WO2018131617A1 - Roulement à rouleaux à alignement automatique et double rangée et gabarit de prévention de saillie - Google Patents

Roulement à rouleaux à alignement automatique et double rangée et gabarit de prévention de saillie Download PDF

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Publication number
WO2018131617A1
WO2018131617A1 PCT/JP2018/000378 JP2018000378W WO2018131617A1 WO 2018131617 A1 WO2018131617 A1 WO 2018131617A1 JP 2018000378 W JP2018000378 W JP 2018000378W WO 2018131617 A1 WO2018131617 A1 WO 2018131617A1
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WO
WIPO (PCT)
Prior art keywords
row
rollers
double
inner ring
roller bearing
Prior art date
Application number
PCT/JP2018/000378
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English (en)
Japanese (ja)
Inventor
一将 ▲瀬▼古
貴志 山本
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 JP2017160074A external-priority patent/JP7029249B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to CN201880006607.7A priority Critical patent/CN110168238A/zh
Priority to EP18738555.4A priority patent/EP3569882A4/fr
Publication of WO2018131617A1 publication Critical patent/WO2018131617A1/fr
Priority to US16/507,661 priority patent/US10883544B2/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
    • 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
    • F16C23/088—Ball or roller bearings self-adjusting by means of crowning
    • 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
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • 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
    • F16C2360/31—Wind motors
    • 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

Definitions

  • the present invention provides a double-row automatic adjustment applied to a bearing that supports a shaft such as a main shaft of a wind power generator or an industrial machine, for example, in applications where an uneven load is applied to the two rows of rollers arranged in the bearing width direction.
  • the present invention relates to a center roller bearing and a pop-out preventing jig.
  • the bearing that supports the main shaft (shaft) of the wind turbine generator is incorporated in the housing, and in addition to the radial load due to the weight of the blade and the rotor head, an axial load due to wind force acts.
  • the bearing for supporting the main shaft is a double row self-aligning roller bearing 41 as shown in FIG. 16, the axial load Fa is mainly selected from the two rows 44 and 45 interposed between the inner ring 42 and the outer ring 43. Only the roller 45 in one row 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 like a double row spherical 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
  • a roller 65 having a larger diameter can receive a large axial load
  • a roller 64 having a smaller contact angle ⁇ 1 can receive a large radial load
  • Patent Document 2 By setting the contact angles ⁇ 1 and ⁇ 2 so that the load capacities of the rollers 64 and 65 in each row become appropriate, the rolling lives of the rollers 64 and 65 in each row become substantially the same, and the actual life of the entire bearing Can be improved.
  • the center of gravity in the bearing width direction does not match the center position in the bearing width direction. For this reason, the balance is poor, and when the bearing is assembled or assembled into another device, the aligning operation may be performed arbitrarily, and it is necessary to pay attention to handling. For example, as shown in FIG.
  • FIG. 19 shows a double-row self-aligning roller bearing 1 in which the contact angles ⁇ 1, ⁇ 2 of the left and right rows of rollers 4 and 5 are different from each other. The same operation is performed.
  • 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.
  • An object of the present invention is to provide a double row self-aligning roller bearing capable of preventing self-aligning operation.
  • Another object of the present invention is to provide an assembling method capable of incorporating a double row spherical roller bearing into another device safely and efficiently.
  • Still another object of the present invention is to use the double-row spherical roller bearing in the state where the inner ring and the outer ring of the double-row spherical roller bearing face each other by being used when the double-row spherical roller bearing is assembled or incorporated into another device.
  • Another object of the present invention is to provide a pop-out preventing jig that can be inclined with respect to each other and prevent the width surface of the inner ring from protruding in the bearing width direction rather than the width surface of the outer ring.
  • the double-row self-aligning roller bearing according to the present invention has two rows of rollers arranged in the bearing width direction between the inner ring and the outer ring, the raceway surface of the outer ring is spherical, and the two-row roller Is a cross-sectional shape of the outer peripheral surface along the raceway surface of the outer ring, In the two rows of rollers, either one or both of the shape and the contact angle are different from each other, A mounting hole is provided in the width surface of one or both of the inner ring and the outer ring, and the inner ring and the outer ring are inclined to each other with respect to a state in which the inner ring and the outer ring face each other, and more than the width surface of the outer ring. It is possible to attach a pop-out preventing jig that prevents the width surface of the inner ring from popping out in the bearing width direction.
  • This double row spherical roller bearing has different load capacity for each row of rollers because either one or both of the shape and contact angle of the two rows of rollers are different from each other.
  • this double row spherical roller bearing is used under conditions where an axial load and a radial load are applied, the roller having the larger load capacity bears almost all of the axial load and a part of the radial load. The smaller roller bears the rest of the radial load.
  • a pop-out prevention jig is attached to the mounting hole provided in either the inner ring or the outer ring.
  • the inner ring and the outer ring are inclined to each other with respect to the facing state, and the width surface of the inner ring is prevented from jumping out in the bearing width direction rather than the width surface of the outer ring. It can be performed safely and efficiently.
  • the mounting hole may be a screw hole.
  • the attachment hole is a screw hole, the pop-out preventing jig can be easily and firmly attached.
  • This double row self-aligning roller bearing is suitable for supporting the main shaft of the 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 of the row that receives the axial load is the roller with the larger load capacity
  • the roller of the row that receives only the radial load is the roller with the smaller load capacity.
  • the pressure can be made almost uniform.
  • Each of the rows of rollers is provided with a cage, and each cage has an annular ring portion that guides an axially inner end face of each row of rollers, an axially extending from the annular portion, and a circular shape.
  • a plurality of pillars provided at intervals defined along the circumferential direction, and a pocket for holding the rollers between the pillars, and holding one of the rows of rollers that receive an axial load.
  • the vessel may have an inclination angle such that 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 predetermined interval is an interval arbitrarily determined by design or the like.
  • Each of the rollers may have a DLC film on the roller rolling surface.
  • the DLC is an abbreviation for Diamond-like Carbon.
  • wear on the raceway surfaces of the roller rolling surface, the inner ring, and the outer ring is less likely to occur, and the wear resistance can be improved as compared with those without the DLC film.
  • Each roller may have a crowning at the end of the roller rolling surface. In this case, the edge stress can be relaxed.
  • 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 end surface on the outer side in the axial direction of each row of rollers provided on both ends of the outer peripheral surface.
  • the inner ring has a slot into which the roller is inserted into the bearing in the small brim facing the axially outer end surface of the roller of the row receiving the axial load among the small brims. May be. Since such an insertion groove is provided, it is possible to further improve the assemblability of the row roller receiving the axial load into the bearing.
  • the method of assembling the double row spherical roller bearing according to the present invention is a method of incorporating the double row spherical roller bearing into a shaft or a housing, wherein the inner ring and the outer ring are separated by the pop-out preventing jig.
  • the inner ring is incorporated in the shaft and the housing in a state where the inner ring is prevented from jumping out in the bearing width direction with respect to the facing state, and the inner ring is prevented from jumping in the bearing width direction. According to this assembling method, the double row spherical roller bearing can be safely and efficiently incorporated into the shaft and the housing.
  • the pop-out preventing jig of the present invention is used for the double-row self-aligning roller bearing, and a contact material applied to the same width surface of the inner ring and the outer ring in the bearing width direction, A fixing tool that is inserted into the mounting hole and fixes the contact member to the race ring provided with the mounting hole of the inner ring and the outer ring.
  • the inner ring and the outer ring of the double-row self-aligning roller bearing are inclined relative to each other so that the width of the inner ring protrudes in the bearing width direction rather than the width of the outer ring. Therefore, it is possible to safely and efficiently perform the bearing assembly work and the assembly work of the double row spherical roller bearing.
  • FIG. 5 is a partial view showing a state in which the double row self-aligning roller bearing shown in FIG. 4 is suspended by a wire. It is sectional drawing of the double row self-aligning roller bearing which concerns on 2nd Embodiment of this invention. It is an expanded sectional view showing crowning etc. of a roller of a double row self-aligning roller bearing concerning a 3rd embodiment of this invention. It is a figure which shows the relationship between the straight length and PV value of the same time.
  • FIG. 1 is a sectional view of a double row self-aligning roller bearing according to a first embodiment of the present invention.
  • this double-row self-aligning roller bearing 1
  • left and right two-row rollers 4, 5 aligned in the bearing width direction are interposed between an inner ring 2 attached to a shaft 60 and an outer ring 3 attached to a housing 70.
  • 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.
  • the left and right rows of rollers 4 and 5 are held by cages 6 and 7, respectively.
  • the cage 6 for the left row is defined by an annular ring portion 32 that guides the axially inner end face of the roller 4 in the left row, the axial portion extending from the annular portion 32, and the circumferential direction.
  • a plurality of pillar portions 33 provided at intervals are provided, and a pocket Pt for holding the roller 4 is provided between the pillar portions.
  • the right row retainer 7 is defined by an annular ring portion 34 that guides an axially inner end face of the right row roller 5, an axial direction extending from the annular portion 34, and a circumferential direction.
  • a plurality of pillar portions 35 provided at intervals are provided, and a pocket Pt for holding the roller 5 is provided between the pillar portions.
  • collars 8 and 9 are provided, respectively.
  • An intermediate collar 10 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 inner ring 2 may have no collar.
  • the outer ring 3 has an annular oil groove 11 between the left and right roller rows on the outer peripheral surface, and oil holes 12 penetrating from the oil groove 11 to the inner peripheral surface are provided at one or a plurality of locations in the circumferential direction. ing.
  • the left and right rollers 4 and 5 have the same lengths L1 and L2 along the center lines C1 and C2, the same maximum diameters D1max and D2max, and the left and right rows.
  • the rollers 4 and 5 are all asymmetric rollers.
  • the asymmetric roller is an asymmetrical roller in which the positions of the maximum diameters D1max and D2max deviate from the center of the roller length.
  • the position of the maximum diameter D1max of the roller 4 in the left row is on the right side of the center of the roller length
  • the position of the maximum diameter D2max of the roller 5 in the right row is on the left side of the center of the roller length. is there.
  • the contact angle ⁇ 2 of the roller 5 in the right row is set larger than the contact angle ⁇ 1 of the roller 4 in the left row.
  • the action lines S1 and S2 forming the contact angles ⁇ 1 and ⁇ 2 of the rollers 4 and 5 in each row intersect with each other at the alignment center point P on the bearing center axis O. Thereby, the inner ring 2 and the rollers 4 and 5 can be aligned along the raceway surface 3 a of the outer ring 3. The position of the alignment center point P in the bearing width direction is shifted toward the roller 4 having the smaller contact angle ⁇ 1 than the center position Q of the middle collar 8 in the bearing width direction.
  • 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.
  • crowning may be provided on the rolling surface 13 of one or both of the rollers 4 and 5 in each of the left and right rows.
  • the curvature diameters of both end portions 13b and 13c are made smaller than the central portion 13a of the rolling surface 13.
  • the shape of the crowning is, for example, a logarithmic curve. In addition to the logarithmic curve, a straight line, a single arc, or a combination of a plurality of arcs may be used.
  • the crowning at both ends of the rolling surfaces 13 of the rollers 4 and 5 in this way, the surface pressures at both ends 13b and 13c having a large sliding speed on the rolling surfaces 13 of the rollers 4 and 5 are reduced, and the PV value (surface The absolute value of (pressure ⁇ sliding speed) is suppressed, and friction can be reduced.
  • the double-row self-aligning roller bearing 1 shown in FIG. 1 has a center of gravity (not shown) and a bearing in the bearing width direction because the contact angles ⁇ 1 and ⁇ 2 of the rollers 4 and 5 in the left and right rows are different as described above.
  • the center position Q in the width direction does not match and the balance is poor. For this reason, there is a possibility that a self-aligning operation may be performed at the time of assembling the double-row self-aligning roller bearing 1 or assembling it into another device. Therefore, mounting holes 15 and 16 are provided at three or more locations in the circumferential direction on the width surfaces 2c and 3b of the inner ring 2 and the outer ring 3 to which pop-out preventing jigs (see FIG.
  • These mounting holes 15 and 16 are preferably provided in the width surfaces 2c and 3b which are wider in the radial direction among the width surfaces 2c, 2d, 3b and 3c on both sides of the inner ring 2 and the outer ring 3 in the bearing width direction.
  • the attachment holes 15 and 16 are screw holes.
  • FIG. 3 is an exploded perspective view of the pop-out preventing jig according to the first embodiment.
  • the pop-out stopper 17 includes a pad 18 and a fixture 19.
  • the contact member 18 is an elongated plate member, and a fixture insertion hole 18a penetrating in the thickness direction is provided at one end in the longitudinal direction.
  • the fixing tool 19 is made of a bolt, can be inserted into the fixing tool insertion hole 18a of the abutting member 18, and can be screwed into the mounting holes 15 and 16 including screw holes.
  • the pop-out stopper 17 is attached to the mounting holes 15 and 16 of the double-row self-aligning roller bearing 1. That is, the contact member 18 is applied to the width surfaces 2 c and 3 c (or the width surfaces 2 d and 3 b) on the same side in the bearing width direction of the inner ring 2 and the outer ring 3, and the contact member 18 is fixed to the inner ring 2 or the outer ring 3 by the fixture 19.
  • the fixing method is such that the fixing tool 19 is placed on the outer side in the bearing width direction in a state where the fixing tool insertion hole 18a of the abutting member 18 and the mounting holes 15 and 16 of the inner ring 2 or the outer ring 3 are aligned in the circumferential direction and radial position.
  • the pop-out preventing jig 17 can be easily and firmly attached.
  • the contact member 18 of the pop-out stopper 17 causes the width surfaces 2 c, 3 c of the inner ring 2 and the outer ring 3.
  • the width surfaces 2d and 3b is prevented from inclining with respect to the state in which the inner ring 2 and the outer ring 3 face each other.
  • the width surfaces 2d and 2c of the inner ring 2 are prevented from jumping out in the bearing width direction from the width surfaces 3b and 3c of the outer ring 3.
  • the double-row self-aligning roller bearing 1 is incorporated in the shaft 60 or the housing 70 with the pop-out stopper 17 attached to the mounting holes 15 and 16. After completion of the assembly of the double-row self-aligning roller bearing 1, the pop-out stopper 17 is removed from the mounting holes 15 and 16.
  • the pop-out stoppers 17 are respectively attached to the mounting holes 15 and 16 of both the inner ring 2 and the outer ring 3, but the pop-out stoppers 17 are attached only to the one mounting hole 15 or the mounting hole 16. It may be attached.
  • the center position Q in the bearing width direction is located on the right side of the drawing with respect to the centering center point P. A force that tends to rotate in the bearing width direction along the raceway surface 3a of the outer ring 3 is likely to act. For this reason, when attaching the pop-out stopper 17 only to one of the attachment holes 15 or 16, it is desirable to attach the pop-out stopper 17 to the attachment hole 16 of the outer ring 3 so as to receive the force.
  • the mounting holes 15 and 16 of the double-row self-aligning roller bearing 1 are screw holes and the fixing tool 19 of the pop-out stopper 17 is a bolt, but the present invention is not limited to this.
  • the attachment holes 15 and 16 and the fixture 19 may be configured so that the contact member 18 can be fixed to the inner ring 2 or the outer ring 3.
  • the mounting holes 15 and 16 may be pin holes
  • the fixing tool 19 may be a pin inserted in a fixed state in the pin hole.
  • the double-row spherical roller bearing 1 When the double-row spherical roller bearing 1 is assembled or assembled into another device, as shown in FIG. 5, the double-row spherical roller bearing 1 is in a posture in which the bearing center axis O is in the vertical direction. A pin 71 is inserted into the oil hole 12 of the outer ring 3, and a wire 72 is hooked on the pin 71 and suspended. At this time, if the pop-out stopper 17 is attached to the attachment holes 15 and 16, the inner ring 2 and the outer ring 3 are inclined with respect to the facing state, and the inner ring 2 is more than the width surfaces 3 b and 3 c of the outer ring 3. The width surfaces 2d and 2c are prevented from jumping out in the bearing width direction. For this reason, the bearing assembly work and the assembly work of the double row self-aligning roller bearing 1 can be performed safely and efficiently.
  • 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 large contact angle ⁇ 2 bears almost all of the axial load and a part of the radial load
  • the roller 4 in the left row having a small contact angle ⁇ 1 bears the rest of the radial load.
  • the double-row self-aligning roller bearing 1 of the first embodiment is different from each other in both shapes and contact angles ⁇ 1 and ⁇ 2 of the two rows of rollers 4 and 5, but only one of the shape and the contact angle.
  • the present invention can also be applied to double-row self-aligning roller bearings having different diameters. Different shapes include a difference in roller length, a difference in maximum diameter, a difference between a symmetric roller and an asymmetric roller, and the like.
  • This double row self-aligning roller bearing 1 includes a cage 7A with an inclination angle.
  • One retainer 7A for the right row shown in FIG. 6 is a retainer for holding the rollers 5 in the row receiving the axial load.
  • the retainer 7A has an inclination angle ⁇ that is inclined inward in the radial direction as the outer diameter surface 35Aa of the column portion 35A 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 cage 7A is set to a range (0 ⁇ ⁇ ⁇ 2) that is larger than zero and equal to or less than the maximum diameter angle ⁇ 2 of the roller 5.
  • the maximum diameter angle ⁇ 2 is an inclination angle of a position where the maximum diameter D2max of the rollers 5 in the right row is relative to a plane perpendicular to the bearing center axis O.
  • the inner diameter surface of the column portion 35A has an inclined surface portion 35Ab and a flat surface portion 35Ac connected to the inclined surface portion 35Ab.
  • the inclined surface portion 35Ab extends from the base end side of the inner diameter surface of the column portion 35A to the vicinity of the middle in the axial direction of the inner diameter surface, and has an inclination angle ⁇ inclined inward in the radial direction from the base end side toward the vicinity of the axial middle.
  • 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 35Ac 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 35Ab.
  • the outer diameter surface and the inner diameter surface of the column portion 33 do not have an inclination angle, in other words, are parallel to the bearing center axis O.
  • the pocket surface of the cage 7A can hold the maximum diameter position of the roller 5. As a result, the posture stability of the rollers 5 in the row receiving the axial load is not impaired, and the roller 5 can be easily assembled.
  • the left and right rows of rollers 4 and 5 each have crowning Cw at the end portions 13 b and 13 c of the roller rolling surface 13. It may be.
  • composite R crowning that increases the drop amount by applying the end portions 13b and 13c of the roller rolling surface 13 to be smaller than the reference R of the roller rolling surface 13 is applied.
  • the length Ls (hereinafter referred to as “straight length”) of the roller central portion 13a not provided with the crowning Cw is 50% to 70%, preferably 60% of the total length L1 (L2).
  • FIG. 8 is a graph showing the relationship between the PV value (surface pressure ⁇ slip speed) and the straight length when an average wind load is applied to the double row spherical roller bearing for the wind turbine main bearing.
  • the rollers 4 and 5 in each row may have a DLC film 14 on the roller rolling surface 13.
  • 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 36, an intermediate layer 37, and a stress relaxation layer 38.
  • the surface layer 36 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 mixed hydrogen is suppressed.
  • the intermediate layer 37 is a layer mainly composed of at least Cr or W formed between the surface layer 36 and the base material.
  • the stress relaxation layer 38 is formed between the intermediate layer 37 and the surface layer 36.
  • the intermediate layer 37 has a structure including a plurality of layers having different compositions, and FIG. 10 illustrates a three-layer structure of 37a to 37c.
  • a layer 37c mainly composed of Cr is formed on the surface of the substrate, a layer 37b mainly composed of W is formed thereon, and a layer 37a mainly composed of W and C is formed thereon.
  • the intermediate layer 37 may include a number of layers less than or greater than that as necessary.
  • the layer 37a adjacent to the stress relaxation layer 38 can improve the adhesion between the intermediate layer 37 and the stress relaxation layer 38 by mainly including the metal that is the main component of the adjacent layer 37b and carbon.
  • the layer 37a is mainly composed of W and C
  • the W content is decreased from the intermediate layer 37b mainly composed of W toward the stress relaxation layer 38 mainly composed of C.
  • the adhesion can be further improved.
  • the stress relaxation layer 38 is an inclined layer whose main component is C and whose hardness increases continuously or stepwise from the intermediate layer 37 side to the surface layer 36 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 (SP2) and the diamond structure (SP3) in the DLC structure is biased toward the latter as the bias voltage increases.
  • the surface layer 36 is a film mainly composed of DLC formed by extension of the stress relaxation layer 38, and in particular, is 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 38 and the surface layer 36, but any other known film forming method can 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 37, the stress relaxation layer 38, and the surface layer 36 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.
  • the DLC film 14 is provided on one end surface of each roller 4, 5 guided to the middle collar 10 (FIG. 6), the one end surface of each roller 4, 5 becomes difficult to wear. Abrasion resistance can be further increased.
  • the inner ring 2 is the axial direction of the roller 5 in the row that receives the axial load among the small collars 8 and 9 (FIG. 6).
  • An insertion groove 20 for inserting the roller 5 into the bearing may be provided in the small collar 9 facing the outer end surface.
  • an arc-shaped insertion groove 20 is provided at one place in the circumferential direction of the small collar 9 of the inner ring 2.
  • the radius of curvature of the arc 20a of the insertion groove 20 is appropriately set according to the maximum diameter of the roller 5 to be inserted (FIG. 11).
  • the inclination angle ⁇ of the outer diameter surface 35Aa of the column portion 35A in one of the cages 7A for the right row is less than zero.
  • the inclination angle ⁇ of the inner diameter surface 35Ad of the column portion 35A may be set to be the same as the inclination angle ⁇ of the outer diameter surface 35Aa.
  • 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 35Ad of the column portion 35A is composed only of an inclined surface portion, and the above-described flat surface portion is not provided.
  • the pocket Pt surface of the cage 7A is more reliably maintained near the pitch circle diameter of the roller 5, and is retained during the bearing operation.
  • the pocket Pt surface of the container 7A can hold the maximum diameter position of the roller 5 smoothly and reliably. Also, the roller 5 can be assembled more easily.
  • a casing 23a of the nacelle 23 is installed on the support base 21 via a swivel bearing 22 (FIG. 15) 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.
  • the double-row self-aligning roller bearing 1 according to any one of the above embodiments is used.
  • the roller 5 having the larger contact angle ⁇ 2 is used as the row farther from the blade 27.
  • the roller 4 having the smaller contact angle ⁇ 1 is used as the roller closer to the blade 27.
  • the present invention is not limited to the above embodiment, and various additions, changes, or deletions are possible without departing from the gist of the present invention. Therefore, such a thing is also included in the scope of the present invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un roulement à rouleaux à alignement automatique et double rangée (1) comprenant des rouleaux (4, 5) interposés en deux rangées en parallèle dans la direction de la largeur du roulement entre un anneau interne (2) et un anneau externe (3). La surface de chemin de roulement (3a) de l'anneau externe (3) a une forme sphérique. La surface circonférentielle externe de chacun des rouleaux (4, 5) a une forme en section transversale s'adaptant à la surface de chemin de roulement (3a) de l'anneau externe (3). Les formes et/ou les angles de contact (θ1, θ2) des rouleaux (4, 5) diffèrent l'un par rapport à l'autre. Des trous de montage (15, 16), dans lesquels un gabarit de prévention de saillie (17) peut être monté, sont disposés dans des surfaces de largeur (2c, 3b) d'au moins un anneau quelconque parmi l'anneau interne (2) et l'anneau externe (3). Le gabarit de prévention de saillie (17) empêche les surfaces de largeur (2c, 2d) de l'anneau interne (2) de faire saillie davantage dans la direction de la largeur du roulement que les surfaces de largeur (3b, 3c) de l'anneau externe (3).
PCT/JP2018/000378 2017-01-13 2018-01-10 Roulement à rouleaux à alignement automatique et double rangée et gabarit de prévention de saillie WO2018131617A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201880006607.7A CN110168238A (zh) 2017-01-13 2018-01-10 双排自动调心滚子轴承及凸出防止夹具
EP18738555.4A EP3569882A4 (fr) 2017-01-13 2018-01-10 Roulement à rouleaux à alignement automatique et double rangée et gabarit de prévention de saillie
US16/507,661 US10883544B2 (en) 2017-01-13 2019-07-10 Double-row self-aligning roller bearing and protrusion prevention jig

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2017003895 2017-01-13
JP2017-003895 2017-01-13
JP2017160074A JP7029249B2 (ja) 2017-01-13 2017-08-23 複列自動調心ころ軸受および飛出し止め治具
JP2017-160074 2017-08-23

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US16/507,661 Continuation US10883544B2 (en) 2017-01-13 2019-07-10 Double-row self-aligning roller bearing and protrusion prevention jig

Publications (1)

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WO2018131617A1 true WO2018131617A1 (fr) 2018-07-19

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022050298A1 (fr) * 2020-09-04 2022-03-10 Ntn株式会社 Gabarit de prévention de saillie et roulement à rotule sur rouleaux à double rangée

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JP2001065574A (ja) * 1999-08-31 2001-03-16 Nsk Ltd ころ軸受
JP2004108429A (ja) * 2002-09-17 2004-04-08 Nsk Ltd 円すいころ軸受
JP2004245251A (ja) * 2003-02-10 2004-09-02 Nsk Ltd 自動調心ころ軸受
JP2005061594A (ja) * 2003-08-20 2005-03-10 Nsk Ltd 自動調心ころ軸受
WO2005050038A1 (fr) 2003-11-18 2005-06-02 Ntn Corporation Roulement a rotule sur deux rangees de rouleaux et dispositif de support d'un arbre secondaire de turbo-generateur d'eolienne
JP2005207517A (ja) * 2004-01-23 2005-08-04 Ntn Corp 自動調心ころ軸受および風力発電機主軸支持装置
DE102010054318A1 (de) * 2010-12-13 2012-06-14 Schaeffler Technologies Gmbh & Co. Kg Rotorlagerung einer Windkraftanlage
JP2013044374A (ja) * 2011-08-24 2013-03-04 Ntn Corp 円すいころ軸受
US20140112607A1 (en) 2012-10-18 2014-04-24 Schaeffler Technologies AG & Co. KG Roller bearing for wind turbines

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001065574A (ja) * 1999-08-31 2001-03-16 Nsk Ltd ころ軸受
JP2004108429A (ja) * 2002-09-17 2004-04-08 Nsk Ltd 円すいころ軸受
JP2004245251A (ja) * 2003-02-10 2004-09-02 Nsk Ltd 自動調心ころ軸受
JP2005061594A (ja) * 2003-08-20 2005-03-10 Nsk Ltd 自動調心ころ軸受
WO2005050038A1 (fr) 2003-11-18 2005-06-02 Ntn Corporation Roulement a rotule sur deux rangees de rouleaux et dispositif de support d'un arbre secondaire de turbo-generateur d'eolienne
JP2005207517A (ja) * 2004-01-23 2005-08-04 Ntn Corp 自動調心ころ軸受および風力発電機主軸支持装置
DE102010054318A1 (de) * 2010-12-13 2012-06-14 Schaeffler Technologies Gmbh & Co. Kg Rotorlagerung einer Windkraftanlage
JP2013044374A (ja) * 2011-08-24 2013-03-04 Ntn Corp 円すいころ軸受
US20140112607A1 (en) 2012-10-18 2014-04-24 Schaeffler Technologies AG & Co. KG Roller bearing for wind turbines

Non-Patent Citations (1)

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Title
See also references of EP3569882A4

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022050298A1 (fr) * 2020-09-04 2022-03-10 Ntn株式会社 Gabarit de prévention de saillie et roulement à rotule sur rouleaux à double rangée

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