NZ615999B2 - Large rolling bearing - Google Patents
Large rolling bearing Download PDFInfo
- Publication number
- NZ615999B2 NZ615999B2 NZ615999A NZ61599912A NZ615999B2 NZ 615999 B2 NZ615999 B2 NZ 615999B2 NZ 615999 A NZ615999 A NZ 615999A NZ 61599912 A NZ61599912 A NZ 61599912A NZ 615999 B2 NZ615999 B2 NZ 615999B2
- Authority
- NZ
- New Zealand
- Prior art keywords
- ball
- rolling bearing
- raceway
- ball row
- shoulder
- Prior art date
Links
- 238000005096 rolling process Methods 0.000 title claims abstract description 66
- 210000002832 Shoulder Anatomy 0.000 claims description 116
- CWFOCCVIPCEQCK-UHFFFAOYSA-N Chlorfenapyr Chemical compound BrC1=C(C(F)(F)F)N(COCC)C(C=2C=CC(Cl)=CC=2)=C1C#N CWFOCCVIPCEQCK-UHFFFAOYSA-N 0.000 claims description 6
- 238000009434 installation Methods 0.000 claims description 6
- 238000011068 load Methods 0.000 description 22
- 230000000875 corresponding Effects 0.000 description 13
- 238000006073 displacement reaction Methods 0.000 description 5
- 230000000284 resting Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 1
- 230000001050 lubricating Effects 0.000 description 1
- 238000009420 retrofitting Methods 0.000 description 1
- 230000002441 reversible Effects 0.000 description 1
Classifications
-
- 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
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/08—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with two or more rows of balls
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
- F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
-
- 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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/10—Application independent of particular apparatuses related to size
- F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
-
- 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
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
-
- 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
- F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
-
- 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
large rolling bearing which is in the form of a multi-row ball-type revolute joint for absorbing axial loads, radial loads and tilting moments is disclosed. The large rolling bearing (1) has an outer ring (5), an inner ring (3), a first ball row (K1) and a second ball row (K2). The first ball row and the second ball row are arranged, so as to be spaced apart from one another axially, in each case in a four-point bearing configuration, wherein the first ball row is assigned four raceway portions (7, 9, 15, 17) and the second ball row is assigned four raceway portions (11, 13, 19, 21) which each have a surface for receiving the ball raceway. The invention relates in particular to a large rolling bearing in which the surface area of in each case one raceway portion provided in the inner ring (7, 11) is larger than the surface area of the respectively adjacent raceway portion provided in the inner ring (9, 13) and is equal to the surface area of the respectively diametrically opposite raceway portion provided in the outer ring (17, 21). and the second ball row are arranged, so as to be spaced apart from one another axially, in each case in a four-point bearing configuration, wherein the first ball row is assigned four raceway portions (7, 9, 15, 17) and the second ball row is assigned four raceway portions (11, 13, 19, 21) which each have a surface for receiving the ball raceway. The invention relates in particular to a large rolling bearing in which the surface area of in each case one raceway portion provided in the inner ring (7, 11) is larger than the surface area of the respectively adjacent raceway portion provided in the inner ring (9, 13) and is equal to the surface area of the respectively diametrically opposite raceway portion provided in the outer ring (17, 21).
Description
Large rolling bearing
The present invention concerns a large-size rolling bearing which is in
the form of a multi-row ball-bearing rotary joint for carrying axial loads, radial
loads and tilting moments, comprising an outer race, an inner race, a first ball
row and a second ball row, wherein the first ball row and the second ball row
are respectively arranged in axially mutually spaced relationship in a four-point
bearing configuration, wherein associated with the first ball row are four
raceway portions and associated with the second ball row are four raceway
portions which respectively have a surface for receiving the ball raceway.
Large-size rolling bearings are used in machine and plant production for
providing a rotary connection in relation to high loads. The term large-size
rolling bearings is used in particular in relation to running circle diameters of
300 mm and larger. Depending on the respective installation condition and in
dependence on the forces to be carried the running circle diameters of the
large-size rolling bearings are certainly also several 1000 mm. In the case of
bearings of that order of magnitude the large-size rolling bearings themselves
are of a considerable inherent weight and require considerable fitment
complication and expenditure. With that background in mind the aim is to use
integrated bearings which have a single unit which can be fitted in place and
which are adapted to carry axial forces, radial forces and possibly tilting
moments. For that reason rolling bearings of a multi-row structural
configuration are primarily used, if there is a requirement to carry axial forces,
radial forces and tilting moments. Inter alia the use of multi-row four-point
bearings is known.
In terms of selecting the correct bearing designers are faced with the
conflicting aims of providing a bearing enjoying the highest possible load-
bearing capability while involving a very small installation space and with the
lowest possible complication and expenditure in fitment thereof. In situations
where, due to the structure involved, it is necessary to observe a
predetermined limited structural space, or in (rare) cases involving retro-
fitment of large-size rolling bearings in an existing environment with the aim of
retro-fitting a bearing enjoying a higher load-bearing capability (in comparison
with the one which was previously fitted there), there is the problem that
higher stability with known bearing types is not readily achieved without
affording a larger structural space in the axial or radial direction, that being
linked to a high constructional burden.
As state of the art attention is directed at this point generally to the
following documents: DE 10 2008 049 813 A1, DE 10 2004 023 774 A1, DE 10
2004 051 054 A1, DD 46 126 A5, DE 18 55 303 U and DE 10 2006 031 956
With that background in mind the object of the present invention is to
provide a large-size rolling bearing of the kind set forth in the opening part of
this specification, with improved load-bearing capability and with the smallest
possible installation dimensions.
In a large-size rolling bearing of the kind set forth in the opening part of
this specification the invention attains that object in that the surface of a
respective raceway portion provided in the inner race is larger than the surface
of the respectively adjacent raceway portion provided in the inner race and
equal to the surface of the respectively diametrally oppositely disposed
raceway portion provided in the outer race. The invention is based on the
realisation that the ball row of a four-point bearing has in total four contact
points with respectively separate surface portions in the inner and outer races.
Those contact points are not constantly at the same location – in relation to
the cross-section of the bearing – but alter in dependence on the load
situation. That also applies for the situation involving load reversal. The
greater the force acting on the bearing in the axial direction, the
correspondingly greater is the contact point displaced in the loaded raceway
portions in the direction of the bearing gap between the inner race and the
outer race. That is due to the fact that the balls and raceway surfaces, as a
result of the axial force occurring, are exposed to a deformation and
respectively make surface contact with the raceway portion. To be able to
achieve a certain running tolerance, in the case of four-point bearings the
radius of curvature of the balls is slightly less than the radius of curvature of
the corresponding raceway portions (in cross-section). That means that, when
high axial forces occur, the inner race and the outer race experience a force
acting thereon, which urges them apart, whereby the contact region between
the respective balls and the corresponding loaded raceway surface can move.
According to the invention in particular those surfaces of the raceway portions,
which are loaded more heavily upon a preferential loading on the large-size
rolling bearing, are increased in size. Irrespective of whether the load is a load
resting thereon or a lifting load, the bearing is to be so designed in accordance
with the invention that the respective surfaces of the raceway portions, that
are more heavily loaded in the preferential direction, are increased in size.
As each raceway portion in the bearing is finite, upon the attainment of
a critical axial load is point is reached at which the contact region between the
ball and the raceway surface (in the sense of: surface available for the
raceway) travels to the edge of the raceway surface or therebeyond. As a
consequence of that, both the balls and also the edges of the raceway portions
are exposed to severe wear.
Based on those realisations, the invention makes use of the fact that, in
the design of the bearing arrangement, the direction – considered axially – in
which the load on the bearing will be greater is already known. The bearing
can therefore be specifically adapted to carry higher loadings from one axial
direction than from the other. Because two diagonally opposite raceway
portions are always loaded more greatly than the respective other oppositely
disposed raceway portions by virtue of the axial load, the invention makes use
of knowledge of the displacement of the contact region within the raceway
surfaces, insofar as the surfaces which are expected to be loaded more greatly
are increased in size in comparison with the surfaces which are expected to be
loaded to a lesser extent. The additional structural space which is required as
a consequence of an increase in size of a surface can be compensated in that
way in that the respectively corresponding surface which is subjected to a
lesser load is reduced in accordance with the increase in size of the one
surface.
An advance development of the invention provides that the surface of
the raceway portion provided in the inner race is equal to the surface of the
respectively diametrally opposite raceway portion provided in the outer race.
Further preferably the respectively larger surfaces of the raceway
portions are of equal size. In the present case surfaces of equal size means
that, having regard to tolerances resulting from production engineering, the
length of a raceway surface should not alter in cross-section by more than +/-
When hereinbefore or hereinafter reference is made to
surfaces, that generally means the cross-sectional surface area and not the
actual peripherally extending surface.
In a preferred embodiment of the invention the inner race for the first
ball row has an annular first inner shoulder and an annular second inner
shoulder which respectively delimit one of the surfaces for receiving a ball
raceway of the first ball row. In addition the inner race for the second ball row
has an annular third inner shoulder and an annular fourth inner shoulder which
respectively delimit one of the surfaces for receiving the ball raceway of the
second ball row, wherein a maximum diameter of the fourth inner shoulder is
different from a maximum diameter of the first inner shoulder. The increase in
diameter of the inner shoulders in the aforementioned manner permits an
increase in surface area in a fashion which can be calculated and predicted in
geometrically simple fashion, without the geometry of the bearing overall
having to be completely re-designed.
In a preferred embodiment the maximum diameter of the third inner
shoulder is different from the maximum diameter of the second inner shoulder.
Preferably the outer race for the first ball row has a first annular outer
shoulder and a second annular outer shoulder which respectively delimit one of
the surfaces for receiving the ball raceways of the first ball row. The outer race
for the second ball row also has a third annular outer shoulder and a fourth
annular outer shoulder which respectively delimit one of the surfaces for
receiving the ball raceways of the second ball row, wherein the minimum
diameter of the fourth outer shoulder is different from the minimum diameter
of the first outer shoulder. The outer race and the raceway portions provided
in the outer race are preferably of a configuration corresponding to the
respective portions of the inner race in order to compensate equally for a
symmetrically occurring displacement of the contact region between the balls
and the surfaces of the raceway portions both in the inner race and also in the
outer race.
Preferably the minimum diameter of the third outer shoulder is different
from the minimum diameter of the second outer shoulder.
In another particularly preferred embodiment of the invention the
largest of the maximum diameters of the inner shoulders is smaller than or
equal to the smallest of the minimum diameters of the outer shoulders.
That embodiment has the additional advantage that, in spite of an increase in
size according to the invention of the surfaces of the raceway portions, that are
to be expected to be loaded more heavily, the inner race can still be passed
completely through the outer race, whereby assembly and dismantling of the
bearing is considerably simplified.
In a preferred embodiment the balls of the first ball row are arranged
together with the balls of the second ball row along a first running circle
diameter.
Preferably the largest of the maximum diameters of the inner shoulders
and/or the smallest of the minimum diameters of the outer shoulders is equal
to or in a range of up to 0.5 mm below the first running circle diameter of the
first and second ball rows.
Further preferably the smallest of the minimum diameters of the outer
shoulders is equal to or in a range of up to 0.5 mm above the first running
circle diameter of the first and second ball rows.
In an advantageous development of this embodiment the maximum
diameter of the first inner shoulder is equal to the maximum diameter of the
third inner shoulder and larger than the maximum diameter respectively of the
second and fourth inner shoulders.
Further preferably the minimum diameter of the second outer shoulder
is equal to the minimum diameter of the fourth outer shoulder and smaller
than the minimum diameter respectively of the first and third outer shoulders.
In an alternative embodiment the balls of the first ball row are arranged
along the first running circle diameter and the balls of the second ball row are
arranged along a second running circle diameter which is different from the
diameter of the first ball row. That gives the advantage that the possible
pressure angle, that is to say the possible displacement of the contact points in
the direction of the gap between the inner and outer races of the bearing, can
be altered to a substantially greater degree than would be the case if the balls
of all rows were arranged on the same running circle diameter. The extent of
the increase occurs in dependence on the size of the displacement between the
first running circle diameter and the second running circle diameter.
In this alternative embodiment preferably the maximum diameter of
the first inner shoulder is larger than the maximum diameter of the second
inner shoulder and the maximum diameter of the third inner shoulder is larger
than the maximum diameter of the fourth inner shoulder.
Further preferably the minimum diameter of the fourth outer shoulder is
smaller than the minimum diameter of the third outer shoulder and the
minimum diameter of the second outer shoulder is smaller than the minimum
diameter of the first outer shoulder.
In a further preferred embodiment the first ball row comprises balls of a
first ball diameter and the second ball row comprises balls of a second ball
diameter different from the first ball diameter.
In a further preferred embodiment the large-size rolling bearing has one
or more further ball rows. The one or more further ball rows are preferably of
a configuration corresponding to the first ball row and/or the second ball row in
accordance with the above-described preferred embodiments. That concerns
in particular the configuration of oppositely disposed shoulders, raceway
portions, ball diameters and/or running circle diameters. In a particularly
preferred embodiment the large-size rolling bearing has a third ball row.
The invention further concerns a wind power installation comprising a
pylon having a pylon head, and a pod adapted to receive a rotor, wherein the
pod is mounted rotatably relative to the pylon by means of an azimuth bearing.
According to the invention the aforementioned wind power installation is
improved in that the azimuth bearing is in the form of a large-size rolling
bearing according to one of the above-described preferred embodiments.
The invention is described in greater detail hereinafter by means of two
preferred embodiments by way of example and with reference to the
accompanying Figures in which:
Figure 1 shows a detail view of a large-size rolling bearing according to a
first embodiment of the invention,
Figure 2 shows a detail view of a large-size rolling bearing according to a
second embodiment of the invention,
Figure 3 shows a large-size rolling bearing from the state of the art in a
first condition,
Figure 4 shows the large-size rolling bearing of Figure 3 in a second
condition,
Figure 5 shows a detail view of the large-size rolling bearing of the first
embodiment in a first condition, similarly to Figure 3, and
Figure 6 shows a detail view of the large-size rolling bearing of the first
embodiment of the invention in a second condition, similarly to Figure 4.
The Figures described in greater detail hereinafter illustrate the
invention on the basis of a load situation by way of example. That load
situation represents a load resting on the bearing, which acts from above on
the inner race of the respectively illustrated bearing in a direction which is
vertical – in relation to Figures 1 to 6. It will be apparent that the
corresponding configuration and numbering of the shoulders and ball rows can
be reversed in dependence on the load situation having regard to the
orientation of the bearings in the Figures, to illustrate a respectively different
load situation.
Figure 1 shows a cross-sectional view in detail through a large-size
rolling bearing according to the invention in accordance with a first
embodiment of the invention. The large-size rolling bearing 1 has an inner
race 3 and outer race 5. The large-size rolling bearing 1 shown in Figure 1 is a
two-row large-size rolling bearing having a first ball row K1 and a second ball
row K2. The second ball row K2 is axially spaced from the first ball row K1.
The first ball row K1 includes a multiplicity of balls 22 arranged along a running
circle diameter DL1. The second ball row K2 includes a multiplicity of balls 24
arranged along a second running circle diameter DL2.
The inner race 3 has a first raceway portion 7 and a second raceway
portion 9 which are associated with the first ball row K1. In addition the inner
race 3 has a third raceway portion 11 and a fourth raceway portion 13 which
are associated with the second ball row K2. The first raceway portion 7 and
the second raceway portion 9 are arranged in mutually adjacent relationship
and separated from each other by a peripherally extending annular groove.
The first raceway portion 7 is delimited by an annular first inner shoulder 23.
The second raceway portion 9 is delimited by an annular second inner shoulder
. The first inner shoulder 23 is of a maximum diameter d1. The second
inner shoulder 25 is of a second maximum diameter d2. In this case the
maximum diameter d1 of the first inner shoulder 23 is greater than the
maximum diameter d2 of the second inner shoulder 25.
The third raceway portion 11 and the fourth raceway portion 13 are
arranged adjacent to each other in the inner race 3 and separated from each
other by a peripherally extending annular groove. The third raceway portion
11 is delimited by an annular third inner shoulder 27. The fourth raceway
portion 13 is delimited by an annular fourth inner shoulder 29. The third inner
shoulder 27 is of a maximum diameter d3. In the Figure 1 embodiment the
maximum diameter d3 of the third inner shoulder 27 corresponds to the
maximum diameter d2 of the second inner shoulder 25. The fourth inner
shoulder 29 is of a maximum diameter d4. In the Figure 1 embodiment the
maximum diameter d3 of the third inner shoulder 27 is larger than the
maximum diameter d4 of the fourth inner shoulder 29.
Provided in the outer race 5 are outer shoulders which correspond to the
inner shoulders of the inner race 3 and which respectively delimit a raceway
portion also provided in the outer race 5. The outer race 5 has in particular a
first raceway portion 15 and a second raceway portion 17 which are associated
with the first ball row K1. In addition the outer race 5 has a third raceway
portion 19 and a fourth raceway portion 21 which are associated with the
second ball row K2. The first raceway portion 15 in the outer race 5 is of a
configuration corresponding to the second raceway portion 9 of the inner race
3, that is diametrally opposite – with respect to the balls 22. The second
raceway portion 17 in the outer race 5 is of a configuration corresponding to
the first raceway portion 7 of the inner race 3, that is diametrally opposite –
with respect to the balls 22.
The third raceway portion 19 in the outer race 5 is of a configuration
corresponding to the fourth raceway portion 13 of the inner race 3 – with
respect to the balls 24. The fourth raceway portion 21 in the outer race 5 is of
a configuration corresponding to the third raceway portion 11 of the inner race
3, that is diametrally opposite – with respect to the balls 24.
The first raceway portion 15 is delimited by a first annular outer
shoulder 31 which is of a minimum diameter D1. The second raceway portion
17 is delimited by a second annular outer shoulder 33 which is of a minimum
diameter D2. The third raceway portion 19 is delimited by a third annular
outer shoulder 35 which is of a minimum diameter D3. The fourth
raceway portion 21 is delimited by a fourth annular outer shoulder 37 which is
of a minimum diameter D4.
The balls 22 of the first ball row K1 are arranged along a first running
circle diameter DL1. The balls 24 of the second ball row K2 are arranged along
a second running circle diameter DL2. As shown in Figure 1 DL1 is larger than
DL2.
The surface of the first raceway portion 7 of the inner race 3 is increased
in size by the diameter d1 of the first inner shoulder 23 being larger than the
diameter d2 of the second inner shoulder 25.
As shown in Figure 1 d1 is also larger than DL1. The surface of the
second raceway portion 17 of the outer race is increased in size in a manner
corresponding to the surface of the first raceway portion 7 of the inner race 3
by the diameter D2 being less than the diameter D1 of the first outer shoulder
31. The diameter D2 of the second outer shoulder 33 is smaller than the first
running circle diameter DL1 by the same amount as the diameter d1 of the
first inner shoulder 23 is larger than DL1.
The raceway portions of the second ball row K2 are also of a
configuration similar to the first ball row K1. The third raceway portion 11 has
an enlarged surface which is precisely as large as the surface of the fourth
raceway portion 21 of the outer race 5. The diameter d3 of the third inner
shoulder 27 is larger than the running circle diameter DL2 of the second ball
row K2 by the same amount as the diameter D4 of the fourth outer shoulder
37 of the fourth raceway portion 21 of the outer race 5 is smaller than the
second running circle diameter DL2. The raceway portions 13 and 19 of the
inner race 3 and the outer race 5 respectively, which are in diametrally
opposite relationship with respect to the balls 24, are reduced in size in the
same manner relative to the raceway portions 11 and 21 as was already
described hereinbefore in relation to the first ball row K1 and the raceway
portions 9 and 15.
Figure 2 shows a large-size rolling bearing 1 of the present invention in
accordance with a second embodiment. The large-size rolling bearing 1 in
Figure 2 is similar in structure to the large-size rolling bearing 1 in Figure 1 in
regard to the arrangement of the first ball row K1 and the second ball row K2.
In regard to the inner shoulders, the raceway portions delimited thereby,
the outer shoulders and the raceway portions delimited thereby, attention is
directed in this respect to the description relating to Figure 1, insofar as
identical references have been allocated.
It will be noted however that the embodiments of Figures 1 and 2 differ
in regard to the dimensioning of the shoulders. The inner race 3 of Figure 2 is
in particular of the configuration as follows:
The first inner shoulder 23 of the inner race 3 is of a maximum diameter
d1 equal to the running circle diameter DL1 of the first ball row K1. In contrast
the minimum diameter D1 of the first outer shoulder 31 of the outer race 5 is
larger than the running circle diameter DL1 of the first ball row K1. The
second inner shoulder 25 of the inner race 3 is of a maximum diameter d2
which is smaller than the running circle diameter DL1 of the first ball row K1.
The corresponding minimum diameter D2 in the outer race 5 of the second
outer shoulder 33 is of a minimum diameter D2 which is equal to the running
circle diameter DL1 of the first ball row K1.
The maximum diameter d3 of the third inner shoulder 27 in the inner
race 3 is equal to the maximum diameter d1 of the first inner shoulder 23 of
the first ball row K1. In the Figure 2 embodiment the running circle diameter
DL1 of the first ball row K1 also corresponds to the running circle diameter of
the second ball row K2. Unlike Figure 1 therefore the two ball rows K1 and K2
are arranged on an identical running circle diameter DL1 and are axially spaced
relative to each other. The minimum diameter D3 of the third outer shoulder
in the outer race 5 is in turn larger than the running circle diameter DL1.
D3 is equal to D1.
The maximum diameter d4 of the fourth inner shoulder 29 of the inner
race 3 is equal to the diameter d2 of the second inner shoulder 25. The
corresponding minimum diameter D4 of the fourth outer shoulder 37 of the
outer race 5 is equal to the minimum diameter D2 of the second outer shoulder
33.
In the Figure 2 embodiment the running circle diameter DL1 serves as a
reference value. Provided between the outer race and the inner race is a
respective gap which varies by the same amount in the direction of the outer
race or inner race, whereby raceway portions which are uniformly increased
and reduced in size and which are in mutually diametrally opposite
relationship (with respect to the respective ball row K1, K2) are afforded. At
the same time, after removal of the balls 22, 24 or prior to introduction of the
balls 22, 24, the inner race 3 can be fitted completely through the outer race 5
because there is no overlap.
The mode of operation of a large-size rolling bearing 1 according to the
invention is now to be illustrated with reference to Figures 3 to 6, in
comparison with a large-size rolling bearing 101 from the state of the art.
Figures 3 and 4 firstly show a large-size rolling bearing 101 from the state of
the art. The large-size rolling bearing 101 has an inner race 103 and an outer
race 105. Two ball rows K11 and K12 are arranged between the inner race
103 and the outer race 105. The large-size rolling bearing 101 from the state
of the art is a two-row four-point bearing. The balls of the first ball row K11
have two respective contact points with the inner race 103 and the outer race
105. The contact points are respectively arranged in a separate raceway
portion 107, 109, 115 and 117. A pressure angle 1 is formed relative to a
radial axis. The same applies to the second ball row K12 as to the first ball
row K11, in relation to the raceway portions 111, 113, 119 and 121. The
surfaces of the raceway portions 107, 109, 111, 113, 115, 117, 119 and 121
are respectively of substantially equal size.
Figure 4 shows the bearing of Figure 3 when a high axial load resting
thereon is applied by way of the inner race and acts on the bearing. The inner
race 103 is urged downwardly in relation to the outer race 105. The inner race
103 and the outer race 105 are driven away from each other, which is shown
on an exaggerated scale in Figure 4, by virtue of the balls of the first ball row
K11 and the second ball row K12 engaging against the surfaces of the raceway
portions. As a consequence of that relative movement between the inner race
and the outer race and additional deformation of the balls 122, 124, there is an
increase in the pressure angle which now assumes the value 2. By virtue of
the deformation of the balls and the raceway surfaces, the point contact of a
ball with the surface of the raceway portion, that is in contact with the ball, is
increased to afford a surface, this being indicated in relation to the second ball
row K12 by the ellipse 126. In the view shown in Figure 4 that deformation
region is in the region of an edge which delimits the raceway portion 121. The
same phenomenon is also seen by virtue of the symmetrical
configuration of the bearing in relation to the other, heavily loaded raceway
portions 111, 107 and 117. Severe wear occurs, both on the part of the balls
and also on the part of the raceway portions.
To distinguish from Figures 3 and 4, Figures 5 and 6 show the improved
function of the large-size rolling bearing according to the present invention.
The mode of operation shown in Figures 5 and 6 applies for both embodiments
of the present invention, but for the sake of simplicity reference is only made
to the first embodiment of the invention which has also already been described
and shown in Figure 1. Figure 5 shows the large-size rolling bearing of Figure
1 in a substantially unloaded condition. The contacting points of the balls 22,
24 of the first and second ball rows K1, K2 are oriented substantially at an
angle of 1 relative to the radial direction of the bearing with respect to the
centre point of the balls. In the condition shown in Figure 6 an axial load is
applying a load to the inner race and acts downwardly in the illustrated
orientation in Figure 6. By virtue of the engagement of the balls 22, 24 of the
first ball row K1 and the second ball row K2 against the surfaces of the
raceway portions the inner race 3 and the outer race 5 are urged away from
each other. Consequently the contact of the balls 22, 24 with the respective
raceway portions is displaced. A contact surface which is formed by virtue of
the deformation of the balls and the raceway surfaces, illustrated by the ellipse
26, is displaced in the direction of the inner shoulders 23, 27 of the inner race
3 and the outer shoulders 33, 37 of the outer race 5. The surface of the
raceway portions 9, 15 of the first ball row K1 and the surface of the raceway
portions 13, 19 of the second ball row K2 are substantially unloaded but at any
event are loaded markedly less heavily than the above-mentioned surfaces of
the raceway portions 7, 11, 17, 21. It will be noted however that the ellipse
26 is not disposed in the region of the annular shoulders 23, 33, 27, 37, by
virtue of the surface, that is increased in size according to the invention, of the
raceway portions 7, 17, 11 and 21, in spite of the heavy axial load.
Consequently no wear of the balls and/or raceway portions of the inner race 3
and outer race 5 occurs. In the case of a similar load situation and a similar
pressure angle displacement as in the case of bearings known from the state of
the art (see Figures 3 and 4), the bearing according to the invention still
does not attain a critical operating condition.
The present information relating to preferred embodiments and the
present specific description refer to two-row bearings. In addition however the
invention also concerns further multi-row embodiments of the large-size rolling
bearing according to the present invention. In particular the invention
concerns a three-row large-size rolling bearing which has a third ball row. The
third ball row is disposed between the inner race and the outer race in a four-
point bearing configuration, wherein the third ball row is axially spaced relative
to the first ball row and the second ball row, wherein associated with the third
ball row are four raceway portions which each have a surface for receiving the
ball raceway and wherein the surface of a respective raceway portion of the
third ball row, that is provided in the inner race, is larger than the surface of
the respectively adjacent raceway portion of the third ball row, that is provided
in the inner race, and is equal to the surface of the respectively diametrally
opposite raceway portion of the third ball row, that is provided in the outer
race.
Preferred embodiments which were described hereinbefore with
reference to two-row configurations of the large-size rolling bearing are also to
be transferred in a similar manner to the three-row configuration of the large-
size rolling bearing.
Preferred embodiments of the present invention are preferably adapted
to different sectors of use by means of further structural details. Thus the
large-size rolling bearings according to the invention can have for example an
internal tooth arrangement, an external tooth arrangement, or no tooth
arrangement at all. The large-size rolling bearings can have axially extending
fixing bores passing therethrough or other flange-like or radial fixing bores. In
addition the bearings according to the invention preferably have spacers
between the balls, or cages for holding the balls. In further preferred
embodiments the large-size rolling bearings according to the invention have
lubricating bores for introducing and expelling lubricants or for example
openings for introducing or removing the balls from the ball rows.
Claims (19)
1. A large-size rolling bearing which is in the form of a multi-row ball- bearing rotary joint for carrying axial loads, radial loads and tilting moments, comprising an outer race, an inner race, a first ball row (K1) and a second ball row (K2), wherein the first ball row (K1) and the second ball row (K2) are respectively arranged in axially mutually spaced relationship in a four-point bearing configuration, wherein associated with the first ball row are four raceway portions and associated with the second ball row are four raceway portions which respectively have a surface for receiving the ball raceway, characterised in that the surface of a respective raceway portion provided in the inner race is larger than the surface of the respectively adjacent raceway portion provided in the inner race and equal to the surface of the respectively diametrally oppositely disposed raceway portion provided in the outer race.
2. A large-size rolling bearing according to claim 1 characterised in that the surface of the raceway portion provided in the inner race is equal to the surface of the respectively diametrally opposite raceway portion provided in the outer race.
3. A large-size rolling bearing according to one of the preceding claims characterised in that the inner race for the first ball row (K1) has an annular first inner shoulder and an annular second inner shoulder which respectively delimit one of the surfaces for receiving the ball raceway of the first ball row (K1) and the inner race for the second ball row (K2) has an annular third inner shoulder and an annular fourth inner shoulder which respectively delimit one of the surfaces for receiving the ball raceway of the second ball row (K2), wherein a maximum diameter (d4) of the fourth inner shoulder is different from a maximum diameter (d1) of the first inner shoulder.
4. A large-size rolling bearing according to any one of the preceding claims characterised in that the maximum diameter (d3) of the third inner shoulder is different from the maximum diameter (d2) of the second inner shoulder.
5. A large-size rolling bearing according to any one of the preceding claims characterised in that the outer race for the first ball row (K1) has a first annular outer shoulder and a second annular outer shoulder which respectively delimit one of the surfaces for receiving the ball raceways of the first ball row (K1), and the outer race for the second ball row (K2) has a third annular outer shoulder and a fourth annular outer shoulder which respectively delimit one of the surfaces for receiving the ball raceways of the second ball row (K2), wherein the minimum diameter (D4) of the fourth outer shoulder is different from the minimum diameter (D1) of the first outer shoulder.
6. A large-size rolling bearing according to any one of the preceding claims characterised in that the minimum diameter (D3) of the third outer shoulder is different from the minimum diameter (D2) of the second outer shoulder.
7. A large-size rolling bearing according to any one of the preceding claims characterised in that the largest of the maximum diameters (d1, d2, d3, d4) of the inner shoulders is smaller than or equal to the smallest of the minimum diameters (D1, D2, D3, D4) of the outer shoulders.
8. A large-size rolling bearing according to any one of the preceding claims characterised in that the balls of the first ball row (K1) and the balls of the second ball row (K2) are arranged along a first running circle diameter (DL1).
9. A large-size rolling bearing according to claim 8 characterised in that the largest of the maximum diameters (d1, d2, d3, d4) of the inner shoulders is equal to or in a range of up to 0.5 mm below the first running circle diameter (DL1) of the first and second ball rows.
10. A large-size rolling bearing according to claim 8 or claim 9 characterised in that the smallest of the minimum diameters (D1, D2, D3, D4) of the outer shoulders is equal to or in a range of up to 0.5 mm above the first running circle diameter (DL1) of the first and second ball rows.
11. A large-size rolling bearing according to claim 9 or claim 10 characterised in that the maximum diameter (d1) of the first inner shoulder is equal to the maximum diameter (d3) of the third inner shoulder and larger than the maximum diameter (d2, d4) respectively of the second and fourth inner shoulders.
12. A large-size rolling bearing according to any one of the preceding claims characterised in that the minimum diameter (D2) of the second outer shoulder is equal to the minimum diameter (D4) of the fourth outer shoulder and smaller than the minimum diameter (D1, D3) respectively of the first and third outer shoulders.
13. A large-size rolling bearing according to any one of the preceding claims characterised in that the balls of the first ball row (K1) are arranged along the first running circle diameter (DL1) and the balls of the second ball row (K2) are arranged along a second running circle diameter (DL2) which is different from the diameter (DL1) of the first ball row (K1).
14. A large-size rolling bearing according to claim 13 characterised in that the maximum diameter (d1) of the first inner shoulder is larger than the maximum diameter (d2) of the second inner shoulder and the maximum diameter (d3) of the third inner shoulder is larger than the maximum diameter (d4) of the fourth inner shoulder.
15. A large-size rolling bearing according to claim 13 or claim 14 characterised in that the minimum diameter (D4) of the fourth outer shoulder is smaller than the minimum diameter (D3) of the third outer shoulder and the minimum diameter (D2) of the second outer shoulder is smaller than the minimum diameter (D1) of the first outer shoulder.
16. A large-size rolling bearing according to any one of the preceding claims characterised in that the first ball row (K1) comprises balls of a first ball diameter and the second ball row (K2) comprises balls of a second ball diameter different from the first ball diameter.
17. A large-size rolling bearing according to any one of the preceding claims characterised in that the large-size rolling bearing has one or more further ball rows, wherein the one or more ball rows are arranged in axially mutually spaced relationship respectively in a four-point bearing configuration, wherein respectively associated with a ball row are four raceway portions which respectively have a surface for receiving the ball raceway and wherein the respective surface of a raceway portion provided in the inner race is larger than the surface of the respectively adjacent raceway portion provided in the inner race and equal to the surface of the respectively diametrally opposite raceway portion provided in the outer race.
18. A wind power installation comprising a pylon having a pylon head, and a pod adapted to receive a rotor, wherein the pod is mounted rotatably relative to the pylon by means of an azimuth bearing, characterised in that the azimuth bearing is in the form of a large-size rolling bearing according to any one of claims 1 to 17.
19. A large-size rolling bearing substantially as hereinbefore described with reference to accompanying
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011076872.6 | 2011-06-01 | ||
DE102011076872A DE102011076872A1 (en) | 2011-06-01 | 2011-06-01 | slewing bearings |
PCT/EP2012/059342 WO2012163707A1 (en) | 2011-06-01 | 2012-05-21 | Large rolling bearing |
Publications (2)
Publication Number | Publication Date |
---|---|
NZ615999A NZ615999A (en) | 2015-01-30 |
NZ615999B2 true NZ615999B2 (en) | 2015-05-01 |
Family
ID=
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