CN201236886Y - Dynamic/static mixed bidirectional hydraulic thrust bearing - Google Patents
Dynamic/static mixed bidirectional hydraulic thrust bearing Download PDFInfo
- Publication number
- CN201236886Y CN201236886Y CNU2008200297060U CN200820029706U CN201236886Y CN 201236886 Y CN201236886 Y CN 201236886Y CN U2008200297060 U CNU2008200297060 U CN U2008200297060U CN 200820029706 U CN200820029706 U CN 200820029706U CN 201236886 Y CN201236886 Y CN 201236886Y
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- bearing
- oil film
- film wedge
- seat ring
- thrust bearing
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Abstract
The utility model relates to the technical field of the design and manufacture of bearing, which mainly relates to a hydro-hybrid double-way thrust bearing used for grinding and burnishing equipment. The hydro-hybrid double-way thrust bearing comprise a shaft washer (1) and a seat ring (2). The hydro-hybrid double-way thrust bearing is characterized in that an oil wedge groove (3) is formed on the corresponding contact surfaces of the shaft washer (1) and the seat ring (2), a centering rabbet (4) is formed on the seat ring (2) corresponding to the shaft washer (1), and the oil wedge groove (3) comprises a forward oil wedge (3-1), a backward oil wedge (3-2), an oil chamber (3-3) and an isolating groove (3-4). The function of double-way dynamic pressure is realized through the double-way oil wedge, and the function of hydrostatic bearing is realized through the oil chamber when the speed is zero. The hydro-hybrid double-way thrust bearing effectively avoids the influence of the error of the axial runout and the radial runout of the main shaft of a grinding disk to the rotation accuracy of the fluid bearing.
Description
Technical field:
The utility model relates to the design and fabrication technology field of bearing, relates generally to a kind of sound that is used for polishing grinding equipment and mixes the bidirectional hydraulic thrust-bearing.
Background technique:
High-precision polishing apparatus is in course of working, abrasive disk is when bearing very big pressure under it, also to guarantee very high running accuracy, often adopt the compound of thrust-bearing and radial bearing in traditional technology or use paired tapered roller bearing to reach its force request, but common thrust-bearing and the radial bearing limited and physical dimension of precision at the volley have narrow limitation, simultaneously because self gap and the axial runout of abrasive disk main shaft and the machining accuracy that run-out error all can greatly influence polishing apparatus, and bearing itself also is easy to wearing and tearing in the using process of equipment, influenced the proper functioning of entire equipment.
Summary of the invention:
The purpose of this utility model is to avoid the deficiencies in the prior art part and provides a kind of sound to mix the bidirectional hydraulic thrust-bearing, it utilizes the technical concept of thrust-bearing, simultaneously in conjunction with hydraulics, thereby effectively satisfied the usage requirement of high-precision polishing apparatus.
The purpose of this utility model can be by realizing by the following technical solutions: described sound is mixed the bidirectional hydraulic thrust-bearing, include blowout patche (1) and seat ring (2), it is characterized in that described blowout patche (1) is provided with oil film wedge groove (3) with the corresponding surface of contact of seat ring (2), seat ring (2) is gone up the corresponding centering seam (4) that is provided with blowout patche (1), and oil film wedge groove (3) includes forward oil film wedge (3-1), reverse oil film wedge (3-2), grease chamber (3-3) and isolation channel (3-4).Two-way oil film wedge is realized two-way dynamic pressure function, and the function of grease chamber's realization speed hydrostatic bearing when being zero.
The oil film wedge angle of described forward oil film wedge (3-1) and reverse oil film wedge (3-2) is less than 1 °.Be provided with oil-feed port (5) in the grease chamber (3-3), the interior outside of oil film wedge groove (3) is provided with return opening (6).Pressure in the grease chamber (3-3) is 0.3～0.5Mpa.
The beneficial effects of the utility model are, described sound is mixed the bidirectional hydraulic thrust-bearing, when the rotational speed of lower wall main shaft lower or main frame is in startup, when stopping, can utilize the lubricated static pressure oil film that forms of forced feed, when the lower wall main shaft reaches certain rotational speed, relative movement between rubbing surface forms the pressure oil film wedge, form dynamic pressure oil film, thereby in whole process, form the neat liquid friction, because oil film has bigger bearing capacity and absorbing performance preferably, so effectively improved the running accuracy of time abrasive disk.Can also torsional moment be passed to fluid bearing by flexiblesystem with abrasive disk main shaft at present, avoid the influence of the axial runout of time abrasive disk main shaft and run-out error the fluid bearing rotation precision.
Description of drawings:
Fig. 1 is the utility model embodiment's a structural representation;
Fig. 2 (a) looks schematic representation for the structure master of the blowout patche (1) among the utility model Fig. 1;
Fig. 2 (b) shows structural representation for the A-A among the utility model Fig. 2 cuts open;
Fig. 3 is the E place partial structurtes enlarged diagram among the utility model Fig. 2;
Fig. 4 shows structural representation for the B-B among the utility model Fig. 2 cuts open;
Fig. 5 (a) looks schematic representation for the structure master of the seat ring (2) among the utility model Fig. 1;
Fig. 5 (b) shows structural representation for the B-B of the Fig. 5 (a) among the utility model Fig. 1 cuts open;
Embodiment:
Be described in further detail below in conjunction with the most preferred embodiment shown in the accompanying drawing:
See Fig. 1,2,3,4,5, described sound is mixed the bidirectional hydraulic thrust-bearing, include blowout patche 1 and seat ring 2, it is characterized in that described blowout patche 1 is provided with oil film wedge groove 3 with the corresponding surface of contact of seat ring 2, with the blowout patche 1 corresponding centering seam 4 that is provided with, oil film wedge groove 3 includes forward oil film wedge 3-1, reverse oil film wedge 3-2, the 3-3 of grease chamber and isolation channel 3-4 on the seat ring 2.Two-way oil film wedge is realized two-way dynamic pressure function, and the function of grease chamber's realization speed hydrostatic bearing when being zero.
The oil film wedge angle of described forward oil film wedge 3-1 and reverse oil film wedge 3-2 is less than 1 °.Be provided with oil-feed port 5 in the 3-3 of grease chamber, the interior outside of oil film wedge groove 3 is provided with return opening 6.Pressure in the 3-3 of grease chamber is 0.3～0.5Mpa.
During enforcement, blowout patche 1 is installed on the supporting base 7, seat ring 2 is installed on the supporting disk 8, and pressure oil enters oil film wedge groove 3 by oil-feed port 5, thereby it is lubricated to form forced feed, when the lower wall main shaft reaches certain rotational speed, relative movement between rubbing surface forms the pressure oil film wedge, and movement parts is held up, and two rubbing surfaces are isolated, the friction of formation neat liquid, dynamic pressure this moment plays the main support effect.When the rotational speed of lower wall main shaft lower or main frame is in startup, when stopping, can not set up effective carrying oil film wedge between rubbing surface, lubricant oil under certain pressure under the pressure that produces on the effective bearing area between rubbing surface can balance the weight of abrasive disk assembly and last disc system applied pressure, this moment, static pressure played a major role, and bearing still has very big bearing capacity.Because oil film has bigger bearing capacity and absorbing performance preferably, so effectively improved the running accuracy of time abrasive disk.Can also torsional moment be passed to fluid bearing by flexiblesystem with abrasive disk main shaft at present, avoid the influence of the axial runout of time abrasive disk main shaft and run-out error the fluid bearing rotation precision.
Claims (4)
1. a sound is mixed the bidirectional hydraulic thrust-bearing, include blowout patche (1) and seat ring (2), it is characterized in that described blowout patche (1) is provided with oil film wedge groove (3) with the corresponding surface of contact of seat ring (2), seat ring (2) is gone up the corresponding centering seam (4) that is provided with blowout patche (1), and oil film wedge groove (3) includes forward oil film wedge (3-1), reverse oil film wedge (3-2), grease chamber (3-3) and isolation channel (3-4).
2. sound as claimed in claim 1 is mixed the bidirectional hydraulic thrust-bearing, it is characterized in that: the oil film wedge angle of described forward oil film wedge (3-1) and reverse oil film wedge (3-2) is less than 1 °.
3. sound as claimed in claim 1 is mixed the bidirectional hydraulic thrust-bearing, and it is characterized in that: be provided with oil-feed port (5) in described grease chamber (3-3), the interior outside of oil film wedge groove (3) is provided with return opening (6).
4. sound as claimed in claim 3 is mixed the bidirectional hydraulic thrust-bearing, it is characterized in that: the pressure in described grease chamber (3-3) is 0.3～0.5Mpa.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008200297060U CN201236886Y (en) | 2008-07-15 | 2008-07-15 | Dynamic/static mixed bidirectional hydraulic thrust bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008200297060U CN201236886Y (en) | 2008-07-15 | 2008-07-15 | Dynamic/static mixed bidirectional hydraulic thrust bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201236886Y true CN201236886Y (en) | 2009-05-13 |
Family
ID=40649626
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008200297060U Expired - Lifetime CN201236886Y (en) | 2008-07-15 | 2008-07-15 | Dynamic/static mixed bidirectional hydraulic thrust bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201236886Y (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103438097A (en) * | 2013-08-30 | 2013-12-11 | 哈尔滨理工大学 | Two-way dynamic-static pressure mixture lubrication thrust bearing |
| CN103921208A (en) * | 2013-01-15 | 2014-07-16 | 云南飞隆劳尔设备有限公司 | Hydrostatic bearing for optical plane polishing machine tool |
| CN106594076A (en) * | 2016-12-07 | 2017-04-26 | 北京工业大学 | Dynamic and static pressure mixed fan-shaped oil pad |
| CN106763153A (en) * | 2017-01-19 | 2017-05-31 | 重庆江增船舶重工有限公司 | A kind of axial flow turbine booster floating thrust bearing |
| CN110107595A (en) * | 2019-04-11 | 2019-08-09 | 西安理工大学 | By the Hydrodynamic-static Thrust Bearings in Water Turbo of tilting bush and static-pressure oil chamber sharing lood |
-
2008
- 2008-07-15 CN CNU2008200297060U patent/CN201236886Y/en not_active Expired - Lifetime
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103921208A (en) * | 2013-01-15 | 2014-07-16 | 云南飞隆劳尔设备有限公司 | Hydrostatic bearing for optical plane polishing machine tool |
| CN103921208B (en) * | 2013-01-15 | 2016-05-11 | 云南飞隆劳尔设备有限公司 | Hydrostatic bearing for optical plane polishing machine tool |
| CN103438097A (en) * | 2013-08-30 | 2013-12-11 | 哈尔滨理工大学 | Two-way dynamic-static pressure mixture lubrication thrust bearing |
| CN103438097B (en) * | 2013-08-30 | 2016-02-10 | 哈尔滨理工大学 | Two-way hybrid lubricating thrust bearing |
| CN106594076A (en) * | 2016-12-07 | 2017-04-26 | 北京工业大学 | Dynamic and static pressure mixed fan-shaped oil pad |
| CN106763153A (en) * | 2017-01-19 | 2017-05-31 | 重庆江增船舶重工有限公司 | A kind of axial flow turbine booster floating thrust bearing |
| CN106763153B (en) * | 2017-01-19 | 2019-04-19 | 重庆江增船舶重工有限公司 | A kind of axial flow turbine booster floating thrust bearing |
| CN110107595A (en) * | 2019-04-11 | 2019-08-09 | 西安理工大学 | By the Hydrodynamic-static Thrust Bearings in Water Turbo of tilting bush and static-pressure oil chamber sharing lood |
| CN110107595B (en) * | 2019-04-11 | 2020-07-28 | 西安理工大学 | Dynamic and static pressure thrust bearing jointly borne by tilting pad and static pressure oil cavity |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Lanzhou Reed Equipment Manufacturing Co., Ltd. Assignor: Hangzhou Rapid Industrial (Group) Co., Ltd. Contract record no.: 2011640000010 Denomination of utility model: Dynamic/static mixed bidirectional hydraulic thrust bearing Granted publication date: 20090513 License type: Exclusive License Record date: 20110822 |
|
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20090513 |