GB2057068A - Rolling bearings - Google Patents
Rolling bearings Download PDFInfo
- Publication number
- GB2057068A GB2057068A GB8020747A GB8020747A GB2057068A GB 2057068 A GB2057068 A GB 2057068A GB 8020747 A GB8020747 A GB 8020747A GB 8020747 A GB8020747 A GB 8020747A GB 2057068 A GB2057068 A GB 2057068A
- Authority
- GB
- United Kingdom
- Prior art keywords
- disc
- bearing
- wedge
- bore
- radial clearance
- 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.)
- Granted
Links
- 238000005096 rolling process Methods 0.000 title abstract description 4
- 229920003023 plastic Polymers 0.000 claims abstract description 7
- 239000004033 plastic Substances 0.000 claims abstract description 7
- 239000000463 material Substances 0.000 claims abstract description 5
- 239000000428 dust Substances 0.000 claims description 7
- 238000004519 manufacturing process Methods 0.000 claims description 6
- 238000005266 casting Methods 0.000 claims description 4
- 239000013013 elastic material Substances 0.000 claims description 2
- 238000001746 injection moulding Methods 0.000 claims description 2
- 238000000465 moulding Methods 0.000 claims description 2
- 238000002347 injection Methods 0.000 abstract 1
- 239000007924 injection Substances 0.000 abstract 1
- 238000010276 construction Methods 0.000 description 6
- 239000002184 metal Substances 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000000717 retained effect Effects 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
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
- F16C25/08—Ball or roller bearings self-adjusting
- F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
-
- 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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
-
- 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
- F16C2380/00—Electrical apparatus
- F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Rolling Contact Bearings (AREA)
Abstract
A device for compensating for a radial clearance between a rolling bearing (3), as shown a ball bearing, and a bore (41) in which the bearing is mounted comprises a disc (2) which is formed with an axially protruding rim in the form of a wedge (21) which engages in the radial clearance and a spring (22) for urging the wedge of the disc into the clearance. A double wedge may be provided to locate spring 22, Fig. 2 (not shown). Alternatively, the spring may be moulded integrally with the disc and may comprise a bellows. Such a device may be injection moulded in a plastics material. Disc (2) also acts as a seal. <IMAGE>
Description
SPECIFICATION
Device for compensating for a radial clearance between a roller bearing and a bore in which the bearing is mounted
The present invention relates to a device for compensating for a radial clearance between a roller bearing and a bore in which the bearing is mounted.
In a device known from German Patent
Specification No. 851,865, an annular intermediate member, which is radially deformable, is inserted in the space between the parts of a friction connection, whereby the radial dimension of the intermediate member is adjusted to the radial clearance in such a way that a plastic deformation of the intermediate member results during the insertion. According to a particular design, the device for compensation of the radial clearance of the friction connection consists of a substantially circular plate, which is recessed at the circumference in order to form lobes which are bent at right angles to the flat middle section of the plate. These lobes, arranged in a circle, are dished such that their concave sides face outwards.During assembly, the dished lobes are compressed to form the lobes occupying the radial clearance, the bulging, the thickness of the wall and the width and spacing of the lobes being chosen, with regard to the size of the clearance in such a way that the desired radial pressure on the bearing is maintained.
According to the present invention there is provided a device for compensating for a radial clearance between a roller bearing and a bore in which the bearing is mounted, which device comprises a disc having an axially protruding rim in the form of a wedge for engagement in the radial clearance, and spring means for urging the disc towards the bearing so as to urge the wedge of the disc into the radial clearance.
It is known to provide a spring between the outer and inner rings of a bearing for the purpose of engaging the roller bearing and to avoid noise resulting from the bearing tolerance, which spring is a helical spring with one end supported against one shoulder of a bearing plate in the bearing bore and with the other end engaged with the outer ring of the roller bearing. When the bearing is biased or engaged in this way, the bearing clearance play between the inner and outer rings and the noise otherwise caused thereby can be markedly reduced by the axial displacement between the outer ring of the bearing and the inner ring of the bearing attached to the shaft under the axial pressure of the helical spring.
In order further to reduce this bearing clearance play and, in addition, to avoid a radial clearance between the outer circumferential surface, i.e. the outer ring of the roller bearing, and the bearing bore of the bearing plate, the disc with the axially protruding rim in the form of a wedge facing the outer ring is now inserted, according to the invention, between the end of the helical spring facing away from the bearing shoulder and the
outer ring of the ball bearing, and the wedge is
urged by the axial biasing force of the helical
spring into the clearance between the ball bearing
and the bearing bore in such a way as to provide an additional balance of the radial clearance of each.Under the influence of the axial biasing force, which is split up at the slope of the wedge
into an axial and a radial force component, the disc with the protruding wedge-shaped rim can adapt itself to the radial clearance between the outer ring of the roller bearing and the roller bearing bore even though the clearance may be variable.
As a result of the axial biasing force of the spring means and the design of the disc with the protruding wedge-shaped rim, not only are clearances resulting from machining tolerances lifted and pressed at the wedge shaped rim of the outer ring onto a rolling path conforming to the inner ring, as a result of the adjustability of the outer ring, but a clearance-free bearing seating is also maintained during operation, if the size of the clearance changes during operation, for example by heating of the bearing bore on the one hand and of the bearing on the other when the respective coefficients of expansion differ.
The wedge may be asymmetrical and comprise a first radially outer wedge surface to extend parallel to the bearing bore, and a second radially inner frustoconical wedge surface which is inclined to the bearing bore. Thus, on the one hand, a good guided positioning of the wedge in the bearing bore results and, on the other hand, the wedge slope is particularly effective for the avoidance of an unwanted radial clearance.
The disc may be constructed as a dust plate for the roller bearing. When the roller bearing is a ball bearing, the disc is designed in such a way that it does not abrade against the inner cage of the ball bearing. Where the end of the rotating shaft does not substantially project axially beyond the bearing the disc can seal the entire assembly from the exterior.
The rim of the disc may be interrupted by a plurality of axially extending slot-shaped recesses.
This enables a more precise determination of the spring rate of the disc.
The disc may be made of an elastic material which enables the wedge-shaped rim to accommodate the different radial dimensions of each contact point of the wedge surface on the outer circumferential surface of the roller bearing depending on the dimensions of the radial clearance to be compensated.
The disc may be provided with two oppositely directed wedge-shaped rims. By this means, the spring means is centred automatically during assembly and it is no longer necessary to monitor that the correct face of the disc is inserted into the bore during assembly.
In one form of the invention, the disc and the spring means are formed as a component which can be manipulated in one piece. The device may be made as a unitary component made of a plastics material and formed, for example, by moulding, injection moulding or casting.
The spring means may be in the form of, for example, a bellows, a corrugated disc, a plate spring or a plurality of elastic arms distributed around the disc. Where elastic arms are provided, they may be helical, but in any case it is preferable to provide the disc with perforations in the region of the arms to facilitate integral production of the device.
For a better understanding of the present invention and to show more clearly how it may be carried into effect reference will now be made, by way of example, to the accompanying drawings in which Figure 1 shows a section of part of a disc with a wedge-shaped rim moulded axially at one edge and a separate helical spring lying against the disc;
Figure 2 shows a sectional side view of part of a symmetrical disc;
Figure 3 shows a top view of a disc, the wedgeshaped rim of which is interrupted on the circumference by slot-shaped recesses;
Figure 4 is a cross-section along the line IV--IV of Figure 3;
Figure 5 shows a section of part of a disc with a wedge-shaped rim and a spring element in the form of a bellows moulded integrally with the disc;;
Figure 5 shows a section of part of a disc with an inner, cast dust plate and an outer cast bearing cap;
Figure 7 shows the construction according to
Figure 6 as a one-piece moulded part;
Figure 8 is a section of part of a disc with a wedge-shaped rim and a spring element in the form of a plate spring moulded integrally with the rim;
Figure 9 is a plan view of the construction according to Figure 8;
Figure 10 is a section along the line VIll-VIll of
Figure 9;
Figure 11 shows a disc with a wedge-shaped rim and a spring element in the form of several elastic arms distributed over the circumference and moulded integrally with the rim;
Figure 12 is a plan view of the construction according to Figure 11; and
Figure 13 is a section along the line Xl-Xl of
Figure 12.
According to Figure 1, a motor shaft 6 is rotatably supported by a roller bearing 3 with an inner ring 32 and an outer ring 31 in a bearing bore 41 of a bearing plate 4. In order to avoid the generation of noise as a result of the bearing clearance between the inner ring 32 and the outer ring 31, a helical spring 22 is provided in a known manner for biasing of or engagement with the bearing: the left-hand end (as seen in Figure 1) of the helical spring 22 is braced against a shoulder 42 of the bearing plate 4 in the bearing bore 41, and the right-hand end lies against the outer ring 31 of the ball bearing 3 with a disc 2 in an intermediate position.
In order to avoid the generation of noise as a result of a radial clearance 5 between the outer circumferential surface of the outer ring 31 of the roller bearing 3 and the inner circumferential surface of the bearing bore 41 of the bearing plate 4, which clearance is designated in Figure 1 as a, the disc 2, which is urged by the helical spring 22 against the outer ring 31 of the ball bearing 3, is provided with a moulded axial rim in the form of a wedge 21 facing the outer ring 31 of the roller bearing 3, and the wedge 21 is urged by the axial biasing force of the helical spring 22 into the clearance 5 in such a way as to compensate for the respective radial clearance a.At the same time, the outer ring of the ball bearing is also urged onto a rolling path adapted to the rigidly fixed inner ring as a result of the engagement at the wedge; in this way part of the manufacturing tolerances, to which the ball bearing itself is subject, do not affect the performance of the bearing.
The disc 2 is expediently designed at the same time as a dust plate of the roller bearing 3, in such a way that the inner bore of the disc 2 extends almost to the outer diameter of the motor shaft 6 and in the region of the inner ring 32 is maintained at a distance from the ring, so that abrasion against the rotating inner ring is avoided. Where the shaft end does not extend axially outwards beyond the bearing, the disc can also be advantageously designed at the same time as a bearing cap which seals off the entire arrangement of the shaft end from the exterior.
The rim moulded onto the disc 2 in the form of a wedge 21 is advantageously provided with a first radially outer wedge surface 211 running parallel to the bearing bore 41 and a second radially inner wedge surface 212, which is conical and runs at an angle which is inclined to the outer circumferential surface of the outer ring 31 of the roller bearing 3.
Figure 2 shows a symmetrical version of the disc 2 with a rim in the form of a wedge 21 moulded identically onto each of its two faces.
With this construction, a centering of the helical spring 22 at the left face (as shown in Figure 2) of the disc 2 is achieved, while at the same time the wedge at the right-hand face of the disc 2 obviates the radial clearance. Moreover, a symmetrical disc construction according to Figure 2 makes it unnecessary to monitor that the correct face of the disc is inserted into the bore during assembly.
As can be seen from Figures 3 and 4, the circular rim, which is moulded in the form of a wedge 21 on the faces of the disc, can be interrupted by narrow slot-shaped recesses 29 distributed around its circumference. The spring rate of the disc 2 can be adjusted precisely by the number and construction of these recesses 29.
Figure 5 shows a device for compensation of the radial clearance (clearance a) of a roller bearing 3 in a bearing bore 41, where the disc 2 with the rim in the form of a wedge 21 moulded axially onto it is designed in one piece with a bellows 23, the bellows providing a spring element. This assembly part, which is particularly simple to manufacture in one piece and to manipulate, consists expediently of a one-piece plastics component, in particular a one-piece moulded component, injection-moulded component or casting. In addition to being particularly simple to manufacture, a plastics component of this kind, in comparison to for example a metal component which can be produced as a flexible stamped component, contributes to the reduction of noise as a result of its increased damping properties.
Figure 6 shows a positioning of the bearing in which the left-hand side of the outer ring 31 of the ball bearing 3 does not bear against a shoulder 42 of the bearing plate 4, but is retained by a bearing cap 8, which can be screwed tightly onto the bearing plate 4 by means of screws 7. Both the bearing cap 8 and a dust plate 9 which covers the ball bearing 3 are initially formed as individual components, but are incorporated integrally into the annular disc 2 with the moulded rim in the form of a wedge 21 in such a way that the bearing cap 8, the dust plate 9, the disc 2 and the rim with the moulded wedge 21 form an assembly part which can be manipulated in one piece. The bearing cap 8 is itself designed to be elastic, as a spring element.Such an elastic design of the bearing cap 8 can be achieved in particular by slots running concentric to the motor shaft 6 in the area of the outer ring 31 of the roller bearing 3, which method is not shown here in detail. Such a positioning of the bearing is described for example in German Auslegeschrift No. 1,575,609.
Whilst in the design according to Figure 6, the bearing cap 8 on the one hand and the disc 2 on the other can be made, for example, of different materials, in particular the bearing cap 8 of metal and the disc 2 of plastics. In the design according to Figure 7, the bearing cap 8, the dust plate 9 and the disc 2, and the rim in the form of a wedge 21 facing the outer ring 31 of the roller bearing 3 are designed as a one piece moulded part or an injection-moulded part or a casting of uniform material.
An embodiment is shown in Figures 8 to 10 in which the spring element consists of a plate spring 24 which is connected integrally with the disc 2 or is moulded onto the disc 2. Here the annular disc 2 changes axially into the rim in the form of a wedge 21 and radially inwards into the plate spring 24. The plate spring 24 is formed by four slots 241-244 distributed uniformly over the circumference and opening radially inwards towards the shaft opening, and disc sections extending between these slots at an angle to the shoulder 42, the radially inner portions of the disc sections being adjacent to the radially inner section of the shoulder 42.
A further advantageous design of the device is shown in Figures 11 to 13, where the spring element consists of several elastic arms 25 to 28 distributed over the circumference and either connected integrally with the disc 2 or moulded with it. As can be seen in particular from the sectional views according to Figures 11 and 13, the arms 25 to 28 on the one hand the disc 2 with the rim moulded in the form of a wedge 21 on the other hand are arranged in a V-shape, in such a way that the elastic arms 25 to 28 lie with their radially upper ends adjacent to the shoulder 42 of the bearing plate 4, and the disc 2 also runs at an angle to the shoulder 42, so that the disc 2 and the arms 25 to 28 thus moulded form an axially flexible counter-pressure element for the wedge.
The disc 2 has, advantageously, perforations 251, 261,271,281 in the area ofthe arms 25 to 28, in such a way that the structural unit consisting of the disc 2, the arms 25 to 28 and the rim moulded onto the disc 2 in the form of a wedge 21 can be manufactured as a one-piece injection-moulded component with forming dies which are movable only in an axial direction.
Thus, the manufacture and assembly of the illustrated compensation device is simple.
Claims (18)
1. A device for compensating for a radial clearance between a roller bearing and a bore in which the bearing is mounted, which device comprises a disc having an axially protruding rim in the form of a wedge for engagement in the radial clearance, and spring means for urging the disc towards the bearing so as to urge the wedge of the disc into the radial clearance.
2. A device as claimed in claim 1, wherein the wedge is asymmetrical and comprises a first radially outer wedge surface to extend parallel to the bearing bore, and a second radially inner frustoconical wedge surface which is inclined to the bearing bore.
3. A device as claimed in claim 1 or 2, wherein the disc is constructed as a dust plate for the roller bearing.
4. A device as claimed in any preceding claim, wherein the rim of the disc is interrupted by a plurality of axially extending slot-shaped recesses.
5. A device as claimed in any preceding claim, wherein the disc is made of an elastic material.
6. A device as claimed in any preceding claim, wherein the disc is provided with two oppositely directed wedge-shaped rims.
7. A device as claimed in any one of claims 1 to 5, wherein the disc and the spring means are formed as a component which can be manipulated in one piece.
8. A device as claimed in claim 7, wherein the device is made as a unitary component made of a plastics material.
9. A device as claimed in claim 8, wherein the device is formed by moulding.
10. A device as claimed in claim 8, wherein the device is formed by injection moulding.
11. A device as claimed in claim 8, wherein the device is formed by casting.
12. A device as claimed in any one of claims 7 to 11, wherein the spring means comprises a bellows.
13. A device as claimed in any one of claims 7 to 11 , wherein the spring means comprises a corrugated disc.
14. A device as claimed in any one of claims 7 to 11, wherein the spring means comprises a plate spring.
15. A device as claimed in any one of claims 7 to 11, wherein the spring means comprises a plurality of elastic arms distributed around the disc.
16. A device as claimed in claim 15, wherein the arms are helical.
17. A device as claimed in claim 15 or 16, wherein the disc is provided with perforations in the region of the arms to facilitate integral production of the device.
18. A device for compensating for a radial clearance between a roller bearing and a bore in which the bearing is mounted substantially as hereinbefore described with reference to, and as shown in, Figure 1, Figures 2, 3 and 4, Figure 5,
Figure 6, Figure 7, Figures 8, 9 and 10 or Figures 11, 12 and 13 of the accompanying drawings.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2926541A DE2926541C3 (en) | 1979-06-30 | 1979-06-30 | Device for compensating the respective radial play of a roller bearing in a bearing bore |
| DE19792939596 DE2939596A1 (en) | 1979-09-29 | 1979-09-29 | Axially spring loaded ball bearing - has disc with wedge section rim entering clearance gap between outer race and bearing housing bore |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB2057068A true GB2057068A (en) | 1981-03-25 |
| GB2057068B GB2057068B (en) | 1983-07-06 |
Family
ID=25779772
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB8020747A Expired GB2057068B (en) | 1979-06-30 | 1980-06-25 | Roller bearings |
Country Status (11)
| Country | Link |
|---|---|
| AT (1) | AT389573B (en) |
| CS (1) | CS251758B2 (en) |
| DD (1) | DD151209A5 (en) |
| DK (1) | DK153966C (en) |
| FR (1) | FR2460414A1 (en) |
| GB (1) | GB2057068B (en) |
| HU (1) | HU181143B (en) |
| IT (1) | IT1131373B (en) |
| NL (1) | NL8003742A (en) |
| PL (1) | PL126642B1 (en) |
| SE (1) | SE443203B (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2297362A (en) * | 1995-01-30 | 1996-07-31 | Aisin Seiki | Shaft supported by ball bearing assemblies |
| GB2410772A (en) * | 2004-02-03 | 2005-08-10 | Hansen Transmissions Int | Roller bearing |
| EP2100047A1 (en) * | 2006-12-06 | 2009-09-16 | Husqvarna Aktiebolag | A crankshaft bearing arrangement of a combustion engine |
| EP2902648A1 (en) * | 2014-02-03 | 2015-08-05 | Maxon Motor AG | Bearing assembly for an electric motor with axially pre-tensioned roller bearing |
| GB2607572A (en) * | 2021-05-28 | 2022-12-14 | Leybold Gmbh | Vacuum pump |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102010043595A1 (en) | 2010-11-09 | 2012-05-10 | Zf Friedrichshafen Ag | Bearing for transmission shaft, particularly for output shaft of motor vehicle transmission, particularly motor vehicle automatic transmission, has rolling bearing, which is incorporated in bearing bore of transmission housing |
| DE102015213022A1 (en) * | 2015-07-13 | 2017-01-19 | Bühler Motor GmbH | electric motor |
| FR3097912B1 (en) * | 2019-06-25 | 2021-06-18 | Valeo Equip Electr Moteur | ROTATING ELECTRIC MACHINE EQUIPPED WITH A BEARING PRE-TENSIONING BODY |
| DE102022109632A1 (en) | 2022-04-21 | 2023-10-26 | Schaeffler Technologies AG & Co. KG | Rolling bearing arrangement and electrical machine |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE351169C (en) * | 1922-04-01 | Fritz Ossberger | ball-bearing | |
| DE844233C (en) * | 1942-10-24 | 1952-07-17 | Separator Ab | Radially movable spindle bearing for fast rotating machine parts, e.g. B. for centrifugal drums |
| US2926051A (en) * | 1957-10-01 | 1960-02-23 | Garrett Corp | Resilient bearing mount |
| DE1940926A1 (en) * | 1969-08-12 | 1971-02-25 | Mauersberger Hans Georg | Machine element for defining rotationally symmetrical bodies |
| SE343027B (en) * | 1970-09-29 | 1972-02-28 | Skf Ind Trading & Dev | |
| SE355401B (en) * | 1970-12-15 | 1973-04-16 | Skf Ind Trading & Dev |
-
1980
- 1980-05-30 DD DD80221477A patent/DD151209A5/en not_active IP Right Cessation
- 1980-06-09 CS CS804054A patent/CS251758B2/en unknown
- 1980-06-20 IT IT22900/80A patent/IT1131373B/en active
- 1980-06-25 GB GB8020747A patent/GB2057068B/en not_active Expired
- 1980-06-25 SE SE8004699A patent/SE443203B/en not_active IP Right Cessation
- 1980-06-25 DK DK271280A patent/DK153966C/en not_active IP Right Cessation
- 1980-06-25 PL PL1980225205A patent/PL126642B1/en unknown
- 1980-06-26 FR FR8014281A patent/FR2460414A1/en active Granted
- 1980-06-27 HU HU80801604A patent/HU181143B/en not_active IP Right Cessation
- 1980-06-27 NL NL8003742A patent/NL8003742A/en not_active Application Discontinuation
- 1980-06-30 AT AT0341280A patent/AT389573B/en not_active IP Right Cessation
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2297362A (en) * | 1995-01-30 | 1996-07-31 | Aisin Seiki | Shaft supported by ball bearing assemblies |
| US5899574A (en) * | 1995-01-30 | 1999-05-04 | Aisin Seiki Kabushiki Kaisha | Supporting structure of bearings |
| GB2297362B (en) * | 1995-01-30 | 1999-05-12 | Aisin Seiki | A supporting structure for bearings |
| GB2410772A (en) * | 2004-02-03 | 2005-08-10 | Hansen Transmissions Int | Roller bearing |
| GB2410772B (en) * | 2004-02-03 | 2007-04-11 | Hansen Transmissions Int | Roller bearing |
| EP2100047A1 (en) * | 2006-12-06 | 2009-09-16 | Husqvarna Aktiebolag | A crankshaft bearing arrangement of a combustion engine |
| EP2100047A4 (en) * | 2006-12-06 | 2010-01-06 | Husqvarna Ab | A crankshaft bearing arrangement of a combustion engine |
| EP2902648A1 (en) * | 2014-02-03 | 2015-08-05 | Maxon Motor AG | Bearing assembly for an electric motor with axially pre-tensioned roller bearing |
| GB2607572A (en) * | 2021-05-28 | 2022-12-14 | Leybold Gmbh | Vacuum pump |
Also Published As
| Publication number | Publication date |
|---|---|
| IT8022900A0 (en) | 1980-06-20 |
| SE443203B (en) | 1986-02-17 |
| DK153966B (en) | 1988-09-26 |
| HU181143B (en) | 1983-06-28 |
| GB2057068B (en) | 1983-07-06 |
| SE8004699L (en) | 1980-12-31 |
| ATA341280A (en) | 1989-05-15 |
| FR2460414B1 (en) | 1983-06-24 |
| DK153966C (en) | 1989-02-06 |
| PL126642B1 (en) | 1983-08-31 |
| DK271280A (en) | 1980-12-31 |
| NL8003742A (en) | 1981-01-05 |
| CS251758B2 (en) | 1987-08-13 |
| IT1131373B (en) | 1986-06-18 |
| DD151209A5 (en) | 1981-10-08 |
| FR2460414A1 (en) | 1981-01-23 |
| PL225205A1 (en) | 1981-02-27 |
| AT389573B (en) | 1989-12-27 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PCNP | Patent ceased through non-payment of renewal fee |