CA2020193C - Aerodynamic plain bearing - Google Patents
Aerodynamic plain bearingInfo
- Publication number
- CA2020193C CA2020193C CA002020193A CA2020193A CA2020193C CA 2020193 C CA2020193 C CA 2020193C CA 002020193 A CA002020193 A CA 002020193A CA 2020193 A CA2020193 A CA 2020193A CA 2020193 C CA2020193 C CA 2020193C
- Authority
- CA
- Canada
- Prior art keywords
- segments
- plain bearing
- damping
- bearing
- spring steel
- 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
- 238000013016 damping Methods 0.000 claims abstract description 18
- 229910000639 Spring steel Inorganic materials 0.000 claims description 8
- 238000000576 coating method Methods 0.000 claims description 7
- 239000011248 coating agent Substances 0.000 claims description 6
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims description 3
- 229910052799 carbon Inorganic materials 0.000 claims description 3
- 239000000463 material Substances 0.000 claims description 2
- 239000002356 single layer Substances 0.000 claims 1
- 238000009434 installation Methods 0.000 abstract description 5
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 238000009760 electrical discharge machining Methods 0.000 description 1
- 239000000835 fiber Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- XOUPWBJVJFQSLK-UHFFFAOYSA-J titanium(4+);tetranitrite Chemical compound [Ti+4].[O-]N=O.[O-]N=O.[O-]N=O.[O-]N=O XOUPWBJVJFQSLK-UHFFFAOYSA-J 0.000 description 1
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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/024—Sliding-contact bearings for exclusively rotary movement for radial load only with flexible leaves to create hydrodynamic wedge, e.g. radial foil bearings
-
- 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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/02—Sliding-contact bearings
-
- 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
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Support Of The Bearing (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
The invention concerns an aerodynamic plain bearing for shafts (1) rotating at high rotation speeds, with a bearing housing (4) having a cylindrical bore (3) and with a tangentially attached, elastic and damping structure (2) having segments (2" or 2a) which is supported at a plurality of circumferential points (2') in bearing housing (4) and forms a multiple converging running gap (6) with shaft (1) and damping gap (5) with bearing housing (4). In order to make do with as few components as possible and as little radial installation space as possible, provision is made for segments (2" or 2a) of the structure to be thin-walled, elastic sleeve sections with a uniform or profiled wall thickness and a low coefficient of friction, which are simultaneously damping and spring elements.
Description
. 2020 ~9 3 Aerodynamic Plain Bearing The invention concerns an aerodynamic plain bearing.
A plain bearing of this kind is known from DE-OS 35 44 392, in which a shaft is mounted on substructures, which have defined spring stiffness values and damping capabilities, distributed around the circumference.
Located between each of the substructures and the bearing housing is a damping gap, which gives the plain bearing a certain damping characteristic. Each of the substructures consists of a sliding segment and a spring element, which are located radially behind one another, with the rigid sliding segment possibly being supported by an external extension on the spring element. This configuration necessitates a relatively large number of parts, which moreover require a correspondingly large - installation space in the radial axis and lead to relatively large total tolerances.
It is also known, from DE-PS 29 09 973, in an aerodynamic plain bearing, to use two thin-walled elastic sleeves one inside the other, the inner one of which serves as the bearing shell and is supported by the outer sleeve by means of webs. The outer sleeve, which provides elastic and damping support for the inner sleeve, is in turn supported by means of webs on the inner wall of the housing bore. The original circular cross section of the inner sleeve is~deformed, because of the fact that the elastic and damping structure is clamped in the housing bore, in such a way that four wedge-shaped constrictions are created in the running gap on the circumference of the bearing. This design is also complex, requires more radial installation space, and leads to relatively large total tolerances.
The object of the invention is therefore to create an aerodynamic plain bearing according to the preamble of Claim 1, which can make do with as few components as . --, ~ Z O Z 0 1 ~- ~
-possible and as little radial installation space as possible.
This object is achieved according to the characterizing portion of Claim 1.
The number of components is considerably reduced by the fact that the damping and spring element are combined into one, as a result of which the radial installation space can also be significantly decreased. At the same time, this means lower total tolerances. This design is therefore also associated with considerable advantages in terms of production, costs, and function, especially when a one-piece spring sleeve made of spring steel is used as the damping and spring element.
Additional embodiments of the invention are indicated in the description below and in the subsidiary Claims.
The invention will be described below in more detail, with reference to the exemplary embodiments illustrated in the attached drawings.
Figure 1 shows a section through an aerodynamic radial bearing in a first embodiment.
Figure 2 shows a portion of a section through an aerodynamic radial bearing in a second embodiment.
In the embodiment of an aerodynamic radial bearing illustrated in Figure 1, a shaft 1 is mounted by means of a thin-walled elastic spring sleeve 2, which has a uniform or profiled wall thickness, in a cylindrical bore 3 of a bearing housing 4.
Spring sleeve 2 is made of spring steel, and is slightly noncircular in section so that at several (at least three, in this case four) support points 2' on the outer circumference it touches the wall of bore 3 and thus has a somewhat "polygonall' shape so that sickle-shaped damping gaps 5 are formed between the wall of bore 3 and those spring segments 2" of spring sleeve 2' which are located between each two adjacent support points 2' . 202019 3 -and have a radius of curvature R greater than the radius of bore 3, with the center point lying outside axis A of shaft 1. Located between the inner circumference of spring sleeve 2 and shaft 1 is a running gap 6 which, corresponding to the "polygonal" shape of spring sleeve 2, is noncircular, i.e. has wedge-shaped constrictions.
Spring sleeve 2 has a tangential attachment 7 to one of the support points 2' in the form of a screw accommodated by bearing housing 3, the free end of which extends into a corresponding opening or recess in spring sleeve 2. Instead of a screw, a pin or the like can also be used.
A spring sleeve 2 of this type can easily be produced from a section of a spring steel tube that is pressed with a suitable tool into the "polygonal" shape.
It may also possibly be cut to length from a suitably shaped or profiled tube. It is important to maintain a certain uniform wall thickness or a precisely defined thickness distribution, so that the damping gap 5 and running gap 6 can be precisely defined to correspond to the shaft and bearing diameter. A profiled spring sleeve 2 or corresponding individual segment 2a can also be manufactured by electrical discharge machining.
As indicated by the embodiment in Figure 2, a plurality of tangential attachments 7 can also be provided. These can be provided at all support points 2' at which spring sleeve 2 contacts the wall of bore 3.
It is also possible to use, instead of spring sleeve 2, corresponding separate spring segments 2a in a number corresponding to the number of support points 2' (four, in the case illustrated), which are then supported at tangential attachments 7. In this case tangential attachments 7 can be configured as axial ribs projecting into bore 3. The individual spring segments 2a can, adjacent to the tangential attachments, be bent slightly . Z020 19 3 -towards the outer circumference, or have a suitable profile.
Spring sleeve 2 or separate spring segments 2a are advantageously provided with a suitable coating, which is elastic and which gives spring sleeve 2 or separate spring segments 2a a low coefficient of friction.
Suitable coatings include diamond-like carbon, which can be also be applied to shaft 1, titanium nitrite [sic], or another hard, wear-resistant, low-friction coating. In the case of a shaft 1 made of hard material or having a hard, wear-resistant coating, a relatively soft coating on spring sleeve 2 or spring segments 2a is also a possibility. This could compensate for small dust or dirt particles without appreciably restricting the function. A hard coating on spring sleeve 2 or spring segments 2a and a soft-coated shaft 1 is also possible.
Spring sleeve 2 or individual spring segments 2a can also be made of artificial carbon and acquire the necessary flexibility, needed over the long term when the damping gap width deflects, by means of fiber reinforcement (CFC).
A plain bearing of this kind is known from DE-OS 35 44 392, in which a shaft is mounted on substructures, which have defined spring stiffness values and damping capabilities, distributed around the circumference.
Located between each of the substructures and the bearing housing is a damping gap, which gives the plain bearing a certain damping characteristic. Each of the substructures consists of a sliding segment and a spring element, which are located radially behind one another, with the rigid sliding segment possibly being supported by an external extension on the spring element. This configuration necessitates a relatively large number of parts, which moreover require a correspondingly large - installation space in the radial axis and lead to relatively large total tolerances.
It is also known, from DE-PS 29 09 973, in an aerodynamic plain bearing, to use two thin-walled elastic sleeves one inside the other, the inner one of which serves as the bearing shell and is supported by the outer sleeve by means of webs. The outer sleeve, which provides elastic and damping support for the inner sleeve, is in turn supported by means of webs on the inner wall of the housing bore. The original circular cross section of the inner sleeve is~deformed, because of the fact that the elastic and damping structure is clamped in the housing bore, in such a way that four wedge-shaped constrictions are created in the running gap on the circumference of the bearing. This design is also complex, requires more radial installation space, and leads to relatively large total tolerances.
The object of the invention is therefore to create an aerodynamic plain bearing according to the preamble of Claim 1, which can make do with as few components as . --, ~ Z O Z 0 1 ~- ~
-possible and as little radial installation space as possible.
This object is achieved according to the characterizing portion of Claim 1.
The number of components is considerably reduced by the fact that the damping and spring element are combined into one, as a result of which the radial installation space can also be significantly decreased. At the same time, this means lower total tolerances. This design is therefore also associated with considerable advantages in terms of production, costs, and function, especially when a one-piece spring sleeve made of spring steel is used as the damping and spring element.
Additional embodiments of the invention are indicated in the description below and in the subsidiary Claims.
The invention will be described below in more detail, with reference to the exemplary embodiments illustrated in the attached drawings.
Figure 1 shows a section through an aerodynamic radial bearing in a first embodiment.
Figure 2 shows a portion of a section through an aerodynamic radial bearing in a second embodiment.
In the embodiment of an aerodynamic radial bearing illustrated in Figure 1, a shaft 1 is mounted by means of a thin-walled elastic spring sleeve 2, which has a uniform or profiled wall thickness, in a cylindrical bore 3 of a bearing housing 4.
Spring sleeve 2 is made of spring steel, and is slightly noncircular in section so that at several (at least three, in this case four) support points 2' on the outer circumference it touches the wall of bore 3 and thus has a somewhat "polygonall' shape so that sickle-shaped damping gaps 5 are formed between the wall of bore 3 and those spring segments 2" of spring sleeve 2' which are located between each two adjacent support points 2' . 202019 3 -and have a radius of curvature R greater than the radius of bore 3, with the center point lying outside axis A of shaft 1. Located between the inner circumference of spring sleeve 2 and shaft 1 is a running gap 6 which, corresponding to the "polygonal" shape of spring sleeve 2, is noncircular, i.e. has wedge-shaped constrictions.
Spring sleeve 2 has a tangential attachment 7 to one of the support points 2' in the form of a screw accommodated by bearing housing 3, the free end of which extends into a corresponding opening or recess in spring sleeve 2. Instead of a screw, a pin or the like can also be used.
A spring sleeve 2 of this type can easily be produced from a section of a spring steel tube that is pressed with a suitable tool into the "polygonal" shape.
It may also possibly be cut to length from a suitably shaped or profiled tube. It is important to maintain a certain uniform wall thickness or a precisely defined thickness distribution, so that the damping gap 5 and running gap 6 can be precisely defined to correspond to the shaft and bearing diameter. A profiled spring sleeve 2 or corresponding individual segment 2a can also be manufactured by electrical discharge machining.
As indicated by the embodiment in Figure 2, a plurality of tangential attachments 7 can also be provided. These can be provided at all support points 2' at which spring sleeve 2 contacts the wall of bore 3.
It is also possible to use, instead of spring sleeve 2, corresponding separate spring segments 2a in a number corresponding to the number of support points 2' (four, in the case illustrated), which are then supported at tangential attachments 7. In this case tangential attachments 7 can be configured as axial ribs projecting into bore 3. The individual spring segments 2a can, adjacent to the tangential attachments, be bent slightly . Z020 19 3 -towards the outer circumference, or have a suitable profile.
Spring sleeve 2 or separate spring segments 2a are advantageously provided with a suitable coating, which is elastic and which gives spring sleeve 2 or separate spring segments 2a a low coefficient of friction.
Suitable coatings include diamond-like carbon, which can be also be applied to shaft 1, titanium nitrite [sic], or another hard, wear-resistant, low-friction coating. In the case of a shaft 1 made of hard material or having a hard, wear-resistant coating, a relatively soft coating on spring sleeve 2 or spring segments 2a is also a possibility. This could compensate for small dust or dirt particles without appreciably restricting the function. A hard coating on spring sleeve 2 or spring segments 2a and a soft-coated shaft 1 is also possible.
Spring sleeve 2 or individual spring segments 2a can also be made of artificial carbon and acquire the necessary flexibility, needed over the long term when the damping gap width deflects, by means of fiber reinforcement (CFC).
Claims (8)
1. An aerodynamic plain bearing for shafts (1) rotating at high rotation speeds, with a bearing housing (4) having a cylindrical bore (3) and with a tangentially attached elastic damping structure (2) having segments (2" or 2a), which is supported at a plurality of circumferentially spaced points (2') in the bearing housing (4) and forms a plurality of converging running gaps (6) with shaft (1) and damping gaps (5) with bearing housing (4), characterized in that segments (2" or 2a) of said damping structure (2) are single-layer, thin-walled, elastic sleeve sections with a substantially uniform wall thickness and a low coefficient of friction, which simultaneously act as damping and spring elements.
2. The plain bearing of Claim 1, wherein said segments (2" or 2a) are made of spring steel.
3. The plain bearing of Claim 2, wherein said segments have a coating of low-friction, wear-resistant material.
4. The plain bearing of Claim 2, wherein said segments (2") form a spring steel sleeve (2) with a shape that is polygonal in section.
5. The plain bearing of Claim 4, wherein said spring steel sleeve (2) is produced by cutting to length from a tube, possibly with subsection forming, to produce the shape that is polygonal in section.
6. The plain bearing of Claim 2, wherein said spring steel sleeve (2) has segments (2" or 2a) that are profiled in section, which form a plurality of converging running gaps (6) together with shaft (1) and sickle-shaped damping gaps (5) when combined with housing (4).
7. The plain bearing of Claim 4, wherein said bearing housing (4) has a tangential attachment (7) and said spring steel sleeve (2) has a recess which engages with said tangential attachment (7).
8. The plain bearing of Claim 1, wherein said segments (2" or 2a) are made of fiber-reinforced artificial carbon.1
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEP3921704.3 | 1989-07-01 | ||
| DE3921704A DE3921704A1 (en) | 1989-07-01 | 1989-07-01 | AERODYNAMIC SLIDING BEARING |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2020193A1 CA2020193A1 (en) | 1991-01-02 |
| CA2020193C true CA2020193C (en) | 1997-09-23 |
Family
ID=6384117
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002020193A Expired - Fee Related CA2020193C (en) | 1989-07-01 | 1990-06-29 | Aerodynamic plain bearing |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0406722B1 (en) |
| CA (1) | CA2020193C (en) |
| DE (2) | DE3921704A1 (en) |
| ES (1) | ES2060870T3 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19615824A1 (en) * | 1996-04-20 | 1997-10-23 | Igus Gmbh | bearings |
| DE102015010470A1 (en) * | 2015-08-14 | 2017-02-16 | Carl Freudenberg Kg | Arrangement for transmitting torque |
| WO2021101211A1 (en) * | 2019-11-18 | 2021-05-27 | 한양대학교 에리카산학협력단 | Hybrid fluid bearing |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE7024210U (en) * | Lemfoerder Metallwaren Ag | Plain bearings, in particular for universal joints in steering and switching devices of motor vehicles | ||
| JPS5421900B2 (en) * | 1973-02-15 | 1979-08-02 | ||
| DE2310592A1 (en) * | 1973-03-02 | 1974-09-12 | Skf Kugellagerfabriken Gmbh | DRY SLIDING BEARING |
| US4178046A (en) * | 1976-05-24 | 1979-12-11 | The Garrett Corporation | Foil bearing |
| DE2838768C3 (en) * | 1978-09-06 | 1981-02-19 | Dornier System Gmbh, 7990 Friedrichshafen | Multi-surface plain bearings |
| DE2909973C2 (en) * | 1979-03-14 | 1982-10-21 | Forschungsvereinigung Verbrennungskraftmaschinen E.V., 6000 Frankfurt | Aerodynamic springy multi-slide surface bearing |
| EP0068387B1 (en) * | 1981-06-29 | 1986-03-26 | Shimadzu Corporation | Fluid foil bearing |
| DE3331503C2 (en) * | 1983-09-01 | 1985-11-21 | MTU Motoren- und Turbinen-Union München GmbH, 8000 München | Aerodynamic radial bearing |
| DE3544392A1 (en) * | 1985-12-14 | 1987-06-19 | Kloeckner Humboldt Deutz Ag | AERODYNAMIC SLIDING BEARING |
| US4818123A (en) * | 1986-07-24 | 1989-04-04 | Allied-Signal Inc. | Foil journal bearing cooling |
-
1989
- 1989-07-01 DE DE3921704A patent/DE3921704A1/en not_active Withdrawn
-
1990
- 1990-06-29 ES ES90112457T patent/ES2060870T3/en not_active Expired - Lifetime
- 1990-06-29 CA CA002020193A patent/CA2020193C/en not_active Expired - Fee Related
- 1990-06-29 EP EP90112457A patent/EP0406722B1/en not_active Expired - Lifetime
- 1990-06-29 DE DE59007432T patent/DE59007432D1/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CA2020193A1 (en) | 1991-01-02 |
| DE59007432D1 (en) | 1994-11-17 |
| EP0406722B1 (en) | 1994-10-12 |
| EP0406722A2 (en) | 1991-01-09 |
| EP0406722A3 (en) | 1991-07-31 |
| DE3921704A1 (en) | 1991-01-03 |
| ES2060870T3 (en) | 1994-12-01 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKLA | Lapsed |