CN114514382A - Double-row tapered roller bearing - Google Patents

Double-row tapered roller bearing Download PDF

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Publication number
CN114514382A
CN114514382A CN202080067729.4A CN202080067729A CN114514382A CN 114514382 A CN114514382 A CN 114514382A CN 202080067729 A CN202080067729 A CN 202080067729A CN 114514382 A CN114514382 A CN 114514382A
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CN
China
Prior art keywords
load
row
roller bearing
tapered roller
contact angle
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Pending
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CN202080067729.4A
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Chinese (zh)
Inventor
颜伟达
伊藤智仁
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NTN Corp
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NTN Corp
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Publication date
Priority claimed from JP2020092067A external-priority patent/JP7456851B2/en
Application filed by NTN Corp filed Critical NTN Corp
Publication of CN114514382A publication Critical patent/CN114514382A/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
    • 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
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/56—Systems consisting of a plurality of bearings with rolling friction in which the rolling bodies of one bearing differ in diameter from those of another
    • 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
    • F16C33/58—Raceways; Race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/08—Rigid support of bearing units; Housings, e.g. caps, covers for spindles
    • F16C35/12—Rigid support of bearing units; Housings, e.g. caps, covers for spindles with ball or roller bearings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Abstract

A double row tapered roller bearing (1) in face-to-face combination,wherein the contact angle theta of the load line (A) of the axial loadAA contact angle theta larger than that of the non-load side row (B)BAnd the contact angles theta of the two columns (A, B)A、θBThe difference is 15 DEG or more. Either or both of the roller length and the roller diameter of the rollers of the non-load side row (B) may also be larger than those of the rollers of the load side row (a). The values of the contact angles of the columns may also satisfy: contact angle theta of load line (A) of 25 DEG or lessAA contact angle theta of 35 DEG or less and 5 DEG or less to the non-load side row (B)B≤15°。

Description

Double-row tapered roller bearing
RELATED APPLICATIONS
The application claims priority of applications having application numbers of JP patent application nos. 2019-175909 at 26 th 9 th 2019 and JP patent application nos. 2020-092067 at 27 th 2020, which are incorporated herein by reference in their entireties as part of the present application.
Technical Field
The present invention relates to a double-row tapered roller bearing designed to be asymmetric in left and right rows, for example, a double-row tapered roller bearing such as a bearing for a main shaft of a wind turbine generator.
Background
As a tapered roller bearing with a self-aligning ring, it has been proposed to increase the load capacity of rows in the load axis direction by making the roller lengths, roller diameters, and the like of the right and left rows of a double-row tapered roller bearing different from each other (for example, patent document 1).
Documents of the prior art
Patent document
Patent document 1: JP 2006-177446 publication
Disclosure of Invention
Problems to be solved by the invention
An arrangement in which a double row tapered roller bearing and a cylindrical roller bearing are combined in a face-to-face manner is often used as a bearing device for a windmill main shaft.
One of the main causes of insufficient strength of the double row tapered roller bearing is: when unbalanced loads are generated in the rollers in two rows due to the axial load and the specifications of the two rows are the same, it is considered that the load row, which is the row mainly receiving the axial load, reaches the fatigue limit first. Therefore, in the general design concept, the load capacity of the load train is increased.
However, since the wind load of the wind turbine is not constant, a large load may be applied to the non-load side train, and a high load capacity of the non-load side train is also required. Therefore, in the conventional design concept, the load capacity of the non-load side train is insufficient, and the safety factor of the non-load side train becomes strict with respect to the standard.
The invention provides a double row tapered roller bearing, wherein load loads in two rows are balanced under a load condition generated when an axial load mainly acts from one direction and an axial load also acts in the opposite direction by rationalizing a contact angle, and the service life of the whole bearing can be prolonged.
Means for solving the problems
The double row tapered roller bearing of the present invention relates to a double row tapered roller bearing combined in a face-to-face manner, wherein a contact angle of a load row as a row mainly receiving an axial load is larger than a contact angle of a non-load side row as a row on the opposite side, and a difference between the contact angles of the two rows is 15 ° or more.
The above-mentioned "main" indicates directions in which the axial load acts for a plurality of times when the direction of the axial load varies in the direction of the axial load if the direction of the axial load is fixed.
According to this configuration, the contact angle of the load row is larger than the contact angle of the non-load side row, and therefore the load capacity of the axial load of the load row is improved. In contrast, the load capacity of the radial load of the load train is reduced. In the double row tapered roller bearing, as for the applied load, generally, the radial load is larger than the axial load, and the radial load is a load of two rows. Therefore, the double row tapered roller bearing needs to achieve a balance between the axial load and the radial load of the bearing as a whole.
In this case, since the difference between the contact angles of the two rows is increased to 15 ° or more, the contact angle of the load side row can be increased to some extent, and the contact angle of the non-load side row can be sufficiently reduced. By reducing the contact angle of the non-load side row, the load capacity of the radial load of the non-load side row is improved, and the reduction in the load capacity of the radial load of the load side row can be compensated for. Thus, considering both the axial load and the radial load, the load loads in the two rows are balanced, the life of the two rows is balanced, and the life of the entire bearing can be extended.
In the present invention, either one or both of the roller length and the roller diameter of the rollers in the non-load side row may be larger than the roller length and the roller diameter of the rollers in the load side row.
The double row tapered roller bearing may be used under conditions where the direction and magnitude of the load greatly vary. For example, when used as a bearing for a main shaft of a wind turbine generator, a wind load of a wind turbine changes greatly, and therefore a large load may be applied to a non-load side train. In such a case, if either or both of the roller length and the roller diameter of the rollers in the non-load side row are larger than those of the rollers in the load side row, the safety factor criterion is easily satisfied even when a large axial load and a large radial load are applied to the non-load side row.
Particularly preferably, in the present invention, not only the difference between the contact angles of the two rows is 15 ° or more, but also the contact angle of each row satisfies the following condition:
the contact angle of the load line is more than or equal to 25 degrees and less than or equal to 35 degrees
The contact angle of the non-load side row is more than or equal to 5 degrees and less than or equal to 15 degrees.
When the contact angle of the load-side row is 25 ° or more and the contact angle of the non-load-side row is 15 ° or less, the distance M between the points of action of the two rows on the central axes of the two rows is about 50% to 75% of that of a double-row tapered roller bearing designed to be bilaterally symmetrical. Therefore, the load ratio of the radial load in the non-load side row is higher than that in the double-row tapered roller bearing designed to be bilaterally symmetrical. In this way, the load ratio of the radial load in the non-load side row becomes high, and under the use condition where the axial load acts biased in one direction, the load in two rows can be equalized as compared with the symmetrical design.
If the contact angle of the load line is 35 ° or more, the load capacity of the radial load of the load line decreases, and this is not preferable. Further, if the contact angle of the non-load side row is 5 ° or less, the load capacity of the axial load is insufficient when the axial load acts in the opposite direction.
Also in the present invention, the ratio of the pitch circle diameters of the rollers of the two rows (PCD)A/PCDB) Satisfies the following conditions:
0.9≤(PCDA/PCDB)≤1.1。
if the contact angles are made different between the two rows, a difference in the required height of the center flange occurs between the two rows. In order to suppress the difference in height between the middle flanges, it is preferable to quantitatively determine the ratio of the Pitch Circle Diameters (PCD) of the two rows in advanceA/PCDB) The ratio of Pitch Circle Diameters (PCD)A/PCDB) Set to 0.9. ltoreq. PCD as described aboveA/PCDB) The range of 1.1 or less, thereby preventing the difference in height between the two rows of the flanges from becoming excessively large.
Preferably, in the present invention, when the inner ring has the intermediate flange between the track surfaces of the two rows, the thickness TH of the intermediate flange satisfies:
TH is less than or equal to 0.15 multiplied by the width of the inner ring.
When an axial load is applied to the center flange, a certain thickness TH is required to suppress the axial movement of the roller, but if the thickness TH of the center flange is increased beyond the range of 0.15 × the inner ring width, the track surface width and the roller length are unnecessarily reduced by the center flange.
The bearing for a main shaft of a wind turbine generator according to the present invention is a double-row tapered roller bearing having any one of the above-described structures according to the present invention.
In the case of the bearing for the main shaft of the wind turbine generator, the wind load of the wind turbine greatly varies with time, and therefore, the operation and effect of the structure of the double-row tapered roller bearing of the present invention can be effectively exhibited.
Any combination of at least two of the aspects, etc. disclosed in the claims and/or the description and/or the drawings is comprised in the present invention. In particular, any combination of two or more of the individual claims in the claims is also encompassed by the present invention.
Drawings
The present invention can be more clearly understood by the following description of the preferred embodiments with reference to the accompanying drawings. However, the embodiments and drawings are only for illustration and description and are not intended to limit the scope of the present invention. The scope of the invention is defined by the claims. In the drawings, like reference characters designate like or equivalent parts throughout the several views.
Fig. 1 is a partial sectional view of a double row tapered roller bearing according to embodiment 1 of the present invention;
fig. 2 is a sectional view showing the dimensions of each part of the double row tapered roller bearing;
FIG. 3 is a partially cut-away front view of rollers of two rows in the double row tapered roller bearing;
fig. 4A is an explanatory view showing a simulation example of a rolling element load distribution under a fatigue load in a load train of a double row tapered roller bearing which is a symmetrical product in the past;
fig. 4B is an explanatory view showing a simulation example of rolling element load distribution under fatigue load in the load train of the double row tapered roller bearing of design (1) of embodiment 1;
fig. 4C is an explanatory view showing a simulation example of rolling element load distribution under fatigue load in the load train of the double row tapered roller bearing of design (2) of embodiment 1;
fig. 5A is an explanatory view showing a simulation example of a rolling element load distribution under a fatigue load in a non-load side row of a double row tapered roller bearing of a conventional symmetrical product;
fig. 5B is an explanatory view showing a simulation example of the rolling element load distribution under fatigue load in the non-load side row of the double row tapered roller bearing of design (1) of embodiment 1;
fig. 5C is an explanatory view showing a simulation example of the rolling element load distribution under fatigue load in the non-load side row of the double row tapered roller bearing of design (2) of embodiment 1;
FIG. 6 is a partial sectional view of a double row tapered roller bearing according to another embodiment of the present invention;
fig. 7 is a sectional view of a bearing device combining the double-row tapered roller bearing and the cylindrical roller bearing;
fig. 8 is a sectional view of a wind turbine generator in which the double row tapered roller bearing according to embodiment 1 is used as a bearing for a main shaft of the wind turbine generator.
Detailed Description
< embodiment 1 >
Embodiment 1 of the present invention will be described with reference to fig. 1 and 2.
The double row tapered roller bearing 1 has a contact angle θ of the left and right rows A, BA、θBThe left and right asymmetric types are different from each other and face-to-face combined. The double row tapered roller bearing 1 is constituted by an inner ring 2, an outer ring 3, double row rollers 6, 7, and two cages 8, 9, the inner ring 2 and the outer ring 3 are respectively provided in left and right rows A, B, the double row rollers 6, 7 are respectively interposed between double row raceway surfaces 4, 5 of the inner and outer rings 2, 3, and the two cages 8, 9 respectively hold the rollers 6, 7 of each row. The rollers 6, 7 of each row are tapered rollers. The rollers 6 and 7 in each row have a large diameter at the middle side in the bearing width direction.
In the present embodiment, a face-to-face combination type is formed in which the inner ring 2 is formed of a single member having double-row raceway surfaces 4, and the outer ring 3 is formed of two single-row outer rings 3A, 3B formed separately.
The two rows of raceway surfaces 4 and 4 of the inner ring 2 are tapered surfaces having a large diameter at the center in the bearing width direction. An intermediate flange 11 is provided on the outer peripheral surface of the inner ring 2 between the two rows of raceway surfaces 4, 4. The outer peripheral surface portion of the middle flange 11 ranging from the vicinity of the center in the width direction to the non-load row side row end is in a tapered surface shape gradually decreasing toward the non-load row side row B side. End flanges 12, 12 are provided adjacent to the bearing end portions of the raceway surfaces 4, 4.
The two rows of raceway surfaces 5 and 5 of the outer ring 3 are tapered surfaces having a large diameter at the center in the bearing width direction. The inclination angles of the raceway surfaces 5, 5 of the two rows of the outer ring 3 and the inclination angles of the raceway surfaces 4, 4 of the inner ring are different by the inclination angles of the outer peripheral surfaces of the rollers 6, 7. The outer race 3 has no flange. An outer lane spacer 3C is interposed between the outer lanes 3A, 3B in the two rows.
In the double rowIn the tapered roller bearing 1, the left row a in the figure is a load-side row, and the right row B is a non-load-side row. The contact angle θ of the load line A is determined by the difference in the inclination angles of the raceway surfaces 4 and 5 of the inner and outer races 2 and 3 and the taper angles of the rollers 6 and 7AAt a contact angle theta greater than that of the non-load side row BBIn a manner described above. The load line a is a line on the side where the axial load F acting on the inner ring 2 when the inner ring rotates or the axial load G acting on the outer ring 3A when the outer ring rotates is mainly applied. The non-load side row B is a row on the opposite side of the load side row a.
Contact angle theta of load line AAContact angle theta with non-load side row BBThe difference is 15 DEG or more. In addition, the contact angle θ of each column A, BA、θBIs set to a range satisfying the following formula:
25 DEG or less (contact angle theta of load line A)A)≤35°
5 DEG or less (contact angle theta of non-load side row BB)≤15°。
Regarding the roller length and the roller diameter of the rollers 6, 7 of the two rows A, B, the roller length L of the roller 7 of the non-load side row B is setB(FIG. 2) and roller diameter DBRoller length L greater than load row AAAnd roller diameter DA(not shown in the figures). In addition, only the roller length L of the rollers 7 in the non-load side row B may be setBAnd roller diameter DBIs greater than the load train a. When the end portions of the rollers 6 and 7 are provided with chamfered portions on the outer peripheral surfaces, the roller length L is determinedA、LBThe comparison of (1) may be performed by comparing the lengths including the width of the chamfered portion with each other, or may be performed by comparing the lengths not including the width of the chamfered portion with each other. Roller diameter DA、DBThe largest diameter of the rollers 6, 7 of each row.
A center hole 6-1 is provided in the center of the large end face of the row a roller 6 (see fig. 3). The center hole 7-1 is arranged in the middle of the large end face of the roller 7 in the row B, and the annular identification mark 7-2 is arranged on the small end face.
Pitch circle diameter PCD of two rows A, B of roller arraysA、PCDBRatio of (PCD)A/PCDB) Satisfies the following conditions:
0.9≤(PCDA/PCDB)≤1.1。
the thickness TH of the center flange 11 between the raceway surfaces 4, 4 of the two rows A, B of the inner ring 2 satisfies:
TH is less than or equal to 0.15 multiplied by the width W of the inner ring.
The height HA on the a-column side and the height HB on the B-column side of the middle flange 11 satisfy:
HA.gtoreq.HB (preferably, HA. HB).
With respect to the height CA of the contact point with the row a rollers and the height CB of the contact point with the row B rollers of the middle flange 11 described above, the following are satisfied:
|CA—CB|≤3mm。
< action, Effect, detailed construction >
According to this structure, the contact angle θ of the load line A due to the loadA(FIG. 1) contact Angle θ with respect to non-load side column BBTherefore, the load capacity of the axial load of the load train a is improved. In contrast, the load capacity of the radial load of the load train a is reduced. In the double row tapered roller bearing, as to the applied load, generally, the radial load is larger than the axial load, and the radial load is loaded by two rows. Therefore, the double row tapered roller bearing needs to achieve a balance between the axial load and the radial load of the bearing as a whole. In this case, the contact angle θ of the two rows A, B is set to be equal toA、θBThe difference is increased to 15 DEG or more, so that the contact angle theta of the load line A can be increased to some extentAAnd the contact angle theta of the non-load side row B can be sufficiently reducedB. By making the contact angle theta of the non-load side row BBThe load capacity of the radial load of the non-load side row B is improved as the load becomes smaller, and the reduction in the load capacity of the radial load of the load row a can be compensated for. Thus, considering both the axial load and the radial load, the load at the row A, B is balanced, the life of the row A, B is balanced, and the life of the entire bearing can be extended.
Further, the roller length L of the rollers 7 in the non-load side row BBGreater than loadRoller length L of rollers in load train AA. Therefore, the following advantages can be obtained. The double row tapered roller bearing may be used under conditions where the direction and magnitude of the load greatly vary. For example, when used as a bearing for a main shaft of a wind turbine generator, a wind load of a wind turbine changes greatly, and thus a large load may be applied to the non-load side train. In this case, if the roller length L of the rollers 7 in the non-load side row B is set to be longer than that in the other rowBRoller length L of roller 6 larger than load row AAEven when a large load is applied to the non-load side row B, the safety factor criterion is easily satisfied.
Different roller groups can be prevented by arranging the central holes 6-1 and 7-1 and the identification marks 7-2 on the end surfaces of the rollers.
Contact angles theta of two rowsA、θBNot only the difference is made to be 15 ° or more, but also the above-described conditions are satisfied:
a contact angle theta of the load line A is more than or equal to 25 degreesA≤35°
Contact angle theta of non-load side row B of 5 DEG or moreB≤15°，
Therefore, under the use condition where the axial load acts in one direction, the effect of equalizing the loads in two rows and the like can be obtained as compared with the symmetrical design. Contact angle theta of load line AAAt 25 DEG or more and at a contact angle of the non-load side row of 15 DEG or less, the operating points P of the two rows on the bearing center axis O of the two rows A, BA、PBThe distance M between the two rows of tapered roller bearings is about 50-75% of that of the bilaterally symmetrical double-row tapered roller bearing. Therefore, the load ratio of the radial load in the non-load side row B is higher than that in the double row tapered roller bearing designed to be bilaterally symmetrical. In this way, the load ratio of the radial load in the non-load side row B becomes high, and under the use condition that the axial load acts in a direction biased, the load in two rows can be equalized as compared with the symmetrical design.
Contact angle theta of load line AAIf the angle exceeds 35 °, the load capacity of the radial load of the load train a is reduced, and therefore this method is not preferable. This is achieved byIn addition, the contact angle θ of the unloaded side column BBLess than 5 °, the axial load is not sufficiently loaded in the case where the axial load acts in the opposite direction.
In addition, in order to pass the contact angle thetaA、θBThe pitch circle diameters PCD of the two rows are preferably set to suppress the difference in height between the two sides of the center flange 11 in the two rows A, BA、PCDBRatio of (PCD)A/PCDB) The amount was determined to be quantitative.
In the present embodiment, as described above, the ratio of the pitch circle diameters of the rollers (PCD) in two rows A, BA/PCDB) Is less than or equal to 0.9 (PCD)A/PCDB)≤1.1。
Therefore, it is possible to suppress the difference in height between both sides of the flange 11 from becoming excessively large between the two rows A, B.
As for the thickness TH of the center flange 11, as described above, it is preferable that:
TH is less than or equal to 0.15 multiplied by the width W of the inner ring.
When the center flange 11 is subjected to an axial load, a certain thickness TH is required to suppress the axial movement of the rollers 6 and 7, but if the thickness TH of the center flange 6 or 7 is increased beyond the range of 0.15 × the inner ring width W, the track surface width and the roller length are unnecessarily reduced by the center flange 11.
< calculation results >
Table 1 shows the safety factor and the basic rated life of each design of the same size by comparison. In the tables, asymmetric designs (1) and (2) represent the products of the embodiments of fig. 1 and 2, and asymmetric design (3) represents the contact angle θ between the two rows A, BA、θBComparative example with a difference of less than 15 °. Regarding the roller length, roller diameter, and safety factor of each row, the values of symmetrically designed products (existing products having the same contact angle in two rows) are determined by the roller length L and the roller diameter D, respectivelywSafety ratios S0A and S0B are expressed by multiplying values of conventional products in the asymmetric designs (1) and (2). Regarding the basic rated life, the value of the A row (axial load row) of the symmetrically designed product is represented by LA, and the basic rated life of each row in each designThe lifetime and the total lifetime are expressed by the LA rate. As is clear from the results shown in table 1, in the asymmetric designs (1) and (2) to be the product of the embodiment, the basic rated life of the symmetric product was about 2 times as long, and the safety factor was also about the same as that of the symmetric product.
Fig. 4A to 4C and fig. 5A to 5C show rolling element load distributions of the entire circumference of the bearing under fatigue load in the axial load row a and the axial non-load side row B, respectively. In the symmetrical product, the diameter of the rolling element load distribution curve (fig. 4A) in the axial load row a is significantly larger than that in the axial non-load side row B (fig. 5A). In contrast, in the product according to the embodiment (asymmetric product), the rolling element load distribution curves in the axial load row a (fig. 4B and 4C) and the rolling element load distribution curves in the axial non-load side row B (fig. 5B and 5C) do not have a large difference in diameter, and it is found that the rolling element load amounts in the two rows A, B are balanced.
In the product according to the embodiment (asymmetric product), the rolling element load distribution curve (fig. 5B and 5C) in the axially non-load side row B is slightly larger than the rolling element load distribution curve (fig. 5A) in the axially load row a, but the diameter of the rolling element load distribution curve (fig. 4A) in the axially load row a of the symmetric product is significantly larger, so that the rolling element load distribution curve of the product according to the embodiment (asymmetric product) becomes smaller as the whole of the two rows A, B.
[ Table 1]
Figure BDA0003565247810000101
Figure BDA0003565247810000102
< other embodiment >
Fig. 6 shows another embodiment of the present invention. This embodiment is the same as embodiment 1 described with reference to fig. 1 to 5, except for the matters described specifically. In embodiment 1, the inner ring 2 is formed of a single member having double rows of raceway surfaces 4 and 4, but in the embodiment of fig. 6, the inner ring 2 is formed of two single rows of inner rings 2A and 2B formed separately. Accordingly, the middle flange 11 is composed of two single-row middle flanges 11A and 11B. The outer ring 3 is composed of two single-row outer rings 3A and 3B, as in embodiment 1. As described above, the double row tapered roller bearing 1 of the present embodiment is constituted by two single row tapered roller bearings 1A and 1B. In this figure, the same retainers as the retainers 8 and 9 of fig. 1 are provided, but illustration of these retainers is omitted. Even in such a configuration, the respective operations and effects described in embodiment 1 can be obtained.
< example of combination with cylindrical bearing >
Fig. 7 shows an example of a bearing device in which the double row tapered roller bearing 1 and the cylindrical roller bearing 15 are combined. The bearing device is applied to supporting a main shaft of a wind turbine or various industrial machines. The front and rear portions of the main shaft 16 are supported by a housing 17 via a double row tapered roller bearing 1 and a cylindrical roller bearing 15. The double row tapered roller bearing 1 of the embodiment shown in fig. 6 is used, but the double row tapered roller bearing 1 of the 1 st embodiment shown in fig. 1 may be used. The cylindrical roller bearing 15 has an inner ring 18, an outer ring 19, cylindrical rollers 20, and a cage (not shown in the drawings). The housing 17 is formed of a single cylindrical member in this example, but the double row tapered roller bearing 1 and the cylindrical roller bearing 15 that support the shaft 1 may be provided in separate housings (not shown in the figure).
< wind turbine Generator >
Fig. 8 shows an example of a wind turbine using the double row tapered roller bearing 1 according to the embodiment of the present invention. A housing 23a of the nacelle 23 is horizontally rotatably provided on the support base 21 via a rotary bearing 22. A main shaft 26 is rotatably provided in a housing 23a of the nacelle 23 via a bearing 25 for a main shaft of the wind turbine generator provided in a bearing housing 24, and a blade 27 serving as a rotary blade is attached to a portion of the main shaft 26 protruding outward from the housing 23 a. The other end of the main shaft 26 is connected to a speed-increasing gear 28, and an output shaft of the speed-increasing gear 28 is coupled to a rotor shaft of a generator 29. In the illustrated example, two wind turbine main shaft bearings 25 are provided, but one may be provided.
The double row tapered roller bearing 1 according to embodiment 1 of fig. 1 and 2 or embodiment 2 shown in fig. 6 is used as the bearing 25 for the main shaft of each wind turbine generator. The above-described double row tapered roller bearing 1 of the two bearings 25, 25 may be used as any bearing.
While the embodiments for carrying out the present invention have been described above based on the embodiments, the embodiments disclosed herein are illustrative in all respects and are not intended to be limiting. The scope of the present invention is defined not by the above description but by the appended claims, and all changes that come within the meaning and range of equivalency of the claims are intended to be embraced therein.
Description of reference numerals:
reference numeral 1 denotes a double-row tapered roller bearing;
reference numerals 1A, 1B denote single-row tapered roller bearings;
reference numeral 2 denotes an inner ring;
reference numerals 2A, 2B denote single-row inner rings;
reference numeral 3 denotes an outer ring;
reference numerals 3A, 3B denote single-row outer rings;
reference numeral 3C denotes an outer-ring spacer;
reference numerals 4 and 5 denote track surfaces;
reference numerals 6, 7 denote rollers;
reference numerals 6-1 and 7-1 denote roller end face center holes;
reference numeral 7-2 a roller end face identification mark;
reference numerals 8, 9 denote holders;
reference numeral 11 denotes a middle flange;
reference numerals 11A, 11B denote flanges in a single row;
reference numeral 12 denotes an end flange;
reference numeral 15 denotes a cylindrical roller bearing;
reference numeral 16 denotes a main shaft;
reference numeral 17 denotes a housing;
reference numeral 18 denotes an inner ring;
reference numeral 19 denotes an outer ring;
reference numeral 20 denotes a roller;
reference numeral 21 denotes a support table;
reference numeral 22 denotes a slewing bearing;
reference numeral 23 denotes a nacelle;
reference numeral 23a denotes a housing;
reference numeral 24 denotes a bearing housing;
reference numeral 25 denotes a main shaft support bearing;
reference numeral 26 denotes a main shaft;
reference numeral 27 denotes a blade;
reference numeral 28 denotes a speed increaser;
reference numeral 29 denotes a generator;
symbol a represents an axial load train;
symbol B represents an axial load non-load side row;
symbol thetaA、θBRepresents the contact angle;
symbol DA、DBRepresents the roller diameter;
symbol LB、LBRepresenting the roller length;
symbolic PCDA、PCDBRepresents the pitch circle diameter;
symbols HA, HB denote the height of the middle flange;
the symbols CA, CB indicate the height of the contact point of the flange with the roller in the middle.

Claims (6)

1. A double row tapered roller bearing in a face-to-face combination, wherein a contact angle of a load row as a row on the side mainly receiving an axial load is larger than a contact angle of a non-load side row as a row on the opposite side, and a difference between the contact angles of the two rows is 15 DEG or more.
2. The double row tapered roller bearing according to claim 1, wherein either one or both of a roller length and a roller diameter of the rollers in the non-load side row are larger than those of the rollers in the load side row.
3. The double row tapered roller bearing according to claim 1 or 2,
the contact angle of the load line is more than or equal to 25 degrees and less than or equal to 35 degrees;
the contact angle of the non-load side row is more than or equal to 5 degrees and less than or equal to 15 degrees.
4. The double row tapered roller bearing of any one of claims 1 to 3, wherein the ratio of the roller Pitch Circle Diameters (PCD) of the two rowsA/PCDB) Satisfies the following conditions:
0.9≤(PCDA/PCDB)≤1.1。
5. the double row tapered roller bearing according to any one of claims 1 to 4, wherein the inner ring has a center flange between raceway surfaces of two rows, the center flange having a thickness TH satisfying:
TH is less than or equal to 0.15 multiplied by the width of the inner ring.
6. A bearing for a main shaft of a wind turbine generator, wherein the bearing for a main shaft of a wind turbine generator is the double-row tapered roller bearing according to any one of claims 1 to 5.
CN202080067729.4A 2019-09-26 2020-09-24 Double-row tapered roller bearing Pending CN114514382A (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2019-175909 2019-09-26
JP2019175909 2019-09-26
JP2020-092067 2020-05-27
JP2020092067A JP7456851B2 (en) 2019-09-26 2020-05-27 Double row tapered roller bearing
PCT/JP2020/036072 WO2021060389A1 (en) 2019-09-26 2020-09-24 Double row tapered roller bearing

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CN114514382A true CN114514382A (en) 2022-05-17

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WO (1) WO2021060389A1 (en)

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CN113883022B (en) * 2021-10-29 2023-06-16 新疆金风科技股份有限公司 Shafting of wind generating set and wind generating set
CN113969876B (en) * 2021-10-29 2023-07-04 新疆金风科技股份有限公司 Wind generating set shafting and wind generating set

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DE102004047881A1 (en) * 2004-10-01 2006-04-06 Fag Kugelfischer Ag & Co. Ohg Self-aligning roller bearing for use in applications where axial loading is predominantly on one side has two rows of rollers which are inclined to vertical in opposite directions, angle being greater on side with higher loading
CN104968974A (en) * 2013-02-25 2015-10-07 爱信艾达株式会社 Dynamic force transmission device
DE102015204970A1 (en) * 2015-03-19 2016-09-22 Schaeffler Technologies AG & Co. KG Rolling, for example, a wind turbine
WO2017164325A1 (en) * 2016-03-24 2017-09-28 Ntn株式会社 Double-row spherical roller bearing
DE102016223543A1 (en) * 2016-11-28 2018-05-30 Schaeffler Technologies AG & Co. KG Wind turbine shaft arrangement

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