CN101457792B - Half-contact and half-non-contact seal structure for bearing - Google Patents
Half-contact and half-non-contact seal structure for bearing Download PDFInfo
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- CN101457792B CN101457792B CN2007101647678A CN200710164767A CN101457792B CN 101457792 B CN101457792 B CN 101457792B CN 2007101647678 A CN2007101647678 A CN 2007101647678A CN 200710164767 A CN200710164767 A CN 200710164767A CN 101457792 B CN101457792 B CN 101457792B
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- bearing
- inner ring
- inner edge
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- 238000007789 sealing Methods 0.000 claims description 88
- 230000008901 benefit Effects 0.000 abstract description 5
- 238000005299 abrasion Methods 0.000 abstract 2
- 239000004519 grease Substances 0.000 description 19
- 238000000034 method Methods 0.000 description 11
- 230000008569 process Effects 0.000 description 7
- 238000005096 rolling process Methods 0.000 description 6
- 239000003350 kerosene Substances 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 235000010599 Verbascum thapsus Nutrition 0.000 description 2
- 244000178289 Verbascum thapsus Species 0.000 description 2
- 230000032683 aging Effects 0.000 description 2
- 239000002199 base oil Substances 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 206010017389 Frotteurism Diseases 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000029087 digestion Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 239000003566 sealing material Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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- Sealing Of Bearings (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The invention discloses a semi-contact seal structure and a semi-non contact seal structure of a bearing which belongs to a bearing structure. The existing contact seal structure and the non-contact seal structure are difficult to realize the requirements of small operation friction, less abrasion, less temperature rise, high limit rotation speed and good seal performance. The invention comprises an inner ring, an outer ring, and a seal piece arranged between the inner ring and the outer ring; the seal piece is provided with at leas one inner edge seal lip. The invention is characterized in that the part of at least one inner edge seal lip of the inner edge seal lips has a clearance with the inner ring; the rest parts are used as a contact part to be sealed and contacted with the inner ring. The structure realizes the contact seal and the non-contact seal on one inner edge seal lip simultaneously, thus integrating the advantages of the two seal forms and realizing the requirements of small operation friction, less abrasion, low temperature rise, high limit rotation speed and good seal performance.
Description
Technical field
The invention belongs to bearing structure, is half contact of a kind of bearing, half non-contact seal structure specifically.
Background technique
Existing mainly by inner ring, outer ring and the rolling bearing that constitutes between the rolling element between the two and Sealing, during rotation Sealing static relative to the outer ring usually, rotate relative to inner ring.
In the face of the harsh market demands and the real current situation of production, the manufacturing enterprise that has is on the one hand in order to detect bearing static sealing General, on the other hand also in order to pursue " positive confinement ", every suit bearing is carried out sealing detection (see Figure 15,16): at an end fit on Sealing of bearing 22, the other end is not adorned Sealing and is made progress, beneath pad a piece of paper 21 at bearing 22, in bearing, inject kerosene 23, horizontal positioned 24-72 hour, see that pad has the not kerosene of bearing seepage on the paper under the bearing 21, non-leakage person is qualified, and with this one procedure as the total inspection of bearing, so that guide the sealing of bearing into real " positive confinement ".During actual the use, because sealing is very good, (bearing also is the process that interior cavity temperature raises from the process that starts to normal operation when just starting, otherwise, the process that bearing stops from running well to also is the process that interior cavity temperature reduces) bearing cavity is negative pressure, the sealing lip of Sealing presses bearing surface more, bring bigger friction, bigger starting torque, bigger wearing and tearing, bigger temperature rise to bearing, and then aggravated grease and Sealing high temperature ageing and the more seepage of grease more early again, so that cause the premature failure of bearing, things turn out contrary to one's wishes.
And the seal form between Sealing 1 and the inner ring 5 is more common in two kinds of structures: contact seal (seeing Figure 13,14) and noncontact seal (seeing Figure 11,12), the former is that whole inner edge sealing lip all seals contact on inner ring, the latter be whole inner edge sealing lip with inner ring between keep slit 25 to reach all not contacting, when having a plurality of inner edge sealing lips to form multi-layer sealing structure, the inner edge sealing lip that has adopts contact seal, and the inner edge sealing lip that has adopts noncontact seal.The noncontact seal structure does not almost have seal friction, and its advantage is: operation friction is little, wearing and tearing less, temperature rise is little, limit speed is high, its shortcoming is: seal clearance is big, poor sealing performance; Contact seal is because sealing lip is waled tightly or pressed the lasso slidingsurface, and its advantage is: good seal performance; Its shortcoming is: the operation friction resistance is big, temperature rise, limit speed are low, Sealing and easily accelerated ageing in high temperature of grease.These two kinds of patterns all be difficult to realize " operation friction is little, wearing and tearing less, temperature rise is little, limit speed is high and sealability good again " requirement.
Summary of the invention
The technical assignment of the technical problem to be solved in the present invention and proposition be realize being difficult to of overcoming that prior art exists that operation friction is little, wearing and tearing less, temperature rise is little, limit speed is high and the sealability defective of good requirement again, half contact of a kind of bearing, half non-contact seal structure are provided, for this reason by the following technical solutions:
Bearing half contact, half non-contact seal structure, comprise inner ring, outer ring and between the Sealing between the two, described Sealing has at least one inner edge sealing lip, keep being communicated with bearing cavity and extraneous gap between the part that it is characterized in that in the described inner edge sealing lip at least one and the inner ring, should with inner ring between keep the remaining part of the inner edge sealing lip in described gap to seal with inner ring contacting as contacting part.
Technique scheme, by keeping the gap to realize being communicated with of bearing cavity and the external world between the part of inner edge sealing lip and the inner ring, the temperature rise air pressure and the bearing external atmosphere pressure of bearing cavity are almost equal when allowing startup, reduce pressure reduction and cause " squeeze and leak " phenomenon (being the phenomenon that chamber pressure is extruded the grease of inner chamber greater than external atmosphere pressure), the barometric pressure in the cold conditions air pressure of inner chamber and the bearing external world almost is equal to when also allowing the bearing stall, reduce because of " positive confinement " and cause negative pressure in the chamber at this moment, avoid the inner edge sealing lip to press inner peripheral surface and build-up of pressure is excessive, wearing and tearing and temperature rise when aggravation starts.This structure has realized contact seal and noncontact seal simultaneously on an inner edge sealing lip, reach the advantage that has two kinds of seal form concurrently, the requirement of realize that operation friction is little, wear and tear less, temperature rise is little, limit speed is high and sealability is good again.
As the further of technique scheme improved and replenish, make it have multiple implementation, the present invention also comprises following additional technical feature:
Described contacting part contacts with the end face of inner ring; Also can contact with the cylndrical surface of inner ring; Can also contact with the conical surface of inner ring, the diameter of this conical surface inside portion is greater than the diameter of lateral part at this moment, " centrifugal " principle and " pump suction " principle when being convenient to like this use rotation are carried out ingenious design, with because of various reasons and the very big part grease of seepage sucks back in the chamber, further reduce the probability and the quantity of seepage, further, make the inclination angle that forms between inner ring conical surface and the inner edge sealing lip towards inner chamber, allow the external lateral portion of inner edge sealing lip on the inner ring conical surface form half contact, half non-contact sealing, inside part forms noncontact seal, " pump suction " principle during the utilization rotation, the grease of seepage when rotated to an end (bearing cavity side) " pumping " of the big conical surface, is slowed down seepage probability and quantity.
Described gap forms for recess is set on the inner edge sealing lip of Sealing, recess also can be set on inner ring form.
The invention has the beneficial effects as follows:
1, on an inner edge sealing lip, realized contact seal and noncontact seal simultaneously, reached the advantage that has two kinds of seal form concurrently, the requirement of realize that operation friction is little, wear and tear less, temperature rise is little, limit speed is high and sealability is good again;
2, enforcement approach is various;
3, the contacting part by the inner edge sealing lip contacts with the conical surface of inner ring, and the diameter of conical surface inside portion that makes inner ring is greater than the diameter of lateral part, " centrifugal " principle and " pump suction " principle when being convenient to like this use rotation are carried out ingenious design, with because of various reasons and the very big part grease of seepage sucks back in the chamber, further reduce the probability and the quantity of seepage.
4, between conical surface and inner edge sealing lip, form inclination angle towards inner chamber, this inclination angle is divided into the inboard clearance seal district and the close-fitting seal area in the outside with whole inclined-plane seal area, " pump suction " principle during the utilization rotation, the grease of seepage when rotated to an end (bearing cavity side) " pumping " of the big conical surface, is slowed down seepage probability and quantity.
Description of drawings
Fig. 1 be relate to sealing configuration of the present invention a kind of rolling bearing partly cut open schematic representation.
Fig. 2 is the A portion enlarged view (demonstrating a kind of structure of sealing configuration of the present invention) of Fig. 1.
Fig. 3 is that the Z-Z of Fig. 2 is to sectional view.
Fig. 4 is the B portion enlarged view of Fig. 2.
Fig. 5 is the another kind of structural representation of sealing configuration of the present invention.
Fig. 6 is that the K-K of Fig. 7 is to sectional view.
Fig. 7 is the third structural representation of sealing configuration of the present invention.
Fig. 8 is that the W-W of Fig. 7 is to sectional view.
Fig. 9 A, 9B are a kind of experimental model schematic representation of the present invention's " pump suction " phenomenon.
Figure 10 A, 10B are the another kind of experimental model schematic representation of the present invention's " pump suction " phenomenon.
Figure 11 is the schematic representation of existing contact seal structure.
Figure 12 is that the X-X of Figure 11 is to sectional view.
Figure 13 is the schematic representation of existing contact seal structure.
Figure 14 is that the Y-Y of Figure 13 is to sectional view.
Figure 15 is the existing schematic representation that the bearing seal performance is tested.
Figure 16 is the C portion enlarged view of Figure 15.
Among the figure: 1-Sealing, 2-rolling element, 3-outer ring, the 4-retainer, 5-inner ring, 6-inner edge sealing lip, the 7-gap, 8-contacting part, 9-recess, the 10-end face, 11-cylndrical surface, 12-conical surface, the 13-internal cones, 14-external cone, 15-steel ball, the 16-grease, 17-clearance seal district, 18-close-fitting seal area, 19-master's inner edge sealing lip, the secondary inner edge sealing lip of 20/20a/20b-, 21-paper, the 22-bearing, 23-kerosene, 24-inner chamber, the 25-slit, β-inclination angle, the inside portion diameter of D1-conical surface, the lateral part diameter of D2-conical surface.
Embodiment
The present invention will be further described by several preferred embodiments below in conjunction with accompanying drawing.
Embodiment one
Rolling bearing as shown in Figure 1, it is by an outer ring 3, an inner ring 5, some rolling elements 2, retainer 4 and Sealing 1 are assembled, the difference of itself and existing structure is embodied in A portion and (sees Fig. 2 for details, 3,4), Sealing 1 has an inner edge sealing lip 6, uniform two recesses 9 on the inner edge sealing lip 6, it between two recesses 9 contacting part 8, contacting part 8 is conical surface-shaped, form angle of inclination beta between itself and the conical surface 12 towards inner chamber 24, this angle of inclination beta forms inboard clearance seal district 17, the close-fitting seal area 18 in the outside between inner edge sealing lip and inner ring conical surface.Between the recess 9 of assembling condition lower seal 1 and inner ring 5, keep gap 7, contacting part 8 contacts with conical surface 12 (being the face that bus the favours inner ring axis) sealing of inner ring 5, and the diameter D1 of conical surface 12 inside portions (promptly closing on the position of inner chamber) is greater than the diameter D2 of lateral part (promptly closing on extraneous position), the external lateral portion of inner edge sealing lip on the inner ring conical surface is because the close-fitting factor forms contact seal, again because the existence in gap 7, final external lateral portion on the inner ring conical surface has formed half contact, half non-contact sealing, the inside part of inner edge sealing lip then form noncontact seal because of the existence and the inner ring conical surface of angle of inclination beta; When rotating, can form " pump suction " phenomenon again and (shown in Fig. 9 A, test structure, internal cones 13 that cone angle is identical and external cone 14, the small ball 15 that is situated between and is covered with individual layer, one is fixed another rotation, after running a period of time, most of small ball is all made a clean sweep of out (seeing Fig. 9 B) toward one of big taper hole; Change these small balls into the very thin grease of one deck 16, also found similar situation, at an end of big taper hole as there being one " pump " inhaling, grease 16 is inhaled to big end one side (seeing Figure 10 A, 10B), this phenomenon is defined as " pump suction " phenomenon here), with because of various reasons and the very big part grease of seepage sucks back in the chamber, further reduce the probability and the quantity of seepage.
Embodiment two
Shown in Fig. 5,6, Sealing 1 has a main inner edge sealing lip 19 and a secondary inner edge sealing lip 20, secondary inner edge sealing lip 20 is generally Spielpassung with the cylndrical surface 11 of inner ring, main inner edge sealing lip 19 is made non-just justifying (as ellipse), thereby under assembling condition, make it greatly partly upward form the 11 formation gaps 7, cylndrical surface of sealing contact, sub-fraction and inner ring in the cylndrical surface 11 of inner ring (being the bus face parallel), thereby form partly contact, half non-contact seal structure with inner ring axis as contacting part 8 contacts.
Embodiment three
Shown in Fig. 7,8, Sealing 1 has a main inner edge sealing lip 19 and two secondary inner edge sealing lip 20a, 20b (two secondary inner edge sealing lip 20a, 20b and inner ring 5 surfaces generally be non-contact seal), on main inner edge sealing lip 19, design recess 9 or be designed to main inner edge sealing lip 19 wavy (obvious, also can on the end face of inner ring, recess be set), main inner edge sealing lip 19 is pressed in by elasticity on the end face 10 of inner ring 5 (promptly vertical with inner ring axis face) under assembling condition, forms gap 7 by the end face 10 of the recess 9 of main inner edge sealing lip 19 and inner ring 5; Contacting part 8 by main inner edge sealing lip 19 forms contact seal with inner ring 5 end faces 10; Constitute thus that half between inner ring end face 10 and the main inner edge sealing lip 19 contacts, half non-contact seal structure.
Further, in this structure, the gap wedge transition that wavy main inner edge sealing lip 19 forms, grease that take out of or that other factors are taken out of during with the running exhaust, in the seepage process, wedge again between contacting part and the sealing surface, to play the effect that improves the contacting part Frotteurism, become original dry friction or semi-dry friction and be semi-dry friction or lubrication friction, to reduce inner edge sealing lip adhesive wear, fretting wear, reduce spin friction moment and reduce the product temperature rise, prolong bearing seal performance and grease Life cycle.
Below with the application note work of the present invention of automobile Idle wheel (idle pulley) bearing.
Automobile Idle wheel (idle pulley) bearing is an outer ring high speed rotating under the high temperature owing to be to use at the motor car engine front end, general rotating speed 8000-15000R.P.M; Circumstance of temperature difference changes also greatly, reaches-the 30-150 degree; Dust and rainwater face constantly; So it requires highly to sealing, so to say that Mi Feng life-span almost is exactly the life-span of this bearing.
After the last time uses, bearing has " hot " to become " cold conditions ", because adopted " half contact, half non-contact " Seal Design pattern, the air pressure and the barometric pressure outside the chamber of bearing cavity are almost equal, so the inner edge sealing lip is not waled bearing inner race inflexibly; Owing to there is " capillary " phenomenon, the base oil that grease is separated out will ooze in these both sides in the both sides at " half non-contact " position.
Bearing just started next time the time, inner edge sealing lip and inner peripheral surface just produce friction, and the base oil that oozes in these both sides has played the effect that improves lubricating status, allow its friction is littler, wearing and tearing still less, generate heat not high.The minimizing of wearing and tearing makes Sealing durable more; The reduction of temperature rise has prolonged the digestion period of sealing material and grease conversely again.
Along with continuing of rotating, bearing temperature rise constantly rises, and inner chamber gas also expands gradually, and a part of gas of expansion is discharged by the gap; Evaded the problem that full contact seal structure expanding gas can't rationally discharge (existence of this pressure reduction can be outer sticking near grease extruding cavity inboard the inner edge sealing lip); In the middle of this slow discharging process, can take some greases out of more or less, or other all reason also can slowly be leaked a part of grease, the speed of " taking out of " is much more slowly than the rotating speed of Sealing, so these greases in leakage process with regard to the seal area of wedged " half contact, half non-contact ", rely on " centrifugal " principle and " pump suction " principle of structure, major part in these greases is sucked back again in the inner chamber 24 of Sealing, so just slow down the probability and the quantity of grease seepage, improved the sealability of bearing greatly.
Claims (7)
1. bearing half contact, half non-contact seal structure, comprise inner ring (5), outer ring (3) and between the Sealing between the two (1), described Sealing (1) has at least one inner edge sealing lip (6,19,20a, 20b), keep being communicated with bearing cavity and extraneous gap (7) between the part that it is characterized in that in the described inner edge sealing lip (6,19,20a, 20b) at least one and the inner ring (5), should with inner ring (5) between keep the remaining part of the inner edge sealing lip in described gap (7) to seal with inner ring (5) contacting as contacting part (8).
2. bearing according to claim 1 half contact, half non-contact seal structure is characterized in that described contacting part (8) contacts with the end face (10) of inner ring (5).
3. bearing according to claim 1 half contact, half non-contact seal structure is characterized in that described contacting part (8) contacts with the cylndrical surface (11) of inner ring (5).
4. bearing according to claim 1 half contact, half non-contact seal structure it is characterized in that described contacting part (8) contacts with the conical surface (12) of inner ring (5), and the diameter (D1) of this conical surface (12) inside portion are greater than the diameters (D2) of lateral part.
5. bearing according to claim 4 half contact, half non-contact seal structure is characterized in that forming towards the inclination angle of inner chamber (24) (β) between described conical surface (12) and the inner edge sealing lip (6).
6. according to half contact of the described bearing of the arbitrary claim of 1-5, half non-contact seal structure, it is characterized in that described gap (7) forms for recess (9) is set on the inner edge sealing lip (6) of Sealing (1).
7. according to half contact of the described bearing of the arbitrary claim of 1-5, half non-contact seal structure, it is characterized in that described gap (7) forms for recess is set on inner ring (5).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2007101647678A CN101457792B (en) | 2007-12-13 | 2007-12-13 | Half-contact and half-non-contact seal structure for bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2007101647678A CN101457792B (en) | 2007-12-13 | 2007-12-13 | Half-contact and half-non-contact seal structure for bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101457792A CN101457792A (en) | 2009-06-17 |
| CN101457792B true CN101457792B (en) | 2011-01-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2007101647678A Expired - Fee Related CN101457792B (en) | 2007-12-13 | 2007-12-13 | Half-contact and half-non-contact seal structure for bearing |
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| Country | Link |
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| CN (1) | CN101457792B (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112122630B (en) * | 2020-09-27 | 2022-09-27 | 泉州市井贺精密设备有限公司 | Main shaft seal structure and tool turret |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19709056A1 (en) * | 1997-03-06 | 1998-09-10 | Schaeffler Waelzlager Ohg | Seal for automotive clutch bearing |
| DE10135176C1 (en) * | 2001-07-19 | 2003-04-10 | Skf Ab | Seal ring for roller bearing has support ring mounted on bearing race to carry seal ring and opposed gap seal ring |
| EP1589242A1 (en) * | 2004-04-02 | 2005-10-26 | INA-Schaeffler KG | Release bearing provided with a sealing lip and a device limiting the amplitude of its movement |
| DE102005029979A1 (en) * | 2005-06-28 | 2007-01-11 | Schaeffler Kg | Spherical plain bearings |
| CN2908904Y (en) * | 2006-04-20 | 2007-06-06 | 青岛泰德汽车轴承有限责任公司 | Bearing sealing device of electromagnetic clutch |
| CN200949605Y (en) * | 2006-09-11 | 2007-09-19 | 洛阳轴研科技股份有限公司 | Sealing deep groove ball bearing of novel vehicle AC generator |
-
2007
- 2007-12-13 CN CN2007101647678A patent/CN101457792B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19709056A1 (en) * | 1997-03-06 | 1998-09-10 | Schaeffler Waelzlager Ohg | Seal for automotive clutch bearing |
| DE10135176C1 (en) * | 2001-07-19 | 2003-04-10 | Skf Ab | Seal ring for roller bearing has support ring mounted on bearing race to carry seal ring and opposed gap seal ring |
| EP1589242A1 (en) * | 2004-04-02 | 2005-10-26 | INA-Schaeffler KG | Release bearing provided with a sealing lip and a device limiting the amplitude of its movement |
| DE102005029979A1 (en) * | 2005-06-28 | 2007-01-11 | Schaeffler Kg | Spherical plain bearings |
| CN2908904Y (en) * | 2006-04-20 | 2007-06-06 | 青岛泰德汽车轴承有限责任公司 | Bearing sealing device of electromagnetic clutch |
| CN200949605Y (en) * | 2006-09-11 | 2007-09-19 | 洛阳轴研科技股份有限公司 | Sealing deep groove ball bearing of novel vehicle AC generator |
Non-Patent Citations (1)
| Title |
|---|
| JP特开2002-155959A 2002.05.31 |
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| Publication number | Publication date |
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| CN101457792A (en) | 2009-06-17 |
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Application publication date: 20090617 Assignee: HANGZHOU TRUST AUTO BEARING CO.,LTD. Assignor: Chen Bingshun Contract record no.: 2015330000182 Denomination of invention: Half-contact and half-non-contact seal structure for bearing Granted publication date: 20110105 License type: Exclusive License Record date: 20150703 |
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Granted publication date: 20110105 |