CA1197541A - Hydrostatic bearing - Google Patents
Hydrostatic bearingInfo
- Publication number
- CA1197541A CA1197541A CA000403699A CA403699A CA1197541A CA 1197541 A CA1197541 A CA 1197541A CA 000403699 A CA000403699 A CA 000403699A CA 403699 A CA403699 A CA 403699A CA 1197541 A CA1197541 A CA 1197541A
- Authority
- CA
- Canada
- Prior art keywords
- bearing
- channels
- movement
- bearing surface
- length
- 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
Links
Classifications
-
- 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0651—Details of the bearing area per se
- F16C32/0659—Details of the bearing area per se of pockets or grooves
-
- 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0662—Details of hydrostatic bearings independent of fluid supply or direction of load
- F16C32/0666—Details of hydrostatic bearings independent of fluid supply or direction of load of bearing pads
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
A hydrostatic bearing for mounting a member movable in a direction relative to the bearing has a bearing surface provided with a plurality of closed loop channels enclosing bearing surface lands and arranged symmetrically relative to the centre of the bearing surface and supplied with oil under pressure. The lands have a uniform width nor-mal to the direction of movement and a length in the direc-tion of movement at least as great as their width, the area of the lands being at least as great as that of the channels enclosing them and the total area of the channels amounting at most to about 25% of the total area of the bearing sur-face.
A hydrostatic bearing for mounting a member movable in a direction relative to the bearing has a bearing surface provided with a plurality of closed loop channels enclosing bearing surface lands and arranged symmetrically relative to the centre of the bearing surface and supplied with oil under pressure. The lands have a uniform width nor-mal to the direction of movement and a length in the direc-tion of movement at least as great as their width, the area of the lands being at least as great as that of the channels enclosing them and the total area of the channels amounting at most to about 25% of the total area of the bearing sur-face.
Description
7~
The invention relates to a hydrostatic bea~ing with a bearing segment which is supported so as -to be capable of tumbling motion, the bearing surface thereof having a plurality of enclosed channels which are arranged symmetric-ally relative to the centre of the bearing surface and aresupplied with oil under pressure.
Hydrosta-tic bearings are used especially Eor the radial and axial mounting of heavy rota-ting machine parts.
A supporting oil film is produced by oil under pressure which is supplied -to the chann01s arranged in the bearing surEace of the hydrostatic bearing.
In a known hydros-tatic bearing of the general -type referred to is described in German Paten-t No. 20 39 720 and has a bearing surface with four sector-shaped oil reser-~oirs which are arranged symmetrically relative to the centreand are each formed by an approximately -triangular channel and a raised surface which is also approximately triangular and is enclosed in this channel. The raised surface of each of these sector-shaped oil reservGirs is substantially smaller than the surface of the channel surrounding i-t.
~ significant disadvantage of this known hydro-static bearing is its poor emergency operating character-istics in the even-t of a failure of the pressurized oil supply. Because of the relatively small surface and above all because of the shape and arrangement of the raised sur-faces enclosed by -the channels an inadequate lubricating film is produced be-tween the supported element and the bear-ing surface of the bearing segment in the event of a failure of the pressurized oil supply in the known bearing. This there~ore leads to severe metal abrasion with all -the dis-advantages resul-ting therefrom and from the high surface pressure.
An object of the invention, therefore, is to miti-gate these disadvantages and to provide a hydrostatic bearing wihich has particularly good emergency operating character-istics with low surface pressure.
The present invention provides a hydrostatic bear-7~
ing for mounting a member movable in a direction relative-to the bearing and having a bearing surface provided with a plurality of closed loop channels enclosing bearing sur-face lands, the channels being arranged symme-trically rela-S tive to the cen-tre of the bearing surface and supplied with oil under pressure, wherein the lands have a uniform width normal to the direction of movement 9 the lands have a length in the direction of movement a-t least as great as -their width, the area of the lands is at least as great as that 1.0 of the channels enclosing them, and the total area of the channels amounts at most to about 25~ oE the -total area of the bearing surface.
The channels and the lands have a favourable eEEec-t on the formation of a supporting film of ~ubricating oil on a relatively large surface of the bearing segment in the event of failure of the pressurized oil supply. In particular, the construction of the lands within the channels which enclose them ensures that, in the event of failure of the pressurized oil supply, an adequate hydrodynamic "pressure peak", which absorbs a substantial proportion of the bearing forces, builds up over this part of the bear-ing surface of the bearing segment.
An embodiment of the present invention is explained in greater detail below wi~h reference to the drawings, in which:
Figure 1 shows a plan view of the bearing surface of a hydrostatic bearing embodying the invention (with schematically indicated arrangements for pressurized oil supply), and Figure 2 shows a section along the line II-II in Figure 1.
Of the hydrostatic bearing only the bearing segment 1 which i.s supported so as to be capable o~ tumbling motion is shown in the drawings. Its bearing surface 2 contains a plurality of closed loop channels 3, 4, 5, 6 which are arranged symmetrically relative to the centre of the bearing surface and are supplied with oil under pressure. Each channel encloses a rectangular raised surEace or land 7, 8, 9 and 10, respectively.
A bore 11 is arranged in the centre of the beariny and communicates with -the surface thereof. In addi-tion bores 12r 13r 14 and 15, respectively, open into -the in-dividual channels 3 to 6. The bores 12, 13, 14 and 15 serve to supply oil under pressure to the channels 3, 4, 5 and 6, whereas a vertical bore lla in communication with the bearing surface a-t its centre enables excess oil to be diverted to the underside of the bearing segment 1 and for pressure relief. If desired, a -trans~erse passage in com-munication with the bore lla can be used to -transfer oil to additional bearing segments in a multiple-segment bearlng.
Oil is supplied to the channels 3 to 6 via two main pumps 16, 17 and two oil stream diverters 18, 19, 20, 21. The channels 4 and 6 which lie diagonally opposite one another are supplied by the main pump 16 via the diverters 18, 19 whilst the main pump 17 and the diverters 20, 21 supply the channels 3 and 5, which are also dia-gonally opposite one another. Thus~ even if one of the two main pumps fails, an approximately symmetrical supply of oil under pressure to the bearing segment is ensured and any tendency to tilting is counteracted.
The supported part (for example a heavy dxum~, which is not shown, rotates in the direction of the arrow 22.
The following abbreviations are used for the di-mensioning and arrangement of the individual elements of the bearing surEace:
A = length of the bearing surface in the direction of move ment, B = width of the bearing surface at right angles to the direction o:E movement, Ta - length of the channels in the direction of movement, 5 Tb = length of the channels a-t right angles to the direction of movement, a = distance of the channels from the edge of the bearing surface lying at right angles to the direction of movement, b = distance of the channels :Erom the edge of the bearing surface lying parallel to the direction of movement, S = distance between adjacent channels in the direc-tion a of movement, Sb = distance between adjacent channels at right angles to the direction oE movement, ta = length of the raised surfaces in the direction of move-ment, tb ~ length of -the raised surfaces at right angles to the direction oE movement, dm ~ diameter of the bore provided in the cen-tre of the bearing surface, 5 e = distance of -the periphery of this bore from -the neigh-bouring corner of the channels.
The following values have proved ideal in order to achieve optimum emergency operating characteristics (in the event of failure of the pressurized oil supply):
B = 1.33 .... 1.85 T T = 0.38 ~.. O 0.5 b = l a = 1.3 .... .2 a Sa S = 1.5 .... 2 t t Ta Tb = 0.51 .... 0.67 a b tb = 1.4 .... 2.6 a b ta . tb) = ¦0.18 .... 0.22) A B
dm ~ = 1.6 .... 2.6
The invention relates to a hydrostatic bea~ing with a bearing segment which is supported so as -to be capable of tumbling motion, the bearing surface thereof having a plurality of enclosed channels which are arranged symmetric-ally relative to the centre of the bearing surface and aresupplied with oil under pressure.
Hydrosta-tic bearings are used especially Eor the radial and axial mounting of heavy rota-ting machine parts.
A supporting oil film is produced by oil under pressure which is supplied -to the chann01s arranged in the bearing surEace of the hydrostatic bearing.
In a known hydros-tatic bearing of the general -type referred to is described in German Paten-t No. 20 39 720 and has a bearing surface with four sector-shaped oil reser-~oirs which are arranged symmetrically relative to the centreand are each formed by an approximately -triangular channel and a raised surface which is also approximately triangular and is enclosed in this channel. The raised surface of each of these sector-shaped oil reservGirs is substantially smaller than the surface of the channel surrounding i-t.
~ significant disadvantage of this known hydro-static bearing is its poor emergency operating character-istics in the even-t of a failure of the pressurized oil supply. Because of the relatively small surface and above all because of the shape and arrangement of the raised sur-faces enclosed by -the channels an inadequate lubricating film is produced be-tween the supported element and the bear-ing surface of the bearing segment in the event of a failure of the pressurized oil supply in the known bearing. This there~ore leads to severe metal abrasion with all -the dis-advantages resul-ting therefrom and from the high surface pressure.
An object of the invention, therefore, is to miti-gate these disadvantages and to provide a hydrostatic bearing wihich has particularly good emergency operating character-istics with low surface pressure.
The present invention provides a hydrostatic bear-7~
ing for mounting a member movable in a direction relative-to the bearing and having a bearing surface provided with a plurality of closed loop channels enclosing bearing sur-face lands, the channels being arranged symme-trically rela-S tive to the cen-tre of the bearing surface and supplied with oil under pressure, wherein the lands have a uniform width normal to the direction of movement 9 the lands have a length in the direction of movement a-t least as great as -their width, the area of the lands is at least as great as that 1.0 of the channels enclosing them, and the total area of the channels amounts at most to about 25~ oE the -total area of the bearing surface.
The channels and the lands have a favourable eEEec-t on the formation of a supporting film of ~ubricating oil on a relatively large surface of the bearing segment in the event of failure of the pressurized oil supply. In particular, the construction of the lands within the channels which enclose them ensures that, in the event of failure of the pressurized oil supply, an adequate hydrodynamic "pressure peak", which absorbs a substantial proportion of the bearing forces, builds up over this part of the bear-ing surface of the bearing segment.
An embodiment of the present invention is explained in greater detail below wi~h reference to the drawings, in which:
Figure 1 shows a plan view of the bearing surface of a hydrostatic bearing embodying the invention (with schematically indicated arrangements for pressurized oil supply), and Figure 2 shows a section along the line II-II in Figure 1.
Of the hydrostatic bearing only the bearing segment 1 which i.s supported so as to be capable o~ tumbling motion is shown in the drawings. Its bearing surface 2 contains a plurality of closed loop channels 3, 4, 5, 6 which are arranged symmetrically relative to the centre of the bearing surface and are supplied with oil under pressure. Each channel encloses a rectangular raised surEace or land 7, 8, 9 and 10, respectively.
A bore 11 is arranged in the centre of the beariny and communicates with -the surface thereof. In addi-tion bores 12r 13r 14 and 15, respectively, open into -the in-dividual channels 3 to 6. The bores 12, 13, 14 and 15 serve to supply oil under pressure to the channels 3, 4, 5 and 6, whereas a vertical bore lla in communication with the bearing surface a-t its centre enables excess oil to be diverted to the underside of the bearing segment 1 and for pressure relief. If desired, a -trans~erse passage in com-munication with the bore lla can be used to -transfer oil to additional bearing segments in a multiple-segment bearlng.
Oil is supplied to the channels 3 to 6 via two main pumps 16, 17 and two oil stream diverters 18, 19, 20, 21. The channels 4 and 6 which lie diagonally opposite one another are supplied by the main pump 16 via the diverters 18, 19 whilst the main pump 17 and the diverters 20, 21 supply the channels 3 and 5, which are also dia-gonally opposite one another. Thus~ even if one of the two main pumps fails, an approximately symmetrical supply of oil under pressure to the bearing segment is ensured and any tendency to tilting is counteracted.
The supported part (for example a heavy dxum~, which is not shown, rotates in the direction of the arrow 22.
The following abbreviations are used for the di-mensioning and arrangement of the individual elements of the bearing surEace:
A = length of the bearing surface in the direction of move ment, B = width of the bearing surface at right angles to the direction o:E movement, Ta - length of the channels in the direction of movement, 5 Tb = length of the channels a-t right angles to the direction of movement, a = distance of the channels from the edge of the bearing surface lying at right angles to the direction of movement, b = distance of the channels :Erom the edge of the bearing surface lying parallel to the direction of movement, S = distance between adjacent channels in the direc-tion a of movement, Sb = distance between adjacent channels at right angles to the direction oE movement, ta = length of the raised surfaces in the direction of move-ment, tb ~ length of -the raised surfaces at right angles to the direction oE movement, dm ~ diameter of the bore provided in the cen-tre of the bearing surface, 5 e = distance of -the periphery of this bore from -the neigh-bouring corner of the channels.
The following values have proved ideal in order to achieve optimum emergency operating characteristics (in the event of failure of the pressurized oil supply):
B = 1.33 .... 1.85 T T = 0.38 ~.. O 0.5 b = l a = 1.3 .... .2 a Sa S = 1.5 .... 2 t t Ta Tb = 0.51 .... 0.67 a b tb = 1.4 .... 2.6 a b ta . tb) = ¦0.18 .... 0.22) A B
dm ~ = 1.6 .... 2.6
Claims (10)
1. A hydrostatic bearing for mounting a member movable in a direction relative to said bearing and having a bearing surface provided with a plurality of closed loop channels enclosing bearing surface lands, said channels being arranged symmetrically relative to the centre of said bearing surface and supplied with oil under pressure, wherein:
(a) the lands have a uniform width normal to said direction of movement;
(b) the lands have a length in said direction of movement at least as great as their width;
(c) the area of the lands is at least as great as that of the channels enclosing them; and (d) the total area of the channels amounts at most to about 25% of tha total area of the bearing surface.
(a) the lands have a uniform width normal to said direction of movement;
(b) the lands have a length in said direction of movement at least as great as their width;
(c) the area of the lands is at least as great as that of the channels enclosing them; and (d) the total area of the channels amounts at most to about 25% of tha total area of the bearing surface.
2. A bearing according to claim 1 wherein the bearing surface has four quadrangular lands each of which is enclosed by a channel.
3. A bearing according to claim 2 wherein the ratio of A to B is between about 1.33 and 1.85; wherein:
A = the length of the bearing surface in the direction of movement; and B = the width of the bearing surface normal to the direction of movement.
A = the length of the bearing surface in the direction of movement; and B = the width of the bearing surface normal to the direction of movement.
4. A bearing according to claim 2 wherein the relationship is between about 0.38 - 0.5;
the relationship ? is about l;
the relationship ? is between about 1.3 -2; and the relationship ? is between about 1.5 and 2; wherein:
A = the length of the bearing surface in the direction of movement; and B = the width of the bearing surface normal to the direction of movement;
Ta = the length of the channels in the direction of move-ment;
Tb = the length of the channels normal to the direction of movement;
a - the distance of the channels from that edge of the bearing surface lying at right angles to the direction of movement;
b = the distance of the channels from that edge of the bear-ing surface lying parallel to the direction of movement;
Sa = the distance between adjacent channels in the direction of movement; and Sb a the distance between adjacent channels at right angles to the direction of movement.
the relationship ? is about l;
the relationship ? is between about 1.3 -2; and the relationship ? is between about 1.5 and 2; wherein:
A = the length of the bearing surface in the direction of movement; and B = the width of the bearing surface normal to the direction of movement;
Ta = the length of the channels in the direction of move-ment;
Tb = the length of the channels normal to the direction of movement;
a - the distance of the channels from that edge of the bearing surface lying at right angles to the direction of movement;
b = the distance of the channels from that edge of the bear-ing surface lying parallel to the direction of movement;
Sa = the distance between adjacent channels in the direction of movement; and Sb a the distance between adjacent channels at right angles to the direction of movement.
5. A bearing according to claim 2, 3 or 4 wherein:
the relationship is between about 0.51 and 0.67; and the relationship is between about 1.4 - 2.6; wherein:
ta = the length of the bearing lands in the direction of movement;
tb = the length of the bearing lands at right angles to the direction of movement;
Ta = the length of the channels in the direction of move-ment; and Tb = the length of the channels at right angles to the direction of movement.
the relationship is between about 0.51 and 0.67; and the relationship is between about 1.4 - 2.6; wherein:
ta = the length of the bearing lands in the direction of movement;
tb = the length of the bearing lands at right angles to the direction of movement;
Ta = the length of the channels in the direction of move-ment; and Tb = the length of the channels at right angles to the direction of movement.
6. A bearing according to claim 2, 3 or 4 wherein the total surface area of channels amounts to between about 18% - 22% of the total bearing surface area.
7. A bearing according to claim 2 wherein said bearing has a bore in communication with said bearing sur-face at its center.
8. A bearing according to claim 7 wherein the relationship is between about 1.5 and 3; and wherein:
dm = the diameter of the bore;
e = the distance from the periphery of the bore to the ad-jacent corner of each of the channels; and .pi. 3.14.
dm = the diameter of the bore;
e = the distance from the periphery of the bore to the ad-jacent corner of each of the channels; and .pi. 3.14.
9. A bearing according to claim 8 wherein said relationship is between about 2.3 and 2.6.
10. A bearing according to claim 2, 3 or 4 in-cluding a number of oil pumps for supplying said channels with oil, those channels situated on diagonally opposite sides of the center of said bearing surface being supplied with oil from the same one of said pump.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19813128186 DE3128186A1 (en) | 1981-07-16 | 1981-07-16 | HYDROSTATIC BEARING |
| DEP3128186.9 | 1981-07-16 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1197541A true CA1197541A (en) | 1985-12-03 |
Family
ID=6137090
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000403699A Expired CA1197541A (en) | 1981-07-16 | 1982-05-26 | Hydrostatic bearing |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP0070375B1 (en) |
| AT (1) | ATE12539T1 (en) |
| BR (1) | BR8204117A (en) |
| CA (1) | CA1197541A (en) |
| DE (2) | DE3128186A1 (en) |
| ES (1) | ES8305471A1 (en) |
| ZA (1) | ZA823679B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| IT1284063B1 (en) * | 1996-06-25 | 1998-05-08 | Voith Riva Hydro S P A | HYDROSTATIC SUPPORT SUPPORT IN PARTICULAR FOR HYDRAULIC MACHINES OF HYDROELECTRIC GROUPS |
| DE19826519C2 (en) * | 1998-06-15 | 2000-05-18 | Freundeskreis Des Lehrstuhles | Hydrostatic guidance |
| US20040042689A1 (en) | 2002-08-30 | 2004-03-04 | Hardinge Inc. | Hydrostatic bearing for linear motion guidance |
| ITVR20090092A1 (en) * | 2009-06-25 | 2010-12-26 | Raffaele Tomelleri | HYDROSTATIC SUPPORT FOR LARGE STRUCTURES AND IN PARTICULAR FOR LARGE TELESCOPES. |
| CN111828477B (en) * | 2019-12-27 | 2022-05-31 | 哈尔滨理工大学 | Oil cavity area optimization method for oil pad tilting type double-rectangular-cavity hydrostatic thrust bearing |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2578711A (en) * | 1947-06-27 | 1951-12-18 | Cincinnati Milling Machine Co | Bearing |
| NL152774A (en) * | 1950-01-24 | |||
| US3053583A (en) * | 1960-03-10 | 1962-09-11 | Monarch Machine Tool Co | Air bearing |
| CH519661A (en) * | 1969-08-21 | 1972-02-29 | Oerlikon Buehrle Ag | Hydrostatic plain bearing |
| US3781070A (en) * | 1972-05-18 | 1973-12-25 | Cincinnati Milacron Heald | Machine tool |
| DE2901064A1 (en) * | 1979-01-12 | 1980-08-07 | Krupp Polysius Ag | Heavy duty bearing for large shaft - has hydrostatic bearings on either side of hydrodynamic bearing |
-
1981
- 1981-07-16 DE DE19813128186 patent/DE3128186A1/en not_active Withdrawn
-
1982
- 1982-05-26 CA CA000403699A patent/CA1197541A/en not_active Expired
- 1982-05-27 AT AT82104665T patent/ATE12539T1/en not_active IP Right Cessation
- 1982-05-27 DE DE8282104665T patent/DE3262859D1/en not_active Expired
- 1982-05-27 EP EP82104665A patent/EP0070375B1/en not_active Expired
- 1982-05-27 ZA ZA823679A patent/ZA823679B/en unknown
- 1982-07-14 ES ES513975A patent/ES8305471A1/en not_active Expired
- 1982-07-15 BR BR8204117A patent/BR8204117A/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| ATE12539T1 (en) | 1985-04-15 |
| ES513975A0 (en) | 1983-04-01 |
| EP0070375B1 (en) | 1985-04-03 |
| EP0070375A1 (en) | 1983-01-26 |
| DE3128186A1 (en) | 1983-02-03 |
| DE3262859D1 (en) | 1985-05-09 |
| BR8204117A (en) | 1983-07-12 |
| ZA823679B (en) | 1983-03-30 |
| ES8305471A1 (en) | 1983-04-01 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |