CA2282074A1 - Support bearing and process for its manufacture - Google Patents
Support bearing and process for its manufacture Download PDFInfo
- Publication number
- CA2282074A1 CA2282074A1 CA002282074A CA2282074A CA2282074A1 CA 2282074 A1 CA2282074 A1 CA 2282074A1 CA 002282074 A CA002282074 A CA 002282074A CA 2282074 A CA2282074 A CA 2282074A CA 2282074 A1 CA2282074 A1 CA 2282074A1
- Authority
- CA
- Canada
- Prior art keywords
- ring
- support bearing
- intermediate ring
- bearing according
- radial
- 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.)
- Abandoned
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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
- F16C27/066—Ball or roller 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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- 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
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/30—Material joints
-
- 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
- F16C2326/00—Articles relating to transporting
- F16C2326/01—Parts of vehicles in general
- F16C2326/06—Drive shafts
Abstract
A process for the manufacture of a support bearing including an inner ring (1), which is surrounded at a radial distance by an outer ring (2), whereby the inner (1) and the outer ring (2) are connected by an intermediate ring (4) made of elastic rubber material which is positioned in the gap (3) formed by the radial distance. The inner (1) and the outer ring (2) are positioned into a vulcanisation tool with an axial misalignment (5) corresponding to a manufacture related shrinkage, whereby the intermediate ring (4) is inclined by the axial misalignment (5) to an imaginary radial plane (7) and vulcanised onto the inner (1) and outer ring (2), whereby the vulcanised support bearing is removed from the vulcanisation tool and whereby the actual misalignment (5) between inner ring (1) and the outer ring (2) is completely compensated by the intermediate ring (4) which inclined during manufacture, because of its shrinkage during cooling and solidification.
Description
SUPPORT BEARING AND PROCESS FOR ITS MANUFACTURE
Field of the Invention The invention relates to a process for the manufacture of a support bearing including an inner ring, which is surrounded by a readily spaced apart outer ring, whereby the inner and outer rings are connected by an intermediate ring of elastic rubber material positioned in the gap formed by the mutual spacing of the rings.
Background of the Invention Such a support bearing is known, for example, from DE 20 61 625 B2 This bearing is used as intermediate support for the articulated drive shaft of motor vehicles, whereby the intermediate ring is formed by several circumferential by evenly spaced web members of elastic rubber material. The web members extend between the inner and the outer ring and in radial direction both in longitudinal section as well as in cross section, whereby between radially spaced apart adjacent web members a stop buffer is positioned which i.s axed to the outer support ring, extends in the radial direction inwardly and in the vibration free condition is positioned at a radial distance from the inner ring. However, it is to be observed that the use properties of the aforementioned support are not satisfactory over a long period of use.
Subsequent to the manufacturing process and during the intended use of the support tensile stress occurs within the intermediate ring which consists of web members which reduce the period of use and can lead to premature failure of the support.
Summary of the Invention It is the object of the invention to further develop a support ring of the above described type and a process for its manufacture so that the intermediate ring is free of tensile r . ... ' stress due to the manufacturing process and even without calibration of the inner and/or the outer ring.
The object is achieved with a support bearing and a process for its manufacture in accordance with the invention.
wherein during manufacture of the support bearing the inner and the outer ring are positioned in a vulcanisation tool with a relative axial displacement which corresponds to the shrinkage upon manufacture, the intermediate ring is vulcanised onto the inner and outer ring and inclined along an imaginary radial plane corresponding to the axial misalignment, and the vulcanised support bearing is removed from the vulcanisation tool, and the axial misalignment between the inner and outer rings because of the inclined intermediate ring during manufacture is completely compensated during cooling and solidification because of shrinkage. The intermediate ring which is manufactured by way of the process in accordance with the invention is free of radial tension stress and therefore provides consistently good operating properties over a long period of use. A
manufacture related shrinkage of the intermediate ring subsequent to the removal of the support bearing from the vulcanisation tool does not result in tension stress contrary to a support bearing in accordance with the art, wherein the vulcanised intermediate ring is not inclined in axial direction and the inner and outer rings are positioned without mutual axial displacement. The axial misalignment of the inner ring relative to the outer ring is automatically and completely compensated by the shrinkage of the intermediate ring.
If the support bearing is used, for example, as support for a cardanic shaft in motor vehicles, the inner and outer ring can be positioned in a vulcanization tool with an axial displacement of 0.1 to 0.5 mm. This displacement is completely compensated by the shrinkage of the intermediate ring subsequent to its vulcanisation, so that the intermediate ring extends radially between the inner and outer ring when viewed in axial cross-section of the support bearing. A calibration of the inner and/or outer ring r ~ , subsequent to vulcanisation. is obviated in that the intermediate ring is not subject to tension stress reducing the period of use which tension stress is generated during manufacture.
The amount of shrinkage is essentially dependent from the material respectively used and the thickness of the material of the intermediate ring.
The invention further relates to a support bearing manufactured according to the aforedescribed process, including an inner ring which is surrounded by a radially spaced apart outer ring, whereby the inner and outer rings are connected by an intermediate ring of elastic rubber material positioned in the gap formed by the radial spacin of the rings.
For the achievement of this object, it is provided that the intermediate ring -when viewed in axial cross-section - during manufacture has a greater length then in the condition ready for use. During manufacture, which means immediately after the removal of the support bearing from the vulcanization tool and prior to the cooling and solidification of the intermediate ring, the inner and outer ring are mutually displaced in axial direction and the intermediate ring is inclined by the axial misalignment from an imaginary radial plane between the inner and outer ring. During the cooling and solidification of the intermediate ring, the length of the intermediate ring decreases because of the shrinkage until the intermediate ring in the condition ready for use, which means in the completely cooled and solidified condition of the intermediate ring, extends only in radial direction and is positioned in a singler radial plane together with the inner ring and the outer ring. .
It has proven advantageous for most applications when the ratio of the length during manufacture to the length in the condition ready for use is 1.05 to 1.15.
Depending on the material used and the material thickness it is thereby insured that the intermediate ring is free of radial tensile stress in the condition ready for use.
Field of the Invention The invention relates to a process for the manufacture of a support bearing including an inner ring, which is surrounded by a readily spaced apart outer ring, whereby the inner and outer rings are connected by an intermediate ring of elastic rubber material positioned in the gap formed by the mutual spacing of the rings.
Background of the Invention Such a support bearing is known, for example, from DE 20 61 625 B2 This bearing is used as intermediate support for the articulated drive shaft of motor vehicles, whereby the intermediate ring is formed by several circumferential by evenly spaced web members of elastic rubber material. The web members extend between the inner and the outer ring and in radial direction both in longitudinal section as well as in cross section, whereby between radially spaced apart adjacent web members a stop buffer is positioned which i.s axed to the outer support ring, extends in the radial direction inwardly and in the vibration free condition is positioned at a radial distance from the inner ring. However, it is to be observed that the use properties of the aforementioned support are not satisfactory over a long period of use.
Subsequent to the manufacturing process and during the intended use of the support tensile stress occurs within the intermediate ring which consists of web members which reduce the period of use and can lead to premature failure of the support.
Summary of the Invention It is the object of the invention to further develop a support ring of the above described type and a process for its manufacture so that the intermediate ring is free of tensile r . ... ' stress due to the manufacturing process and even without calibration of the inner and/or the outer ring.
The object is achieved with a support bearing and a process for its manufacture in accordance with the invention.
wherein during manufacture of the support bearing the inner and the outer ring are positioned in a vulcanisation tool with a relative axial displacement which corresponds to the shrinkage upon manufacture, the intermediate ring is vulcanised onto the inner and outer ring and inclined along an imaginary radial plane corresponding to the axial misalignment, and the vulcanised support bearing is removed from the vulcanisation tool, and the axial misalignment between the inner and outer rings because of the inclined intermediate ring during manufacture is completely compensated during cooling and solidification because of shrinkage. The intermediate ring which is manufactured by way of the process in accordance with the invention is free of radial tension stress and therefore provides consistently good operating properties over a long period of use. A
manufacture related shrinkage of the intermediate ring subsequent to the removal of the support bearing from the vulcanisation tool does not result in tension stress contrary to a support bearing in accordance with the art, wherein the vulcanised intermediate ring is not inclined in axial direction and the inner and outer rings are positioned without mutual axial displacement. The axial misalignment of the inner ring relative to the outer ring is automatically and completely compensated by the shrinkage of the intermediate ring.
If the support bearing is used, for example, as support for a cardanic shaft in motor vehicles, the inner and outer ring can be positioned in a vulcanization tool with an axial displacement of 0.1 to 0.5 mm. This displacement is completely compensated by the shrinkage of the intermediate ring subsequent to its vulcanisation, so that the intermediate ring extends radially between the inner and outer ring when viewed in axial cross-section of the support bearing. A calibration of the inner and/or outer ring r ~ , subsequent to vulcanisation. is obviated in that the intermediate ring is not subject to tension stress reducing the period of use which tension stress is generated during manufacture.
The amount of shrinkage is essentially dependent from the material respectively used and the thickness of the material of the intermediate ring.
The invention further relates to a support bearing manufactured according to the aforedescribed process, including an inner ring which is surrounded by a radially spaced apart outer ring, whereby the inner and outer rings are connected by an intermediate ring of elastic rubber material positioned in the gap formed by the radial spacin of the rings.
For the achievement of this object, it is provided that the intermediate ring -when viewed in axial cross-section - during manufacture has a greater length then in the condition ready for use. During manufacture, which means immediately after the removal of the support bearing from the vulcanization tool and prior to the cooling and solidification of the intermediate ring, the inner and outer ring are mutually displaced in axial direction and the intermediate ring is inclined by the axial misalignment from an imaginary radial plane between the inner and outer ring. During the cooling and solidification of the intermediate ring, the length of the intermediate ring decreases because of the shrinkage until the intermediate ring in the condition ready for use, which means in the completely cooled and solidified condition of the intermediate ring, extends only in radial direction and is positioned in a singler radial plane together with the inner ring and the outer ring. .
It has proven advantageous for most applications when the ratio of the length during manufacture to the length in the condition ready for use is 1.05 to 1.15.
Depending on the material used and the material thickness it is thereby insured that the intermediate ring is free of radial tensile stress in the condition ready for use.
i _ _ ~~ -The intermediate ring can be formed by at least two circumferentially distributed web members which are separated by a circumferential spacing, whereby the web members are defined in circumferential direction by end surfaces which extend parallel to the end surface of an adjacent web body, whereby all end surfaces are essentially planar and inclined in the same direction of rotation and whereby the angle of inclination of the end surfaces, relative to the circumferential direction is consistently 15 to 75 degrees, preferably 30 to 60 degrees. Tensile stress caused during manufacture which reduces the period of use of on elastic :rubber materials is reliably prevented with this construction.
A shrinkage during manufacture of the web members during vulcanisation no longer causes tension stress but oily a rotation of the inner ring relative to the outer ring.
With a view to easy production and installation of the support bearing, it has proven advantageous when adjacent web members merge into one another and are evenly distributed in circumferential direction. The outer ring can include at least one opening which is penetrated by the material of the intermediate ring, whereby the material of the intermediate ring is continued on the side of the opening opposite of the web members.
It is hereby an advantage that a secure mechanical fastening of the intermediate ring on the outer ring is achieved which remains unchanged even over long periods of use.
In order to achieve a construction which requires few parts and is advantageous with respect to manufacture and economics, the web members in radial direction can include inner and outer fastening surfaces, whereby the inner fastening surfaces are adhesively connected with the mantle surface of the inner ring and the outer fastening surfaces with the inner circumferential surface of the outer ring. The use of additional support or stiffening rings is thereby obviated.
In order to avoid a mechanical overload of the web members, stop burls can be provided on the respectively opposite end surfaces and in direction of the opposing end surface.
Large radial and circumferential relative displacements of the inner ring relative to the outer ring can be limited by the stop burls positioned on the end surfaces, whereby the t , a stop burls preferable have .a semi-spherical profile on the side opposite the opposing impact surface so that an end position damping commences~upon contact of the stop burls with the opposing impact surface.
Brief Description of the Drawings The support bearing in accordance with the invention as well as the process for its manufacture are further described in the following by way of the attached drawings.
They show preferred embodiments of the support bearing in schematical illustration.
Figure 1 shows a front elevation of a first embodiment of the support bearing in accordance with the invention;
Figure 2 shows the embodiment of Figure 1 in cross section taken along a line A - A
and in a portion in the condition during manufacture;
Figure 3 shows the embodiment of Figure 2 in the condition ready for use after complete cooling and solidification of the intermediate ring; and Figure 4 shows a second embodiment of the support bearing with accordance with the invention and similar to the embodiment shown in Figure 1.
Detailed Description of the Preferred Embodiment The two embodiments of the support are used, for example, as intermediate shaft supports for cardanic shafts of motar vehicles. The supports have a construction with especially few parts, whereby the webbed bodies 10, 11, 19, 20 are directly vulcanised with their inner and outer fastening surfaces 15, 16 directly onto the adjacent surfaces of the inner ring 1 and the outer ring 2. The inner ring 1 in xhis embodiment is the~outer bearing race of a roller bearing, while the outer ring 2 is constructed as a support ring S
t .. _r and can be pressed in the first embodiment into a bearing base.
In the second embodiment., the outer ring 2 is enclosed on its outer circumference by a rubber track 23 which is itself surrounded, for example, by a bearing mount and under elastic pretension.
Figure 1 shows an intermediate ring 4 which is positioned with its inner fastening surfaces 15 onto the mantle surface 17 of the inner ring 1 and with its outer fastening surfaces 16 onto the inner circumferential surface 18 of the outer ring 2, and in this embodiment includes four circumferentially evenly spaced web members 10, 11, 19, 20 which respectively define a gap with their circumferentially opposite end surfaces 12, 13, 21, 22. The web members 10, 11, 19, 20 are provided with essentially planar end surfaces 12, 13, 21, 22 which are all inclined in the same direction of rotation whereby the angle of inclination 14, relative to the circumferential direction is consistently 45 degrees in this embodiment. To limit the relative rotation of the inner and outer rings 1, 2 relative to one another, the end surfaces 12, 13, 21, 22 can be provided with stop burls which are here not illustrated and which are positioned essentially perpendicularly to the respectively adjacent end surfaces.
Figures 2 and 3 respectively show an axial cross-section through a support bearing in accordance with the invention, whereby the support bearing in Figure 2 is shown in the condition during manufacture and in Figure 3 is shown in the condition ready for use.
As is apparent from Figure 2, the inner ring 1 and the outer ring 2 are positioned with a relative axial misalignment 5 relative to one another. The axial misalignment corresponds to the shrinkage during manufacture of the intermediate ring 4 subsequent to its vulcanisation. The intermediate ring in Figure 2 is inclined by the axial misalignment 5 to an imaginary radial plane 7, whereby the axial misalignment 5 as well as the inclination are exagerated for a better understanding of the invention.
During the cooling and solidification of the intermediate ring 4 subsequent to the removal of the ..
support bearing from the vulcanisation tool, the intermediate ring 4 shrinks, whereby the length 8 during manufacture is reduced to the length 9 in the condition ready for use. By positioning the web members 10, 11, 19, 20 in circumferential direction at the angle of inclination l4 and because of the intermediate ring 4 being free of radial tensions, the intermediate ring 4 is in all directions free of tension stress which would reduce the period of use and has consistently good operating properties during a long period of use.
A shrinkage during manufacture of the web members during vulcanisation no longer causes tension stress but oily a rotation of the inner ring relative to the outer ring.
With a view to easy production and installation of the support bearing, it has proven advantageous when adjacent web members merge into one another and are evenly distributed in circumferential direction. The outer ring can include at least one opening which is penetrated by the material of the intermediate ring, whereby the material of the intermediate ring is continued on the side of the opening opposite of the web members.
It is hereby an advantage that a secure mechanical fastening of the intermediate ring on the outer ring is achieved which remains unchanged even over long periods of use.
In order to achieve a construction which requires few parts and is advantageous with respect to manufacture and economics, the web members in radial direction can include inner and outer fastening surfaces, whereby the inner fastening surfaces are adhesively connected with the mantle surface of the inner ring and the outer fastening surfaces with the inner circumferential surface of the outer ring. The use of additional support or stiffening rings is thereby obviated.
In order to avoid a mechanical overload of the web members, stop burls can be provided on the respectively opposite end surfaces and in direction of the opposing end surface.
Large radial and circumferential relative displacements of the inner ring relative to the outer ring can be limited by the stop burls positioned on the end surfaces, whereby the t , a stop burls preferable have .a semi-spherical profile on the side opposite the opposing impact surface so that an end position damping commences~upon contact of the stop burls with the opposing impact surface.
Brief Description of the Drawings The support bearing in accordance with the invention as well as the process for its manufacture are further described in the following by way of the attached drawings.
They show preferred embodiments of the support bearing in schematical illustration.
Figure 1 shows a front elevation of a first embodiment of the support bearing in accordance with the invention;
Figure 2 shows the embodiment of Figure 1 in cross section taken along a line A - A
and in a portion in the condition during manufacture;
Figure 3 shows the embodiment of Figure 2 in the condition ready for use after complete cooling and solidification of the intermediate ring; and Figure 4 shows a second embodiment of the support bearing with accordance with the invention and similar to the embodiment shown in Figure 1.
Detailed Description of the Preferred Embodiment The two embodiments of the support are used, for example, as intermediate shaft supports for cardanic shafts of motar vehicles. The supports have a construction with especially few parts, whereby the webbed bodies 10, 11, 19, 20 are directly vulcanised with their inner and outer fastening surfaces 15, 16 directly onto the adjacent surfaces of the inner ring 1 and the outer ring 2. The inner ring 1 in xhis embodiment is the~outer bearing race of a roller bearing, while the outer ring 2 is constructed as a support ring S
t .. _r and can be pressed in the first embodiment into a bearing base.
In the second embodiment., the outer ring 2 is enclosed on its outer circumference by a rubber track 23 which is itself surrounded, for example, by a bearing mount and under elastic pretension.
Figure 1 shows an intermediate ring 4 which is positioned with its inner fastening surfaces 15 onto the mantle surface 17 of the inner ring 1 and with its outer fastening surfaces 16 onto the inner circumferential surface 18 of the outer ring 2, and in this embodiment includes four circumferentially evenly spaced web members 10, 11, 19, 20 which respectively define a gap with their circumferentially opposite end surfaces 12, 13, 21, 22. The web members 10, 11, 19, 20 are provided with essentially planar end surfaces 12, 13, 21, 22 which are all inclined in the same direction of rotation whereby the angle of inclination 14, relative to the circumferential direction is consistently 45 degrees in this embodiment. To limit the relative rotation of the inner and outer rings 1, 2 relative to one another, the end surfaces 12, 13, 21, 22 can be provided with stop burls which are here not illustrated and which are positioned essentially perpendicularly to the respectively adjacent end surfaces.
Figures 2 and 3 respectively show an axial cross-section through a support bearing in accordance with the invention, whereby the support bearing in Figure 2 is shown in the condition during manufacture and in Figure 3 is shown in the condition ready for use.
As is apparent from Figure 2, the inner ring 1 and the outer ring 2 are positioned with a relative axial misalignment 5 relative to one another. The axial misalignment corresponds to the shrinkage during manufacture of the intermediate ring 4 subsequent to its vulcanisation. The intermediate ring in Figure 2 is inclined by the axial misalignment 5 to an imaginary radial plane 7, whereby the axial misalignment 5 as well as the inclination are exagerated for a better understanding of the invention.
During the cooling and solidification of the intermediate ring 4 subsequent to the removal of the ..
support bearing from the vulcanisation tool, the intermediate ring 4 shrinks, whereby the length 8 during manufacture is reduced to the length 9 in the condition ready for use. By positioning the web members 10, 11, 19, 20 in circumferential direction at the angle of inclination l4 and because of the intermediate ring 4 being free of radial tensions, the intermediate ring 4 is in all directions free of tension stress which would reduce the period of use and has consistently good operating properties during a long period of use.
Claims (11)
1) Process for the manufacture of a support bearing including an inner ring which is surrounded at a radial distance by an outer ring, whereby the inner and outer rings are connected by an intermediate ring of elastic rubber material positioned in the gap formed by the radial spacing, characterized in that the inner ring and the outer ring are placed into a vulcanisation tool with an axial misalignment corresponding to the manufacture related shrinkage, that the intermediate ring is inclined by the axial misalignment to an imaginary radial plane and vulcanised to the inner and outer rings, that the vulcanised support bearing is removed from the vulcanisation tool and that the axial misalignment between the inner and outer rings is automatically completely compensated by shrinkage of the intermediate ring during cooling and solidification.
2) The process according to Claim 1; characterized in that the inner and outer rings are positioned into the vulcanisation tool with an axial misalignment of 0.1 to 0.5 mm.
3) Support bearing according to one of Claim 1 or 2, including an inner ring which is surrounded at a radial distance by an outer ring, whereby the inner and outer rings are connected by an intermediate ring of elastic rubber material positioned in the gap formed by the radial spacing, characterized in that the intermediate ring - when viewed in axial cross-section - during manufacture has a greater length then in the condition ready for use.
4) Support bearing according to Claim 3, characterized in that the ratio of the length during manufacture to the length in the condition ready for use is 1.05 to 1.15.
5) Support bearing according to one of Claims 3 or 4, characterized in that the intermediate ring is substantially free of radial tension stress in the condition ready for use.
6) Support bearing according to one of Claims 3 to 5, characterized in that the intermediate ring is formed by at least two circumferentially distributed web members which are separated by a circumferential distance, that the web members are delimited in circumferential direction by an end surface which is oriented parallel to an end surface of an adjacent web member, that all end surfaces are essentially planar and that the angle of inclination of the end surfaces relative to the circumferential direction is consistent 15 to 75 degrees.
7) Support bearing according to Claim 6, wherein the angle is 30 to 60 degrees.
8) Support bearing according to one of Claims 6 or 7, wherein the web members are constructed to merge into one another and are circumferentially evenly distributed.
9) Support bearing according to one of Claims 6 to 8, wherein the web members in radial direction have inner and outer fastening surfaces, the inner fastening surfaces being adhesively connected with the mantle surface of the inner ring and the outer fastening surfaces being adhesively connected with the inner circumferential surface of the outer ring.
10) Support bearing according to one of Claims 6 to 9, wherein at least one of the - respectively opposite end surfaces is provided with a surface profile.
11) Support bearing according to Claim 10, wherein the surface profile is formed by burls protruding in direction of the opposing end surface.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19841882A DE19841882C1 (en) | 1998-09-11 | 1998-09-11 | Support bearing and process for its manufacture |
| DEP19841882.5 | 1998-09-11 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2282074A1 true CA2282074A1 (en) | 2000-03-11 |
Family
ID=7880813
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002282074A Abandoned CA2282074A1 (en) | 1998-09-11 | 1999-09-10 | Support bearing and process for its manufacture |
Country Status (15)
| Country | Link |
|---|---|
| EP (1) | EP0985838B1 (en) |
| CN (1) | CN1247808A (en) |
| AR (1) | AR021216A1 (en) |
| AT (1) | ATE225909T1 (en) |
| AU (1) | AU720404B2 (en) |
| BR (1) | BR9904133A (en) |
| CA (1) | CA2282074A1 (en) |
| DE (2) | DE19841882C1 (en) |
| ES (1) | ES2183458T3 (en) |
| HU (1) | HU221937B1 (en) |
| NO (1) | NO994383L (en) |
| PL (1) | PL335361A1 (en) |
| PT (1) | PT985838E (en) |
| TR (1) | TR199901790A1 (en) |
| TW (1) | TW430609B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102005044324B4 (en) * | 2005-09-16 | 2008-03-27 | Mtu Friedrichshafen Gmbh | Method for producing an intermediate bearing for propeller shafts |
| CN102528967B (en) * | 2011-11-17 | 2015-01-21 | 中国航天科技集团公司烽火机械厂 | Rubber pressing mold for insert |
| CN105402250A (en) * | 2016-01-22 | 2016-03-16 | 温州联君机车部件有限公司 | Novel supporting bearing for driving shaft of car |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BE759118A (en) * | 1970-03-11 | 1971-04-30 | Lohmann & Stolterfoht Ag | HIGH ELASTICITY METAL-RUBBER COMPOSITE ELEMENT FOR SHAFT COUPLINGS |
| DE2061625C3 (en) * | 1970-12-15 | 1980-03-06 | Daimler-Benz Ag, 7000 Stuttgart | Intermediate bearings for the cardan shaft of motor vehicles |
| DE4228170C2 (en) * | 1992-08-25 | 1995-06-29 | Freudenberg Carl Fa | camp |
| DE4229614C2 (en) * | 1992-09-04 | 1995-06-22 | Freudenberg Carl Fa | Support bearing |
| CH687559A5 (en) * | 1992-09-09 | 1996-12-31 | Fischer Georg Automobilguss | Arrangement of a rolling bearing. |
-
1998
- 1998-09-11 DE DE19841882A patent/DE19841882C1/en not_active Expired - Fee Related
-
1999
- 1999-05-11 EP EP99109420A patent/EP0985838B1/en not_active Expired - Lifetime
- 1999-05-11 PT PT99109420T patent/PT985838E/en unknown
- 1999-05-11 DE DE59903007T patent/DE59903007D1/en not_active Expired - Fee Related
- 1999-05-11 ES ES99109420T patent/ES2183458T3/en not_active Expired - Lifetime
- 1999-05-11 AT AT99109420T patent/ATE225909T1/en not_active IP Right Cessation
- 1999-06-02 TW TW088109103A patent/TW430609B/en active
- 1999-07-16 CN CN99110474A patent/CN1247808A/en active Pending
- 1999-07-27 TR TR1999/01790A patent/TR199901790A1/en unknown
- 1999-09-02 AR ARP990104426A patent/AR021216A1/en unknown
- 1999-09-10 CA CA002282074A patent/CA2282074A1/en not_active Abandoned
- 1999-09-10 BR BR9904133-2A patent/BR9904133A/en not_active IP Right Cessation
- 1999-09-10 AU AU47521/99A patent/AU720404B2/en not_active Ceased
- 1999-09-10 PL PL99335361A patent/PL335361A1/en unknown
- 1999-09-10 HU HU9903065A patent/HU221937B1/en not_active IP Right Cessation
- 1999-09-10 NO NO994383A patent/NO994383L/en not_active Application Discontinuation
Also Published As
| Publication number | Publication date |
|---|---|
| NO994383L (en) | 2000-03-13 |
| HU221937B1 (en) | 2003-02-28 |
| AU4752199A (en) | 2000-03-16 |
| PL335361A1 (en) | 2000-03-13 |
| TR199901790A1 (en) | 2000-04-21 |
| BR9904133A (en) | 2000-09-12 |
| HU9903065D0 (en) | 1999-11-29 |
| HUP9903065A2 (en) | 2000-04-28 |
| AU720404B2 (en) | 2000-06-01 |
| EP0985838A1 (en) | 2000-03-15 |
| TW430609B (en) | 2001-04-21 |
| DE59903007D1 (en) | 2002-11-14 |
| CN1247808A (en) | 2000-03-22 |
| ES2183458T3 (en) | 2003-03-16 |
| PT985838E (en) | 2003-02-28 |
| AR021216A1 (en) | 2002-07-03 |
| HUP9903065A3 (en) | 2000-06-28 |
| EP0985838B1 (en) | 2002-10-09 |
| ATE225909T1 (en) | 2002-10-15 |
| DE19841882C1 (en) | 2000-03-02 |
| NO994383D0 (en) | 1999-09-10 |
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| FZDE | Discontinued |