KR101988706B1 - Angular ball bearing - Google Patents
Angular ball bearing Download PDFInfo
- Publication number
- KR101988706B1 KR101988706B1 KR1020167023382A KR20167023382A KR101988706B1 KR 101988706 B1 KR101988706 B1 KR 101988706B1 KR 1020167023382 A KR1020167023382 A KR 1020167023382A KR 20167023382 A KR20167023382 A KR 20167023382A KR 101988706 B1 KR101988706 B1 KR 101988706B1
- Authority
- KR
- South Korea
- Prior art keywords
- retainer
- ring
- outer ring
- ball
- diameter
- Prior art date
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Classifications
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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
- F16C33/38—Ball cages
- F16C33/41—Ball cages comb-shaped
- F16C33/418—Details of individual pockets, e.g. shape or ball retaining means
-
- 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
- F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
-
- 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
- F16C33/38—Ball cages
- F16C33/41—Ball cages comb-shaped
- F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
- F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
- F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
-
- 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
- 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
- F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the 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
- F16C19/02—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
- F16C19/16—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 a single row of balls
- F16C19/163—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 a single row 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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/46—Gap sizes or clearances
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The retainer 30 includes a ring portion 31 having a substantially annular shape and a plurality of columnar portions 32 projecting in the axial direction at predetermined intervals from the front surface side or the back surface side of the ring portion 31, And a plurality of pocket portions (33) formed between the pair of side walls (32). To the retainer 30, a reinforcement material is added. The pitch circle diameter of the balls 3 in the X, ΔRmax = X 2 × 5.0 × 10 -6 + a X × 1.8 × 10 -3 +0.14 and, ΔRmin = X 2 × 5.5 × 10 -6 + X × 1.5 × 10 -3 +0.02, the radial movement amount? R of the holder 30 is? Rmin?? R?? Rmax. DELTA t < DELTA R > where DELTA t is the relative expansion of the retainer 30 at 100 DEG C in the radial direction.
Description
The present invention relates to an angular ball bearing.
BACKGROUND ART A ball screw is used for a machine tool such as an NC lathe, a presser half, a machining center, a complex machining tool, a 5-axis machining tool, or the like and a linearly moving mechanism of a bed for mounting a main shaft or a workpiece. An angular ball bearing is employed as a bearing for rotationally supporting the shaft end of the ball screw (for example, see Patent Document 1).
The cutting load generated during machining or the inertia load when the main shaft and the bed are moved by rapid acceleration is loaded as an axial load to the angular ball bearing through the ball screw. In recent machine tools, an inertia load due to a cutting load or a rapid feed is large for the purpose of high-efficiency machining, and a large axial load tends to be loaded on an angular ball bearing.
Therefore, in such an angular ball bearing for ball screw support, it is necessary to increase both the load capacity in the axial direction and high rigidity for maintaining machining accuracy in order to increase the rolling fatigue life.
However, if the bearing size is increased, the space is increased at the ball screw shaft end, and if the number of combinations is large, the ball screw unit The portion becomes a wide configuration. As a result, the required floor area of the machine tool is increased and the dimension in the height direction is increased. Therefore, there is a limit to the increase in the size of the bearing and the increase in the number of heat.
SUMMARY OF THE INVENTION It is an object of the present invention to provide an angular ball bearing capable of achieving both increased load capacity in the axial direction and high rigidity in a limited space.
The above object of the present invention is achieved by the following constitution.
(1) an outer ring having an inner raceway surface,
An inner ring having an orbital surface on its outer circumferential surface,
A plurality of balls disposed between the raceway surfaces of the outer ring and the inner ring,
The ball is kept to be freely rotatable,
And an angular contact ball bearing
D1 > D2 where D1 is the outer diameter of the inner wheel counterbore formed in the outer peripheral surface of the inner ring on the rear side, and D2 is the outer diameter of the convexly formed inner wheel groove shoulder on the front side,
D3 > D4 where D3 is the inner diameter of the outer ring counterbore formed on the front surface side of the inner peripheral surface of the outer ring, and D4 is the inner diameter of the outer ring groove shoulder portion formed on the back surface side,
The contact angle alpha of the ball is 45 DEG &le; 65 DEG,
Ai is defined as 0.35 < / = Ai &le; 0.50 where Ai is the radial height of the inner ring groove shoulder portion divided by the diameter of the ball,
And Ae denotes a value obtained by dividing the radial height of the outer ring groove shoulder by the diameter of the ball, 0.35? Ae? 0.50,
The retainer includes a ring portion having a substantially annular shape and a plurality of pillars protruding in the axial direction at predetermined intervals from a front side or back side of the ring portion, A crown-type retainer having a pocket portion,
In the retainer, a reinforcement material is added,
Wherein X is a pitch circle diameter of the balls and? Rmax = X 2 x 5.0 x 10 -6 + X x 1.8 x 10 -3 +0.14, and ΔRmin = X 2 x 5.5 x 10 -6 + X x 1.5 x 10 - 3 +0.02, the radial motion amount? R of the retainer is? Rmin?? R?? Rmax,
And? T < DELTA Rmin, where DELTA t is the relative expansion of the retainer at 100 DEG C in the radial direction.
(2) The spherical center position of the pocket portion is shifted in the radial direction with respect to the radial center of the ring portion,
The angular ball bearing as set forth in (1), wherein a radial cross-sectional shape of the pocket portion is a cause of an arbitrary radius.
(3) The above-mentioned retainer is made of a polyamide resin,
The reinforcing material is glass fiber,
The angular ball bearing according to (1) or (2), wherein the ratio of the reinforcement material in the retainer is 5 to 30 wt%.
The inner diameter D3 of the outer ring counterbore is larger than the inner diameter D4 of the outer ring groove shoulder (D3 > D4), and the inner diameter of the outer ring groove bore is larger than the inner diameter D2 of the outer ring groove shoulder , And the contact angle? Of the ball satisfies 45???? 65. Therefore, by increasing the contact angle, the load capacity of the axial load of the bearing increases, and it can be used as a larger preload. As a result, it is possible to improve the rigidity of the bearing, and furthermore, the balls.
If Ai is obtained by dividing the radial height of the inner ring groove shoulder portion by the diameter of the ball, Ai is 0.35? Ai? 0.50, and Ae is the radial height of the outer ring groove shoulder portion divided by the diameter of the ball. It is possible to facilitate the grinding process of the inner and outer ring groove shoulder portions while preventing the load capacity of the axial load of the bearing from being insufficient.
Also, the pitch circle diameter of the ball to X and, ΔRmax = X 2 × 5.0 × 10 -6 to + X × 1.8 × 10 -3 +0.14 and, ΔRmin = X 2 × 5.5 × 10 -6 + X × 1.5 × 10 -3 +0.02, the radial movement amount? R of the retainer is set so as to satisfy? Rmin?? R?? Rmax. Therefore, it is possible to prevent the radial movement amount of the retainer from becoming larger than the radial clearance between the retainer and the inner and outer rings, and to prevent the contact between the retainer and the inner or outer ring.
When? T <? Rmin, the relative amount of expansion of the retainer in the radial direction at 100 占 폚 is? T. Therefore, even at the upper limit of the bearing service temperature, the retainer and the ball can be used without interfering with each other.
1 is a sectional view of an angular ball bearing according to an embodiment of the present invention.
Fig. 2 is a cross-sectional view of the angular ball bearings of Fig. 1 in combination.
3 is a side view of the retainer.
4 is a view of the retainer viewed from one side in the axial direction.
5 is a view of the retainer viewed from the other side in the axial direction.
Fig. 6 is a view as seen from a cross-sectional view taken along the line VI-VI in Fig.
7 is a cross-sectional view of an angular ball bearing according to a modification.
Fig. 8 is a view of the retainer related to the modified example viewed from one side in the axial direction. Fig.
9 (a) is a side view of the retainer, and FIG. 9 (b) is a view as seen from arrows IX in FIG.
10 is a graph showing the relationship between the pitch circle diameter of the ball, the radial motion amount of the holder and the radial direction relative expansion amount.
11 is a graph showing the relationship between the glass fiber content and the linear expansion coefficient of polyamide 66. Fig.
Hereinafter, an angular ball bearing according to an embodiment of the present invention will be described with reference to the drawings.
1, an
The inner circumferential surface of the
The outer circumferential surface of the
D1 <D2, the inner diameter of the
If Ai is the height (Hi) in the radial direction of the inner
In the case of 0.35 > Ai or 0.35 > Ae, the radial height (Hi, He) of the inner ring
A tapered
Such an
Next, with reference to Figs. 3 to 6, the structure of the
The
Here, in the
6, both side surfaces in the circumferential direction of the
The spherical center position of the
The ratio of the reinforcement material added to the synthetic resin of the material for the
In order to maintain a large contact angle? As in the
When the radial thickness of the
The radial movement of the
9, the radial movement amount? R of the ball guide
As described above, in the
In addition, by a number of analysis and experimental verification, the diameter the lower limit value (ΔRmin) of forward motion amount (ΔR) is, ΔRmin = X 2 × 5.5 × 10 -6 + X × 1.5 × 10 -3 is set to be +0.02. If DELTA Rmin = 0, the
It is also preferable that the
In Fig. 10, as the amount of the glass fiber added increases, the relative expansion amount? T in the radial direction of the
In the present embodiment, the amount of the glass fiber to be added is set to be in the range of 5 to 30 weight percent with the
Next, the lower limit of the glass fiber content in the polyamide 66 when the polyamide 66 is used as the material of the
(Example 1)
In the case of the
If the radial direction motion amount DELTA R exceeds the upper limit value of 0.24 mm, there is a problem that the radial direction motion amount DELTA R of the
In the application where the
From Table 1 it can be seen that the glass fiber content is 5 weight percent or more and the lower limit value? Rmin of the radial direction movement amount? R of the
(Example 2)
? Rmax? 0.36 mm and? Rmin? 0.21 mm in the bearing inner diameter (d)? 60 mm, the bearing outer diameter (D)? 120 mm and the ball pitch circle diameter (W)? 93 mm, The radial movement amount? R of the
Table 2 shows that the glass fiber content is 5 weight percent or more and the lower limit value DELTA Rmin of the radial direction movement amount DELTA R of the
As described above, it has become clear that the lower limit of the content of reinforcing fibers in the synthetic resin of the material of the
The present invention is not limited to the above-described embodiments, but can be appropriately changed, improved, and the like.
The present application is based on Japanese Patent Application No. 2014-037087 filed on February 27, 2014, the content of which is incorporated herein by reference.
1: Angular contact ball bearing
3: Ball
10: Outer ring
11: raceway surface
12: outer shoulder groove shoulder portion
13: Paddle counterbore
14: Chamfer of the paddle
20: Inner ring
21: Orbital plane
22: inner ring groove shoulder portion
23: inner ring counter bore
24: Chamfer of inner ring
30: retainer
31: Rings
32:
33: pocket portion
34:
35:
Claims (3)
An inner ring having an orbital surface on its outer circumferential surface,
A plurality of balls disposed between the raceway surfaces of the outer ring and the inner ring,
The balls are held in a freely rotatable manner, and a ball guide system,
And an angular contact ball bearing
D1 > D2 where D1 is the outer diameter of the inner wheel counterbore formed in the outer peripheral surface of the inner ring on the rear side, and D2 is the outer diameter of the convexly formed inner wheel groove shoulder on the front side,
D3 > D4 where D3 is the inner diameter of the outer ring counterbore formed on the front surface side of the inner peripheral surface of the outer ring, and D4 is the inner diameter of the outer ring groove shoulder portion formed on the back surface side,
The contact angle alpha of the ball is 45 DEG &le; 65 DEG,
Ai is defined as 0.35 < / = Ai &le; 0.50 where Ai is the radial height of the inner ring groove shoulder portion divided by the diameter of the ball,
And Ae denotes a value obtained by dividing the radial height of the outer ring groove shoulder by the diameter of the ball, 0.35? Ae? 0.50,
The retainer includes an annular ring portion and a plurality of pillar portions protruding in the axial direction at predetermined intervals from a front side or a rear side of the ring portion and a plurality of pockets formed between the adjacent pillar portions, A crown-type retainer having a portion,
In the retainer, a reinforcement material is added,
Wherein X is a pitch circle diameter of the balls and? Rmax = X 2 x 5.0 x 10 -6 + X x 1.8 x 10 -3 +0.14, and ΔRmin = X 2 x 5.5 x 10 -6 + X x 1.5 x 10 - 3 +0.02, the radial motion amount? R of the retainer is? Rmin?? R?? Rmax,
DELTA t < DELTA Rmin, where DELTA t is the relative expansion of the retainer at 100 DEG C in the radial direction,
A notch portion having a V-shaped cross section is formed at the tip of the column portion,
The pitch circle diameter X of the balls is 34 mm or more and 93 mm or less,
Wherein the retainer is made of a polyamide resin,
The reinforcing material is glass fiber,
Wherein the ratio of the reinforcement material in the retainer is 5 to 30 wt%.
The spherical center position of the pocket portion is shifted in the radial direction with respect to the radial center of the ring portion,
Wherein the radial cross-sectional shape of the pocket portion is a cause of an arbitrary radius.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JPJP-P-2014-037087 | 2014-02-27 | ||
JP2014037087 | 2014-02-27 | ||
PCT/JP2014/069096 WO2015129064A1 (en) | 2014-02-27 | 2014-07-17 | Angular ball bearing |
Publications (2)
Publication Number | Publication Date |
---|---|
KR20160113258A KR20160113258A (en) | 2016-09-28 |
KR101988706B1 true KR101988706B1 (en) | 2019-06-12 |
Family
ID=54008418
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
KR1020167023382A KR101988706B1 (en) | 2014-02-27 | 2014-07-17 | Angular ball bearing |
Country Status (5)
Country | Link |
---|---|
JP (1) | JP6376212B2 (en) |
KR (1) | KR101988706B1 (en) |
CN (1) | CN106164512B (en) |
TW (1) | TWI567306B (en) |
WO (1) | WO2015129064A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2017061417A1 (en) * | 2015-10-05 | 2017-04-13 | Ntn株式会社 | Angular contact ball bearing, and ball screw device using same |
JP6765920B2 (en) * | 2015-10-05 | 2020-10-07 | Ntn株式会社 | Angular contact ball bearing and ball screw device using it |
US10618370B2 (en) | 2016-09-02 | 2020-04-14 | Mando Corporation | Active roll stabilizer |
JP2022024610A (en) * | 2020-07-28 | 2022-02-09 | Ntn株式会社 | Angular ball bearing |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005061509A (en) * | 2003-08-11 | 2005-03-10 | Nsk Ltd | Rolling bearing |
JP2008185107A (en) * | 2007-01-29 | 2008-08-14 | Nsk Ltd | Ball bearing |
JP2011007286A (en) * | 2009-06-26 | 2011-01-13 | Ntn Corp | Deep groove ball bearing and gear support device |
JP2013087865A (en) * | 2011-10-18 | 2013-05-13 | Nsk Ltd | Multi-row combination ball bearing |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS596262Y2 (en) * | 1978-10-16 | 1984-02-27 | 株式会社不二越 | Resin crown retainer |
JP2000104742A (en) | 1998-09-29 | 2000-04-11 | Ntn Corp | Rolling bearing for supporting ball screw |
JP4131099B2 (en) * | 2001-10-25 | 2008-08-13 | 日本精工株式会社 | Double row radial ball bearing |
JP4055938B2 (en) * | 2002-04-18 | 2008-03-05 | ミネベア株式会社 | Radial ball bearing retainer |
EP1367277B1 (en) * | 2002-05-30 | 2008-06-25 | Minebea Co., Ltd. | Retainer with rotationally symmetric pockets |
JP4192515B2 (en) * | 2002-07-16 | 2008-12-10 | 株式会社ジェイテクト | Resin cage for angular contact ball bearings |
JP2006153094A (en) * | 2004-11-26 | 2006-06-15 | Nsk Ltd | Ball bearing and rotary table device for machine tool using ball bearing |
JP2007298184A (en) * | 2006-08-25 | 2007-11-15 | Nsk Ltd | Angular ball-bearing |
WO2011062269A1 (en) * | 2009-11-19 | 2011-05-26 | 日本精工株式会社 | Rotation support device for pinion shaft |
-
2014
- 2014-07-17 JP JP2016504985A patent/JP6376212B2/en active Active
- 2014-07-17 WO PCT/JP2014/069096 patent/WO2015129064A1/en active Application Filing
- 2014-07-17 KR KR1020167023382A patent/KR101988706B1/en active IP Right Grant
- 2014-07-17 CN CN201480076581.5A patent/CN106164512B/en active Active
- 2014-09-16 TW TW103131985A patent/TWI567306B/en active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2005061509A (en) * | 2003-08-11 | 2005-03-10 | Nsk Ltd | Rolling bearing |
JP2008185107A (en) * | 2007-01-29 | 2008-08-14 | Nsk Ltd | Ball bearing |
JP2011007286A (en) * | 2009-06-26 | 2011-01-13 | Ntn Corp | Deep groove ball bearing and gear support device |
JP2013087865A (en) * | 2011-10-18 | 2013-05-13 | Nsk Ltd | Multi-row combination ball bearing |
Also Published As
Publication number | Publication date |
---|---|
CN106164512B (en) | 2019-03-29 |
JPWO2015129064A1 (en) | 2017-03-30 |
WO2015129064A1 (en) | 2015-09-03 |
TWI567306B (en) | 2017-01-21 |
CN106164512A (en) | 2016-11-23 |
KR20160113258A (en) | 2016-09-28 |
JP6376212B2 (en) | 2018-08-22 |
TW201533339A (en) | 2015-09-01 |
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