CN102374291B - Improved structure of bearing base sealing ring - Google Patents
Improved structure of bearing base sealing ring Download PDFInfo
- Publication number
- CN102374291B CN102374291B CN201010259064.5A CN201010259064A CN102374291B CN 102374291 B CN102374291 B CN 102374291B CN 201010259064 A CN201010259064 A CN 201010259064A CN 102374291 B CN102374291 B CN 102374291B
- Authority
- CN
- China
- Prior art keywords
- ring
- flanged
- bearing base
- flanged ring
- sealing ring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Rolling Contact Bearings (AREA)
Abstract
The invention relates to an improved structure of a bearing base sealing ring. The improved structure is characterized in that a sealing ring sleeved on a rotating shaft is mutually corresponding to an inner hole formed on the side wall of a bearing base, the outer edge of the sealing ring is provided with multiple parallel flanged rings which are matched with multiple parallel ring form grooves arranged on the inner hole; a first flanged ring of the end of the sealing ring is positioned on the outside of the side wall of the bearing base, the first flanged ring is a convex obtuse angle or an circular arc on a vertical cross-section on which the shaft center is positioned, the guiding oil effect is good, thereby conveniently controlling a gap between the first flanged ring and the side wall of the bearing base; the bottom of a ring groove arranged between the first flanged ring and a second flanged ring is provided with at least a circle of convex reverse spiral diversion trenches, thereby effectively preventing the lubricating oil on the bottom of the ring groove from outward leaking; and multiple backflows are formed from the root of the end face of the first flanged ring to the bottom of each groove uniformly, thereby being capable of leading the stored lubricating oil on the bottom of each groove to back to an inner cavity of the bearing base, and avoiding the phenomenon that the diversion trenches are out of action when too much oil is stored. A combined motive seal structure can effectively prevent the lubricating oil from leaking.
Description
Technical field
The present invention relates to the thin oil lubricating bearing support of centrifuge, relate in particular to a kind of seal ring of bearing support.
Background technique
The thin oil lubricating bearing support of centrifuge is the seal chamber of a hollow, on sidewall, have endoporus, rotatingshaft is horizontally through bearing support from endoporus, bearing by inside cavity is arranged on bearing support, between rotatingshaft and endoporus, configure a seal ring being fixed on rotary bearing, a plurality of parallel flanged rings of seal ring outer rim upper process, match with the multiple tracks parallel ring connected in star of offering on endoporus, form mazy sealing configuration between the two, and the first flanged ring of seal ring end is positioned at bearing support sidewall outside, in block axis bearing chamber, lubricant oil leaks.
But in use, when oil lubrication is cooling, due to bearing High Rotation Speed, lubricating fluid is produced to splash, still there is part fluid to enter in the clearance space between inner hole of bearing seat and seal ring from the gap location between seal ring the first flange and bearing support sidewall, and along with the rotation of seal ring is run to bearing support outside, caused bearing support to occur the phenomenon of oil leakage.
Summary of the invention
Technical problem to be solved by this invention is to provide a kind of bearing base sealing ring structure-improved that can effectively prevent that lubricant oil from revealing from fitting surface between seal ring and inner hole of bearing seat.
The present invention is achieved by the following technical solutions:
A structure-improved for bearing base sealing ring, the seal ring being sleeved on rotatingshaft is corresponding with the endoporus on bearing support sidewall,
A plurality of parallel flanged rings of seal ring outer rim upper process, with endoporus on the multiple tracks parallel ring connected in star offered match,
The first flanged ring of seal ring end is positioned at bearing support sidewall outside,
It is characterized in that:
Described the first flanged ring is obtuse angle or the circular arc of evagination on the vertical cross-section at place, axle center,
On at the bottom of circular groove between the first flanged ring and the second flanged ring, offer the protruding spirality guiding gutter of at least one circle, the Hand of spiral of guiding gutter is contrary with the sense of rotation of rotatingshaft, and the seal ring diameter at place, groove top is less than or equal to diameter of bore,
By the first flanged ring end face root to bottom land, evenly offer a plurality of return ports.
The first flanged ring of seal ring innermost layer is adopted to the horn mouth design that is outer convex corner or circular arc, compare with traditional vertical bar shaped the first flanged ring, can effectively guide the lubricating oil being splashed on the first flanged ring to be back to bearing support inner chamber, and, because seal ring is with rotatingshaft High Rotation Speed, seal ring and bearing support sidewall, between endoporus, must keep certain gap, between traditional vertical bar shaped the first flanged ring and bearing support sidewall, there is a larger fitting surface, the gap of this fitting surface is difficult to control, tend to because excesssive gap and leakage of oil is more, and be the obtuse angle of evagination or the first flanged ring of circular arc, only need the gap control between its top and bearing support sidewall is good, just can more effectively stop the oil that splashes in a large number to outward leakage.In general, this Interval selecting is 0.5～1.5mm, can guarantee phase mutual noninterference between seal ring and bearing support sidewall, can play preferably seal action again.
The first flanged ring of outer convex corner or circular arc has stoped leaking of a large amount of splash lubrication oil, the lubricating oil splashing on a small quantity will enter from the gap of the first flanged ring top and bearing support sidewall between seal ring and inner hole of bearing seat, accumulate in labyrinth sealing space wherein, on at the bottom of the circular groove between the first flanged ring and the second flanged ring, offer the protruding spirality guiding gutter of at least one circle, because the Hand of spiral of guiding gutter is contrary with the sense of rotation of rotatingshaft, can effectively stop that the leakage fluid through the first flanged ring continues to reveal to bearing support is outside, and fluid can be pushed away to cavity direction is counter in bearing support, be beneficial to fluid and return in time bearing support inner chamber from being opened in the return port of bottom land, avoid fluid to accumulate when too much guiding gutter at bottom land ineffective.
Return port has two kinds of effects to offer preferably mode: a kind of is axially by the first flanged ring end face root is flat, to open to the second flanged ring along rotatingshaft, and the evagination place of the outer convex corner of return port height and the first flanged ring or circular arc is contour; A kind of be return port on the vertical cross-section at place, axle center to cavity dumping in bearing support, axially have angle with rotatingshaft, this angle is 15～30 degree conventionally, by the first flanged ring end face root to bottom land.The former opening is large, be beneficial to lubricating oil refluxes, the latter with angle of inclination, can effectively guide the lubricant oil being positioned at the bottom of the circular groove of rotatingshaft top to reflux downwards.
Same, be the backflow effect that guarantees return port, return port should be and is evenly opened in a plurality of on the first flanged ring end, is preferably 4 that symmetry is offered.
Further, for better stopping fluid, can at the bottom of circular groove, offer individual pen guiding gutter, and this guiding gutter in vertical cross-section with 2～4 groove teeth, this guiding gutter has rotated 2～4 weeks along bottom land anchor ring, how all the choked flow effect of groove tooth be more obvious.
Further again, for guaranteeing the Oil Guide effect of the first flanged ring end face, its vertical cross-section is the obtuse angle of evagination, and evagination angle is 120～140 degree.
Beneficial effect of the present invention is:
1, the first flanged ring structure of outer convex corner or circular arc, can play good Oil Guide effect, and is convenient to control the gap between the first flanged ring and bearing support sidewall;
2, between the first flanged ring and the second flanged ring, oppositely offer guiding gutter, effectively the lubricating oil at the bottom of entry deterrence circular groove is further to outward leakage;
3, at the bottom of circular groove and the return port of offering between the first flanged ring end face, can guide in time the lubricating oil that accumulates in bottom land to reflux into bearing support inner chamber, avoid fluid to accumulate when too much guiding gutter ineffective;
4, knockdown movable sealing structure, can effectively prevent leaking of lubricant oil.
Accompanying drawing explanation
Fig. 1 be on the vertical cross-section of place, axle center, the schematic diagram that coordinates of existing seal ring and bearing support
Fig. 2 be on the vertical cross-section of place, axle center, the schematic diagram that coordinates of seal ring of the present invention and bearing support
Fig. 3, Fig. 4 are a kind of enlarged diagram of return port structure within the scope of circle in Fig. 2
Fig. 5, Fig. 6 are the enlarged diagram of another kind of return port structure within the scope of circle in Fig. 2
Fig. 7 is seal ring stereogram
In Fig. 1-7: 1 is seal ring, and 1-1 is the first flanged ring, and 1-2 is the second flanged ring, and 1-3 is guiding gutter, 1-4 is return port, and 1-5 is bottom land, and 2 is bearing support sidewall, and 2-1 is endoporus, 3 is rotatingshaft, and 4 is existing seal ring, and 4-1 is vertical bar shaped the first flanged ring, and 5 is bearing.
Embodiment
Below in conjunction with accompanying drawing, the invention will be further described.
The thin oil lubricating bearing support of centrifuge is the seal chamber of a hollow, on sidewall 2, have endoporus 2-1, rotatingshaft 3 is horizontally through bearing support from endoporus 2-1, bearing 5 by inside cavity is arranged on bearing support, between rotatingshaft 3 and endoporus 2-1, configure an existing seal ring 4 being fixed on rotary bearing, a plurality of parallel flanged rings of existing seal ring 4 outer rim upper process, match with the multiple tracks parallel ring connected in star of offering on endoporus 2-1, form mazy sealing configuration between the two, and the vertical bar shaped first flanged ring 4-1 of seal ring end is positioned at bearing support sidewall 2 outsides, in block axis bearing chamber, lubricant oil leaks.
But in use, when oil lubrication is cooling, due to bearing 5 High Rotation Speeds, lubricating fluid is produced to splash, still there is part fluid to enter in the clearance space between inner hole of bearing seat 2-1 and seal ring 4 from the gap location between vertical bar shaped the first flanged ring 4-1 and bearing support sidewall 2, and along with the rotation of existing seal ring 4 is run to bearing support outside, caused bearing support to occur the phenomenon of oil leakage, as shown by the arrows in Figure 1.
The first flanged ring 1-1 in the present invention is the obtuse angle shape of evagination on the vertical cross-section at place, axle center, and the evagination angle in Fig. 2 is 140 degree.Compare with traditional vertical bar shaped the first flanged ring 4-1, can effectively guide the lubricating oil being splashed on the first flanged ring 1-1 end face to be back to bearing support inner chamber, and, because seal ring 1 is with rotatingshaft High Rotation Speed, seal ring 1 and bearing support sidewall 2, between endoporus 2-1, must keep certain gap, between traditional vertical bar shaped the first flanged ring 4-1 and bearing support sidewall 2, there is a larger fitting surface, the gap of this fitting surface is difficult to control, tend to because excesssive gap and leakage of oil is more, and be the obtuse angle of evagination or the first flanged ring 1-1 of circular arc, only need the gap control between its top and bearing support sidewall 2 is good, just can more effectively stop the oil that splashes in a large number to outward leakage.Gap between the first flanged ring 1-1 top and bearing support sidewall 2 is 1mm herein.
The first flanged ring 1-1 of outer convex corner or circular arc has stoped leaking of a large amount of splash lubrication oil, the lubricating oil splashing on a small quantity will enter from the gap of the first flanged ring 1-1 top and bearing support sidewall 2 between seal ring 1 and inner hole of bearing seat 2-1, accumulate in labyrinth sealing space wherein, on 1-5 at the bottom of the circular groove between the first flanged ring 1-1 and the second flanged ring 1-2, offered the protruding spirality guiding gutter 1-3 of a circle, this guiding gutter 1-3 has rotated 3 weeks on bottom land 1-5, there are three groove teeth, seal ring 1 diameter at place, groove top is less than or equal to endoporus 2-1 diameter, make the rotation in endoporus 2-1 in seal ring 1.Because the Hand of spiral of guiding gutter 1-3 is contrary with the sense of rotation of rotatingshaft 3, can effectively stop through the leakage fluid of the first flanged ring 1-1 and continue outsidely to reveal, and fluid can be pushed away to cavity direction is counter in bearing support to bearing support; By the first flanged ring 1-1 end face root, to bottom land 1-5 symmetry, offer 4 return port 1-4, return port 1-4 can guide the lubricating oil that accumulates in bottom land 1-5 to enter bearing support inner chamber in time, avoids fluid to accumulate when too much guiding gutter at bottom land 1-5 ineffective.Fluid backflow direction as shown by the arrows in Figure 2.
The scheme of offering that Fig. 3～4 are a kind of return port 1-4, return port 1-4 is offered to the second flanged ring 1-2 by the first flanged ring 1-1 end face root vertically, and return port 1-4 height is contour with the evagination place of the outer convex corner of the first flanged ring 1-1 or circular arc.
The scheme of offering that Fig. 5～6 are another kind of return port 1-4, return port 1-4 becomes 15～30 degree angles, by the first flanged ring 1-1 end face root, is upwards offered to bottom land 1-5 on the vertical cross-section at place, axle center with rotatingshaft 3 axle center.
Claims (8)
1. a structure-improved for bearing base sealing ring, the seal ring (1) being sleeved on rotatingshaft (3) is corresponding with the endoporus (2-1) on bearing support sidewall (2),
A plurality of parallel flanged rings of seal ring (1) outer rim upper process, with endoporus (2-1) on the multiple tracks parallel ring connected in star offered match,
First flanged ring (1-1) of seal ring (1) end is positioned at bearing support sidewall (2) outside,
It is characterized in that:
Described the first flanged ring (1-1) is the obtuse angle of evagination or the horn mouth of circular arc on the vertical cross-section at place, axle center,
At the bottom of circular groove between the first flanged ring (1-1) and the second flanged ring (1-2), on (1-5), offer the protruding spirality guiding gutter (1-3) of at least one circle, the Hand of spiral of guiding gutter (1-3) is contrary with the sense of rotation of rotatingshaft (3), seal ring (1) diameter at place, groove top is less than or equal to endoporus (2-1) diameter
By the first flanged ring (1-1) end face root to bottom land (1-5), evenly offer a plurality of return ports (1-4).
2. bearing base sealing ring structure-improved according to claim 1, it is characterized in that: described return port (1-4) is offered to the second flanged ring (1-2) by the first flanged ring (1-1) end face root vertically, return port (1-4) height is contour with the evagination place of the outer convex corner of the first flanged ring (1-1) or circular arc.
3. bearing base sealing ring structure-improved according to claim 1, is characterized in that: described return port (1-4) has angle with rotatingshaft (3) axle center, by the first flanged ring (1-1) end face root, upwards offered to bottom land (1-5) on the vertical cross-section at place, axle center.
4. bearing base sealing ring structure-improved according to claim 3, is characterized in that: described angle is 15～30 degree.
5. bearing base sealing ring structure-improved according to claim 1, is characterized in that: the guiding gutter at the bottom of described circular groove on (1-5) (1-3) on the vertical cross-section at place, axle center with 2～4 groove teeth.
6. bearing base sealing ring structure-improved according to claim 1, is characterized in that: described the first flanged ring (1-1) is the obtuse angle of evagination on the vertical cross-section at place, axle center, and evagination angle is 120～140 degree.
7. bearing base sealing ring structure-improved according to claim 1, is characterized in that: described return port (1-4) is symmetrical 4 of offering on the first flanged ring (1-1) end face.
8. bearing base sealing ring structure-improved according to claim 1, is characterized in that: the gap between described the first flanged ring (1-1) top and bearing support sidewall (2) is 0.5～1.5mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010259064.5A CN102374291B (en) | 2010-08-20 | 2010-08-20 | Improved structure of bearing base sealing ring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010259064.5A CN102374291B (en) | 2010-08-20 | 2010-08-20 | Improved structure of bearing base sealing ring |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102374291A CN102374291A (en) | 2012-03-14 |
| CN102374291B true CN102374291B (en) | 2014-07-23 |
Family
ID=45793334
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010259064.5A Expired - Fee Related CN102374291B (en) | 2010-08-20 | 2010-08-20 | Improved structure of bearing base sealing ring |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102374291B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112983761B (en) * | 2021-03-31 | 2022-06-03 | 东方电气集团东方电机有限公司 | Sliding bearing lubricating system and sliding bearing |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1807938A (en) * | 2006-01-13 | 2006-07-26 | 寿光市康跃增压器有限公司 | End sealing device for compressor of turbosupercharger |
| CN201339717Y (en) * | 2008-12-26 | 2009-11-04 | 艾志工业技术集团有限公司 | Integral type labyrinth seal |
| CN201412514Y (en) * | 2009-06-18 | 2010-02-24 | 桐乡市华强密封件有限公司 | Bearing sealing ring |
| CN201772065U (en) * | 2010-08-20 | 2011-03-23 | 上海市离心机械研究所有限公司 | Sealing ring for bearing seat |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5259628A (en) * | 1992-07-23 | 1993-11-09 | Reliance Electric Industrial Company | Seal assembly |
-
2010
- 2010-08-20 CN CN201010259064.5A patent/CN102374291B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1807938A (en) * | 2006-01-13 | 2006-07-26 | 寿光市康跃增压器有限公司 | End sealing device for compressor of turbosupercharger |
| CN201339717Y (en) * | 2008-12-26 | 2009-11-04 | 艾志工业技术集团有限公司 | Integral type labyrinth seal |
| CN201412514Y (en) * | 2009-06-18 | 2010-02-24 | 桐乡市华强密封件有限公司 | Bearing sealing ring |
| CN201772065U (en) * | 2010-08-20 | 2011-03-23 | 上海市离心机械研究所有限公司 | Sealing ring for bearing seat |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102374291A (en) | 2012-03-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN201772065U (en) | Sealing ring for bearing seat | |
| CN102713376B (en) | Slider | |
| KR20130094319A (en) | Spiral-grooved thrust bearing | |
| CN103711879B (en) | A kind of wind turbine gearbox mechanical labyrinth sealing configuration | |
| CN102374291B (en) | Improved structure of bearing base sealing ring | |
| CN104185756A (en) | Sliding component | |
| CN101603597B (en) | Friction ring of mechanical sealing device | |
| CN206904074U (en) | Damping ring with oil-stored hole | |
| CN103133696A (en) | Dynamic pressure mechanical sealing ring for automatically draining particle type fluids | |
| CN203670269U (en) | Open type water pump | |
| CN203962453U (en) | A kind of bearing | |
| CN203809998U (en) | Running machine lubricating structure | |
| CN1734110A (en) | Hydrodynamic pressure bearing | |
| JP2017026089A (en) | Tilting pad journal bearing | |
| CN202441865U (en) | Transmission case input shaft | |
| CN112128246B (en) | Axial small-hole normal-pressure water supply dynamic-static pressure spiral groove thrust bearing | |
| CN209892347U (en) | Engine crankcase cover | |
| CN209458406U (en) | A kind of shaft end mechanical seal structure | |
| JP3174644U (en) | Lubricating mechanism for vertical hook for sewing machine | |
| CN208107129U (en) | A kind of motorcycle gear box case lid and motorcycle gear box | |
| CN201428801Y (en) | Mechanism sealing device | |
| JP3179765U (en) | Internal gear pump | |
| CN202545820U (en) | Non-contact type mechanical sealing of shaping groove end face with backflow function | |
| JP2015062581A (en) | Washing machine | |
| CN204805490U (en) | Planetary gear thrust washer of adaptable automobile -used high rotational speed operating mode demand |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140723 Termination date: 20190820 |