installation location. Therefore, in a double row self-aligning roller bearing used in a wind power generator having different conditions as compared with an average wind power generator, the optimal contact angle ratio may not be 1: 3. However, even in that case, the optimum contact angle ratio falls within the range of 1: 2 to 1: 4. For this reason, the ratio of the contact angles of the rollers in both rows is preferably in the range of 1: 2 to 1: 4. A more preferable range of the contact angle ratio is 1.0: 2.5 to 1.0: 3.5. If the contact angle ratio is [1: 4 or more], the inner ring is too thin due to dimensional constraints, making it difficult to place a roller having a long length and a large contact angle.
  • the ratio of the contact angles of the rollers in both rows is within the above-mentioned appropriate range within the range of the dimensional standard. It has been found that double row spherical roller bearings can be obtained.
  • the range of the contact angle ⁇ 1 of the short roller is 5 to 7 °
  • the range of the contact angle ⁇ 2 of the long roller is 14 to 16 °.
  • the contact angle ⁇ 1 of both rows of rollers within the range of dimensional standards. ⁇ 2 can be obtained in a double row self-aligning roller bearing in which the above ratio is in the proper range.
  • the position of the maximum diameter is an asymmetrical roller deviating from the center of the roller length, and has an intermediate collar for guiding the two rows of rollers between the two rows of rollers on the outer peripheral surface of the inner ring. Also good.
  • an induced thrust load is generated.
  • the middle collar supports this induced thrust load. The combination of the asymmetrical roller and the middle collar provides good guide accuracy for the roller.
  • the center position in the bearing width direction of the middle collar is shifted to the side of the roller having a longer length than the position in the bearing width direction at the point where the action lines forming the contact angles ⁇ 1 and ⁇ 2 of both rows intersect each other. It may be.
  • the roller having a long length and a large contact angle can bear a larger axial load. It becomes possible.
  • any one or more of the following structures (1) to (4) may be provided.
  • a cage is provided that holds the rollers of each row, and each cage has an annular ring portion that guides an axially inner end face of each row of rollers, and an axial direction from the annular portion.
  • a plurality of pillar portions provided at intervals defined along the circumferential direction, and a retainer for holding the long rollers provided with pockets for retaining the rollers between the pillar portions.
  • roller rolling surface A crowning is provided at an end of a rolling surface on the outer periphery of the roller (hereinafter sometimes referred to as “roller rolling surface”).
  • roller rolling surface Each of the rollers has a DLC (Diamond-like Carbon) coating on the roller rolling surface.
  • the inner ring is provided between the two rows of rollers on the outer peripheral surface of the inner ring and guides the two rows of rollers, and the axial direction of each row of rollers provided at both ends of the outer surface.
  • a small brim that faces the outer end face is provided, and a slot into which the long roller is inserted into the bearing is provided in the small brim that faces the end face of the long roller in the axial direction.
  • the interval determined in the structure (1) is an interval arbitrarily determined by design or the like, and is determined by finding an appropriate interval by, for example, one or both of testing and simulation.
  • the one cage that holds the long roller has an inclination angle in which the outer diameter surface of the column portion is inclined inward in the radial direction from the proximal end side toward the distal end side.
  • the pocket surface can hold the maximum diameter position of the roller.
  • the posture stability of the long roller is not impaired, and the long roller can be easily assembled.
  • the structure (2) since the crowning is provided at the end of the roller rolling surface, the edge stress can be reduced.
  • each roller has the DLC film on the roller rolling surface, it is possible to improve the wear resistance. As a result, the roller rolling surface and the raceway surface of the outer ring are less likely to be worn than those without the DLC film.
  • the structure (4) since the inner ring is provided with the insertion groove for inserting the long roller into the bearing in the small collar facing the axially outer end surface of the long roller, the long roller is incorporated. The property can be further improved.
  • This double row spherical roller bearing is suitable for supporting the main shaft of a wind power generator.
  • a radial load due to the weight of the blade and the rotor head and an axial load due to wind force are applied to the double row spherical roller bearing that supports the main shaft of the wind power generator.
  • the roller in the row receiving the axial load is a roller having a long length and a large contact angle
  • the roller in a row receiving only the radial load is a roller having a short length and a small contact angle.
  • the contact surface pressure of the rows of rollers can be made substantially uniform.
  • rollers are interposed in two rows side by side in the bearing width direction between the inner ring and the outer ring, and the raceway surface of the outer ring is spherical.
  • the two rows of rollers are double row self-aligning roller bearings having an outer peripheral surface having a cross-sectional shape along the raceway surface of the outer ring, and the two rows of rollers are different in length from each other and have a long length.
  • the contact angle is larger than the contact angle of the short roller, and there is a middle collar in the portion between the two rows of rollers on the outer peripheral surface of the inner ring, and the center position of the middle collar in the bearing width direction is It is shifted to the longer roller side from the position in the bearing width direction at the point where the action lines forming the contact angles of both rows intersect each other.
  • the longer roller has a larger load capacity than the shorter roller. Further, since the contact angle of the long roller is larger than that of the short roller, the long roller can bear a large axial load. By making the contact angle of the long roller larger than the contact angle of the short roller, the contact angle of the short roller is reduced and the radial load capacity of the short roller is reduced. improves.
  • the double-row self-aligning roller bearing having this configuration is also suitable for supporting the main shaft of the wind turbine generator.
  • FIG. 4 shows the distribution analysis results of the contact pressure of the roller on the front side when a composite load of axial load and radial load is applied to multiple types of double row spherical roller bearings with different contact angle ratios for both rows of rollers. It is a graph.
  • Fig. 5 shows the distribution analysis results of the contact pressure of the roller on the rear side when a composite load of axial load and radial load is applied to multiple types of double row spherical roller bearings with different contact angle ratios for both rows of rollers. It is a graph. It is the figure which illustrated the ratio of the roller length with respect to a bearing width on the same drawing about several conventional double row self-aligning roller bearings.
  • This double-row self-aligning roller bearing 1 has two rows of left and right rollers 4 and 5 arranged in the bearing width direction between an inner ring 2 and an outer ring 3.
  • the raceway surface 3 a of the outer ring 3 has a spherical shape, and the rollers 4 and 5 in each of the left and right rows have a cross-sectional shape along the raceway surface 3 a of the outer ring 3.
  • the outer peripheral surfaces of the rollers 4 and 5 are rotating curved surfaces obtained by rotating an arc along the raceway surface 3a of the outer ring 3 around the center lines C1 and C2.
  • the inner ring 2 is formed with double-row raceway surfaces 2a and 2b having a cross-sectional shape along the outer peripheral surfaces of the rollers 4 and 5 in the left and right rows.
  • collars (small collars) 6 and 7 are provided, respectively.
  • An intermediate collar 8 is provided at the center of the outer peripheral surface of the inner ring 2, that is, between the left row roller 4 and the right row roller 5.
  • the left and right rollers 4 and 5 are asymmetrical rollers in which the positions of the maximum diameters D1 max and D2 max deviate from the center A1 and A2 of the roller length.
  • the position of the maximum diameter D1 max of the roller 4 in the left row is on the right side of the center A1 of the roller length
  • the position of the maximum diameter D2 max of the roller 5 in the right row is on the left side of the center A2 of the roller length.
  • Induced thrust loads are generated in the rollers 4 and 5 in the left and right rows of such asymmetric rollers.
  • the middle collar 8 of the inner ring 2 is provided.
  • the combination of the asymmetrical rollers 4 and 5 and the middle collar 8 guides the rollers 4 and 5 at three locations of the inner ring 2, the outer ring 3 and the middle collar 8, so that the guiding accuracy is good.
  • the first roller 4 in the left row and the second roller 5 in the right row have the same maximum diameters D1 max and D2 max and have lengths L1 and L1 along the center lines C1 and C2. L2 is different from each other.
  • the length L2 of the long second roller 5 is 39% or more of the bearing width B.
  • the contact angle ⁇ 2 of the long second roller 5 is larger than the contact angle ⁇ 1 of the short first roller 4.
  • the ratio between the contact angle ⁇ 1 of the short roller 4 and the contact angle ⁇ 2 of the long second roller 5 is set in the range of 1: 2 to 1: 4.
  • the most preferable ratio of the contact angles ⁇ 1 and ⁇ 2 is 1: 3.
  • the range of the contact angle ⁇ 1 is, for example, 5 ° to 7 °
  • the range of the contact angle ⁇ 2 is, for example, 14 ° to 16 °.
  • the position in the bearing width direction at the point P where the action lines S1 and S2 forming the contact angles ⁇ 1 and ⁇ 2 of both rows intersect with each other is closer to the side of the roller 4 that is shorter than the center position Q in the bearing width direction of the middle collar 8. Is shifted by a distance K. Thereby, the contact angle ⁇ 2 of the long roller 5 can be increased without making the long roller 5 longer than necessary.
  • the action lines S1 and S2 are lines on which a combined force of forces acting on the contact portions between the rollers 4 and 5 and the inner ring 2 and the outer ring 3 acts.
  • a point P where the action lines S1 and S2 intersect with each other is located on the bearing center axis O.
  • the rollers 4 and 5 in the left and right rows are held by the cages 10L and 10R, respectively.
  • a plurality of column portions 12 extend to the left side from the annular portion 11, and the left row roller 4 is held in a pocket between these column portions 12.
  • the second right row retainer 10 ⁇ / b> R a plurality of column portions 12 extend from the annular portion 11 to the right side, and the right row rollers 5 are held in pockets between the column portions 12.
  • the double-row self-aligning roller bearing 1 having this configuration is used in applications where axial loads and radial loads are applied and loads having different sizes act on the left and right roller arrays, for example, as a spindle support bearing for a wind power generator.
  • the double row self-aligning roller bearing 1 is installed so that the left row roller 4 is located on the side closer to the swirl blade (front side) and the right row roller 5 is located on the far side (rear side).
  • the roller 5 in the right row having a long length L2 and a large contact angle ⁇ 2 bears almost all of the axial load and a part of the radial load, and the left row has a short length L1 and a small contact angle ⁇ 1.
  • Roller 4 bears the remainder of the radial load.
  • FIG. 10 An axial load assumed when the conventional double row spherical roller bearing 41 shown in FIG. 10 and the double row spherical roller bearing 1 of the present invention shown in FIG. 1 are used as main shaft support bearings of a wind turbine generator.
  • the contact pressures of the left and right rows of rollers in the combined load of the load and radial load were analyzed.
  • 3 shows the contact surface pressure distribution of the rollers 44, 4 in the front side, that is, the left row
  • FIG. 4 shows the distribution of the contact surface pressure analysis results of the rollers 45, 5 in the rear side, that is, the right row.
  • FIG. 10 shows the conventional product shown in FIG. 10
  • the conventional product shown in FIG. 10 has a small contact surface pressure on the front side and a large contact surface pressure on the rear side, and the load load is not uniform between the front side and the rear side.
  • the contact surface pressure is generated on the entire roller on the front side, so that the maximum value of the contact surface pressure on the rear side is lowered and the contact surface pressure difference between both rows is small. Are equalized.
  • FIG. 5 shows the contact surface pressure analysis result distribution of the roller 5 in the rear side, that is, the left row
  • FIG. 6 shows the contact surface pressure analysis result distribution of the roller 4 in the front side, that is, the right row.
  • a contact angle ratio of 1: 1 is a conventional product
  • contact angle ratios of 1: 2 and 1: 3 are contact angle change products of the present invention.
  • the contact surface pressure ratio is 1: 3, and the contact surface pressure is most even on the front side and the rear side.
  • the contact angle ratio of 1: 2 is not equalized compared to the contact angle ratio of 1: 3, but it is sufficiently equalized compared to the contact angle ratio of 1: 1.
  • the contact angle ratio is desirably 1: 2 or more and 1: 4 or less. More desirably, it is in the range of 1.0: 2.5 to 1.0: 3.5.
  • the assumed axial load and radial load refer to the axial load and radial load when the average wind power generator is operating most normally in consideration of various conditions such as power generation capacity and installation location. . Therefore, in a double row self-aligning roller bearing used in a wind power generator having different conditions as compared with an average wind power generator, the optimal contact angle ratio may not be 1: 3. However, even in that case, the optimum contact angle ratio falls within the range of 1: 2 to 1: 4.
  • the ratio of the contact angles of the rollers in both rows is made appropriate within the range of the dimensional standard.
  • Double row spherical roller bearings can be obtained.
  • the ratio of the length L2 of the roller 5 to the bearing width B was investigated. As a result, as shown in FIG. 7, the ratio was found to be 39% or more. It was also found that the ratio was 45% or less.
  • the dimensional standard is a standard that defines an inner diameter, an outer diameter, and a bearing width.
  • a casing 23a of the nacelle 23 is installed on the support base 21 via a swivel bearing 22 (FIG. 9) so as to be horizontally swivelable.
  • a main shaft 26 is rotatably installed via a main shaft support bearing 25 installed in the bearing housing 24, and a blade 27 serving as a swirl wing is formed at a portion protruding from the casing 23 a of the main shaft 26. Is attached.
  • the other end of the main shaft 26 is connected to the speed increaser 28, and the output shaft of the speed increaser 28 is coupled to the rotor shaft of the generator 29.
  • the nacelle 23 is turned at an arbitrary angle by the turning motor 30 via the speed reducer 31.
  • two main shaft support bearings 25 are arranged side by side, but may be one.
  • this double row spherical roller bearing 1A includes (1) a cage 10RA with an inclination angle, (2) a crowning 13, (3) a DLC coating 14, and (4 ) A slot 15 is provided.
  • the structures (1) to (4) do not have to be all provided, and at least one structure may be provided.
  • One cage 10RA for the right row shown in FIG. 13 is a cage that holds the rollers 5 having a long axial length.
  • the retainer 10RA has an inclination angle ⁇ that is inclined inward in the radial direction as the outer diameter surface 12Aa of the column portion 12A moves from the proximal end side toward the distal end side.
  • This inclination angle ⁇ is an angle with respect to the bearing center axis O.
  • the inclination angle ⁇ of the outer diameter surface 12Aa of the cage 10RA is set to a range (0 ⁇ ⁇ ⁇ 2) that is larger than zero and not more than the maximum diameter angle ⁇ 2 of the rollers 5 in the right row.
  • the maximum diameter angle ⁇ 2 is an inclination angle of the position of the maximum diameter D2 max of the roller 5 in the right row with respect to a plane perpendicular to the bearing center axis O.
  • the inner diameter surface of the column portion 12A has an inclined surface portion 12Ab and a flat surface portion 12Ac connected to the inclined surface portion 12Ab.
  • the inclined surface portion 12Ab extends from the proximal end side of the inner diameter surface of the column portion 12A to the vicinity of the middle in the axial direction of the inner diameter surface, and has an inclination angle ⁇ that is inclined radially inward from the proximal end side toward the vicinity of the middle of the axial direction.
  • the inclination angle ⁇ is also an angle with respect to the bearing center axis O, and the inclination angle ⁇ is set to be equal to or larger than the inclination angle ⁇ ( ⁇ ⁇ ⁇ ).
  • the inclination angle ⁇ is set to be several degrees larger than the inclination angle ⁇ .
  • the flat surface portion 12Ac is a flat surface parallel to the bearing center axis O extending in the axial direction from the tip edge of the inclined surface portion 12Ab.
  • the outer diameter surface and the inner diameter surface of the column portion 12 do not have an inclination angle, in other words, are parallel to the bearing center axis O.
  • ⁇ (2) About Crowning 13> 14 is an enlarged cross-sectional view showing a part (XIV part) of FIG. 13 in an enlarged manner.
  • the left and right rows of rollers 4 and 5 each have a crowning 13 at the end of the roller rolling surface.
  • the roller rolling surface in this example has a logarithmic crowning shape expressed by a logarithmic curve.
  • the crowning 13 is not limited to a logarithmic crowning shape.
  • the roller rolling surface may be a compound R crowning shape. By making the R dimension of the crowning portion smaller than the reference R of the roller rolling surface, the composite R crowning shape that increases the drop amount can be formed.
  • each of the rollers 4 and 5 has a DLC film 14 on the roller rolling surface.
  • the DLC film 14 in this example employs a multilayer structure having high adhesion to the rollers 4 and 5 as the base material.
  • the DLC film 14 has a surface layer 16, an intermediate layer 17, and a stress relaxation layer 18.
  • the surface layer 16 is a film mainly composed of DLC in which only a solid target graphite is used as a carbon supply source and the amount of hydrogen contamination is suppressed.
  • the intermediate layer 16 is a layer mainly composed of at least Cr or W formed between the surface layer 16 and the base material.
  • the stress relaxation layer 18 is formed between the intermediate layer 17 and the surface layer 16.
  • the intermediate layer 17 has a structure including a plurality of layers having different compositions, and FIG. 15 illustrates a three-layer structure of 17a to 17c.
  • the layer 17c mainly composed of Cr is formed on the surface of the substrate, the layer 17b mainly composed of W is formed thereon, and the layer 17a mainly composed of W and C is formed thereon.
  • the intermediate layer 17 may include a number of layers equal to or less than this, if necessary.
  • the layer 17a adjacent to the stress relaxation layer 18 can improve the adhesion between the intermediate layer 17 and the stress relaxation layer 18 by mainly including the metal that is the main component of the adjacent layer 17b and carbon.
  • the W content is decreased from the intermediate layer 17b side mainly composed of W toward the stress relaxation layer 18 side mainly composed of C.
  • the adhesion can be further improved.
  • the stress relaxation layer 18 is an inclined layer whose main component is C and whose hardness increases continuously or stepwise from the intermediate layer 17 side to the surface layer 16 side. Specifically, it is a DLC gradient layer obtained by forming a film by using a graphite target in the UBMS method and increasing the bias voltage with respect to the substrate continuously or stepwise.
  • the reason why the hardness increases continuously or stepwise is that the constituent ratio of the graphite structure (SP 2 ) and the diamond structure (SP 3 ) in the DLC structure is biased toward the latter as the bias voltage increases.
  • the surface layer 16 is a film mainly composed of DLC formed by extension of the stress relaxation layer 18, and in particular, a DLC film with a reduced hydrogen content in the structure. Abrasion resistance is improved by reducing the hydrogen content.
  • a method in which hydrogen and a compound containing hydrogen are not mixed into a raw material used for the sputtering process and a sputtering gas by using the UBMS method is used.
  • the case of using the UBMS method has been exemplified for the method of forming the stress relaxation layer 18 and the surface layer 16, but any other known film forming method may be used as long as the hardness can be changed continuously or stepwise. Can be adopted.
  • the total thickness of the multilayer including the intermediate layer 17, the stress relaxation layer 18, and the surface layer 16 is preferably 0.5 ⁇ m to 3.0 ⁇ m. If the total film thickness is less than 0.5 ⁇ m, the abrasion resistance and mechanical strength are inferior, and if the total film thickness exceeds 3.0 ⁇ m, peeling tends to occur.
  • the DLC film 14 is provided only on the outer peripheral surfaces of the rollers 4 and 5, but the DLC film 14 may be provided on both end faces of the rollers 4 and 5. In particular, when the DLC film 14 is provided on one end face of each roller 4, 5 guided to the middle collar 8 (FIG. 13), the one end face of each roller 4, 5 becomes difficult to wear, and the rollers 4, 5 Abrasion resistance can be further increased.
  • the inner ring 2 is connected to the second collar 7 facing the end surface of the long second roller 5 in the axial direction, out of the first and second collars 6 and 7 (FIG. 13). , And a groove 15 for inserting the long second roller 5 into the bearing.
  • an arc-shaped insertion groove 15 is provided at one place in the circumferential direction of the second collar 7 of the inner ring 2.
  • the radius of curvature of the arc 15a of the insertion groove 15 is appropriately set according to the maximum diameter of the roller 5 to be inserted (FIG. 16).
  • the same configuration as the above-described embodiment is provided.
  • each of the rollers 4 and 5 has the DLC film 14 on the roller rolling surface, it is possible to improve wear resistance. As a result, the roller rolling surface and the raceway surface 3a of the outer ring 3 are less likely to be worn than those without the DLC film. Further, since the crowning 13 is provided at the end of the roller rolling surface, the edge stress can be relaxed.
  • the one (second) cage 10RA that holds the long roller 5 has an inclination angle ⁇ that is inclined radially inward as the outer diameter surface 12Aa of the column portion 12A moves from the proximal end side toward the distal end side.
  • the pocket Pt surface of the vessel 10RA can hold the maximum diameter position of the roller 5.
  • the pocket Pt surface of the cage 10RA is maintained near the pitch circle diameter of the rollers 5, and the pocket Pt surface of the cage 10RA during the bearing operation.
  • the maximum diameter position of the rollers 5 can be held smoothly. Thereby, the posture stability of the long roller 5 is not impaired, and the assembling work of the long roller 5 can be easily performed.
  • the inner ring 2 is provided with an insertion groove 15 for inserting the long roller 5 into the bearing in the small brim 7 facing the axially outer end surface of the long roller 5 among the small collars 6, 7. Can be further improved.
  • the inclination angle ⁇ of the outer diameter surface 12Ba of the column portion 12B in one cage 10RB is larger than zero, and the right row roller. 5 is set within a range of the maximum diameter angle ⁇ 2 or less, and the inclination angle ⁇ of the inner diameter surface of the column portion 12B is set to be the same as the inclination angle ⁇ of the outer diameter surface.
  • the inclination angle ⁇ in this example is set to an angle that is equal to or less than the maximum diameter angle ⁇ 2 and is substantially close to the maximum diameter angle ⁇ 2.
  • the inner diameter surface of the column portion 12B is composed only of the inclined surface portion, and the above-described flat surface portion is not provided.
  • the pocket Pt surface of the cage 10RB is more reliably maintained in the vicinity of the pitch circle diameter of the roller 5, and is retained during bearing operation.
  • the pocket Pt surface of the container 10RB can hold the maximum diameter position of the roller 5 smoothly and reliably.
  • the assembly work of the long roller 5 can be performed more easily.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)

Abstract

L'invention concerne un palier à rouleaux sphérique à double rangée (1), dans lequel palier des rouleaux (4, 5) sont interposés, entre une piste de roulement interne (2) et une piste de roulement externe (3), en deux rangées l'une à côté de l'autre dans la direction de la largeur du palier, une surface de piste de roulement (3a) de la piste de roulement externe (3) étant sphérique, et les surfaces périphériques externes des deux rangées de rouleaux (4, 5) ayant une forme de section transversale qui s'adapte à la surface de piste de roulement (3a) de la piste de roulement externe (3). Les deux rangées de rouleaux (4, 5) ont des longueurs différentes (L1, L2), et la longueur (L1) du rouleau long (5) est d'au moins 39 % de la largeur de palier (B). Le rapport de l'angle de contact (θ1) du rouleau court (4) à l'angle de contact (θ2) du rouleau long (5) se trouve à l'intérieur de la plage de 1:2 à 1:4. Par conséquent, la présente invention peut recevoir simultanément tout à la fois une charge axiale et une charge radiale, et peut être utilisée dans des applications dans lesquelles des charges de différentes tailles agissent sur deux rangées de rouleaux l'une à côté de l'autre dans la direction axiale, et rend possible d'augmenter suffisamment, à l'intérieur des contraintes de dimensions de limite, la capacité de charge du rouleau dans la rangée qui reçoit la charge axiale.
PCT/JP2017/011775 2016-03-24 2017-03-23 Palier à rouleaux sphérique à double rangée WO2017164325A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
ES17770365T ES2959734T3 (es) 2016-03-24 2017-03-23 Rodamiento de rodillos autoalineable de doble hilera
CN201780019166.XA CN108884867B (zh) 2016-03-24 2017-03-23 双排自调心滚子轴承
EP17770365.9A EP3434918B1 (fr) 2016-03-24 2017-03-23 Palier à rouleaux sphérique auto-alignés à double rangée
US16/138,504 US10655674B2 (en) 2016-03-24 2018-09-21 Double-row self-aligning roller bearing

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP2016-059474 2016-03-24
JP2016-059473 2016-03-24
JP2016059474 2016-03-24
JP2016059473 2016-03-24
JP2017-045679 2017-03-10
JP2017045679A JP6873754B2 (ja) 2016-03-24 2017-03-10 複列自動調心ころ軸受
JP2017048527A JP6871767B2 (ja) 2016-03-24 2017-03-14 複列自動調心ころ軸受
JP2017-048527 2017-03-14

Related Child Applications (1)

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US16/138,504 Continuation US10655674B2 (en) 2016-03-24 2018-09-21 Double-row self-aligning roller bearing

Publications (2)

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WO2017164325A1 true WO2017164325A1 (fr) 2017-09-28
WO2017164325A8 WO2017164325A8 (fr) 2018-09-07

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JP2019190658A (ja) * 2018-04-20 2019-10-31 Ntn株式会社 複列自動調心ころ軸受
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WO2021060389A1 (fr) * 2019-09-26 2021-04-01 Ntn株式会社 Roulement à rouleaux coniques à double rangée
EP3859177A4 (fr) * 2018-09-26 2022-06-08 NTN Corporation Palier de roulement, dispositif de support d'arbre primaire pour la génération d'énergie éolienne
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JP2019190658A (ja) * 2018-04-20 2019-10-31 Ntn株式会社 複列自動調心ころ軸受
CN111989500A (zh) * 2018-04-20 2020-11-24 Ntn株式会社 多排自动调心滚子轴承
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WO2019203265A1 (fr) * 2018-04-20 2019-10-24 Ntn株式会社 Roulement à rouleaux à alignement automatique à double rangée
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JP7488633B2 (ja) 2018-04-20 2024-05-22 Ntn株式会社 複列自動調心ころ軸受
WO2020067334A1 (fr) * 2018-09-26 2020-04-02 Ntn株式会社 Palier de roulement, dispositif de support d'arbre primaire pour la génération d'énergie éolienne
EP3859177A4 (fr) * 2018-09-26 2022-06-08 NTN Corporation Palier de roulement, dispositif de support d'arbre primaire pour la génération d'énergie éolienne
US11542985B2 (en) 2018-09-26 2023-01-03 Ntn Corporation Rolling bearing and wind power generation rotor shaft support device
JP7373341B2 (ja) 2018-09-26 2023-11-02 Ntn株式会社 転がり軸受、および風力発電用主軸支持装置
WO2021060389A1 (fr) * 2019-09-26 2021-04-01 Ntn株式会社 Roulement à rouleaux coniques à double rangée
JP7456851B2 (ja) 2019-09-26 2024-03-27 Ntn株式会社 複列円すいころ軸受

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