EP0289498A1 - Flüssigkeitsdichtung für zueinander rotations- und axialbewegliche maschinenteile - Google Patents
Flüssigkeitsdichtung für zueinander rotations- und axialbewegliche maschinenteileInfo
- Publication number
- EP0289498A1 EP0289498A1 EP87900118A EP87900118A EP0289498A1 EP 0289498 A1 EP0289498 A1 EP 0289498A1 EP 87900118 A EP87900118 A EP 87900118A EP 87900118 A EP87900118 A EP 87900118A EP 0289498 A1 EP0289498 A1 EP 0289498A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- axial
- sealing
- intermediate sleeve
- radial
- sealing gap
- 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.)
- Withdrawn
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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of 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
- F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
- F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
- F16J15/3256—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals
-
- 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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3268—Mounting of sealing rings
Definitions
- Liquid seal for machine parts that are rotatable and axially movable
- the invention relates to a liquid seal in accordance with the preamble of claim 1 and avoids the expense of forced flushing of the sealing gaps, as is customary in the case of mechanical sealing surfaces made of hard materials.
- the object of the invention is to provide a simple seal which is well protected and, at the same time, can be implemented with a short construction against the ingress of dirt and mechanical damage from the outside and against superimposed torsion and thrust movement changes, the parts most at risk of wear and tear are easy to manufacture and inexpensive to obtain.
- the solution is achieved by the invention according to claim 1 by the interfaces for the torsion and shear Tensions are placed in an intermediate sleeve made of stiffer material (e.g. steel sheet), provided radially between two parts of the seal and having a main direction parallel to the undulating machine part. Since this intermediate sleeve can be axially entrained to a limited extent, but is mounted to prevent rotation, only a linear relative movement can occur on the sealing part closing the axial sealing gap. And since. the intermediate sleeve is also secured against rotation with respect to the counter surface in the axial sealing gap, only a rotational movement can result at the sealing part closing the radial sealing gap.
- stiffer material e.g. steel sheet
- the specified liquid seal can be implemented with an axial gap seal arranged at least on the inner surface or the outer surface of the intermediate sleeve.
- the sealing part closing the radial sealing gap can be used without axial spring against projections or recesses.
- the intermediate sleeve on the one hand and the associated shaft-shaped or housing-shaped machine part can be sufficiently axially spread or biased solely for its own elasticity. The reduced contact pressures compared with spring-working sealing elements, together with the constant directions of stress, enable a longer service life and also lower friction losses during operation.
- the arrangement of a bearing arranged closely to the sealing elements, which serves at the same time as an axial fixation of the intermediate sleeve to one of the two machine parts, further prevents the sealing elements from being radially and unevenly loaded by lateral forces, as are often the case with steering forks can be deformed until it leaks.
- a roller bearing as an axial fixation helps to further reduce the friction in the sealing area and to keep the temperatures low. If the anti-rotation device is made of protrusions or profile engagements which engage in the axially moving machine part relative to the intermediate sleeve, the sealing element bridging the radial sealing gap can be safely protected against torsional stresses and the intermediate sleeve including sealing elements can be easily installed.
- An anti-rotation device caused solely by higher radial preload of the sealing elements in the axial sealing gap is particularly important when assigned to a particularly low-friction bearing, e.g. B. rolling bearings, justifiable and then cost-saving and space-saving compared to an anti-rotation device with profile engagement.
- a particularly low-friction bearing e.g. B. rolling bearings
- the bearing and the axial gap sealing element By arranging the bearing and the axial gap sealing element radially one above the other, the radial forces can be kept particularly effectively away from the sealing elements with a short overall length of the seal.
- the bearing of the seal can also take over the functions of a further, liquid-side bearing of the universal joint shaft in a double function.
- Fig. 1 shows a version of the liquid seal with radial support of the intermediate sleeve by Roller bearings against the shaft-shaped machine part.
- FIG. 2A shows the front view of an anti-rotation device according to FIG. 2.
- FIG. 3 shows a version with radial support by a radial ball bearing which is also axially supported against the inner wall of the enveloping machine part and the intermediate sleeve.
- FIG. 4 shows a version in which the anti-rotation device is achieved solely by frictional forces from the axial sealing gap and is otherwise arranged approximately according to FIG. 1.
- FIG. 5 shows a version with an anti-rotation device, also by frictional forces, but roughly in accordance with the principle according to FIG. 3.
- a wave-shaped machine part 1 is led out of a housing-shaped machine part 2, in which there is a liquid (to the left in the drawing).
- a jiluffe 3 which partially overlaps the shaft-shaped machine part 1, is provided here, which together with the shaft-shaped machine part 1 not only with respect to the housing-shaped machine part 1 rotates, but can also move axially into an end position 4.
- the liquid seal 5 arranged radially between the machine parts 1 and 2 prevents the leakage of the liquid, for example oil from splash lubrication.
- the liquid seal is divided radially by an intermediate sleeve 6 made of rigid material (eg sheet metal) and extending parallel to the undulating machine part 1, an axial sealing gap 7 and a radial sealing gap 8 being produced.
- the axial sealing gap 7 is closed by at least one elastomeric sealing element 9 which easily withstands the predominantly radial prestress. This is partially embedded in an annular groove on the outer circumference of the intermediate sleeve 6 and presses against the finely polished bore surface of the housing-shaped machine part 2 from the inside.
- the range of movement of the axial sealing element 9, arranged upstream on the outside, is also a dirt scraper 9 A embedded in the housing-shaped machine part 2, which abuts against a finely polished area of the intermediate sleeve 6.
- the anti-rotation device 11 in the example consists of a pin projecting axially from the intermediate sleeve 6 into the interior of the housing-shaped machine part 2, which bears against the walls of an inner recess 10 in the direction of rotation, but without the axial mobility of the intermediate sleeve carried by the wave-shaped machine part 1 6 compared to the housing-shaped machine part 2.
- the radial sealing gap 8 is closed by at least one predominantly axial prestressing, elastomeric sealing element 12, which allows a relative rotation between the shaft-shaped machine part 1 or the sleeve 3 rotating therewith and the intermediate sleeve 6, but without being subjected to their axial movements .
- the intermediate sleeve 6 is held axially relative to the sleeve 3 or the wave-shaped machine part 1 by an axially fixing 13 that can be rotated in rotation.
- a roller bearing 13 A held on the sealing side by means of locking rings 14, 15 or corresponding contact edges in the intermediate sleeve and on the shaft side in the sleeve 3 was selected for the axial fixation, the inner ring 13 B of which on the sealing side against a shoulder 15 A in the sleeve 3 and the liquid side is supported against a locking ring 15 in the sleeve 3.
- roller bearing 13 A does not permit any axial offset between the intermediate sleeve 6 and the sleeve 3 when it is pushed into or out of the housing-shaped machine part 2.
- the roller bearing 13 A relieves the sealing element 12 which closes the axial sealing gap 8 and an axial gap dirt wiper 12 A which is preferably arranged upstream thereof, against inadmissible radial misalignment as a result of possible lateral forces transverse to the main axis.
- the penetration of dirt from the outside is made more difficult here by an axial dirt wiper 12 A, the sealing lip of which is spring-loaded on the liquid side against a radial intermediate disk 16.
- the intermediate sleeve 6 is provided as a thin-walled sheet metal element with tongue-like projections as anti-rotation means 11 engaging in the recesses 10 of the housing-shaped machine part 2.
- the sealing elements 9, 9 A and 12, 12 A are placed here similarly, as already shown in FIG. 1.
- a locking ring for axial fixation only a radial flanged edge of the intermediate sleeve 6 was used.
- a support element (not designated in more detail) for a shaft sealing ring was welded on the inside. This enables a cassette-like configuration of the sealing element 12, 12 A for the radial sealing gap 8.
- a plain bearing 13 was arranged on the liquid side in front of a leading edge 15 of the housing-shaped machine part 2.
- the anti-rotation device 11 is shown as a tongue-like projection of the intermediate sleeve 6, which engages in the recess 10 of the housing-shaped machine part 2.
- the position of the axial sealing gap 7 has been exchanged compared to the version according to FIGS. 1 and 2. It is located here on the inside of the intermediate sleeve 6 opposite the shaft-shaped machine part 1 or the sleeve 3 fastened thereon.
- the anti-rotation device 11 can consist of a bolt which engages radially into the axial recess of the sleeve 3 from the intermediate sleeve 6.
- the bearing 13 is fixed axially between outer side 'of the intermediate sleeve and the housing-shaped machine part.
- the sealing elements 12 A and 12 closing the radial sealing gap 8 grind on the intermediate sleeve or on the inside of the radially standing intermediate disk 16 at the outer end of the intermediate sleeve 6.
- FIG. 1 An arrangement according to the principle of FIG. 1 is again selected in FIG. 4, but the anti-rotation device 11 is left to the clamping effect of the sealing elements 9 closing the axial sealing gap 7.
- the intermediate sleeve 6 is provided on the inside with a large recess for accommodating the sealing elements 12 closing the radial sealing gap 8 and on the outside with a circumferential annular groove for receiving the sealing element 9 closing the axial sealing gap 7.
- Immediately radially below the sealing element 9 closing the axial sealing gap 7 are located on the inside of the Intermediate sleeve 6 the balls of the bearing 13, so that the intermediate sleeve 6 also serves as an outer ring 13 C of the bearing 13 here in a double function.
- Its inner ring 13 B is connected to the sleeve 3 and the shaft-shaped machine part 1 in a rotationally and slidably fixed manner. Seen overall, the seal in the end position 4 is shown here.
- the arrangement of the sealing elements 9 closing the axial sealing gap 7, which also act here only as a security against rotation 11 due to their clamping force, is exactly the reverse of that in FIG. 4.
- the intermediate sleeve 6 acts here as an inner race 13 C of the roller bearing 13 and the sealing element 12 or 12 A closing the radial sealing gap run around the inside of the outer ring 13 B or a sleeve in the housing-shaped machine part 2.
- the designs of the liquid seal according to FIGS. 4 and 5 are characterized by a particularly short overall length and simple construction, since the bearing and axial gap sealing element 9 are arranged radially one above the other.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sealing Of Bearings (AREA)
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
WOPCT/EP85/00734 | 1985-12-21 | ||
EP8500734 | 1985-12-21 |
Publications (1)
Publication Number | Publication Date |
---|---|
EP0289498A1 true EP0289498A1 (de) | 1988-11-09 |
Family
ID=8165088
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP87900118A Withdrawn EP0289498A1 (de) | 1985-12-21 | 1986-12-10 | Flüssigkeitsdichtung für zueinander rotations- und axialbewegliche maschinenteile |
Country Status (4)
Country | Link |
---|---|
US (1) | US4861172A (de) |
EP (1) | EP0289498A1 (de) |
DE (1) | DE3642082A1 (de) |
WO (1) | WO1987003946A1 (de) |
Families Citing this family (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0516708B1 (de) * | 1990-02-26 | 1994-12-21 | ZF FRIEDRICHSHAFEN Aktiengesellschaft | Dichtungsanordnung |
DE59101742D1 (de) * | 1990-03-13 | 1994-07-07 | Zahnradfabrik Friedrichshafen | Dichtungsanordnung. |
US5082294A (en) * | 1990-09-20 | 1992-01-21 | Federal-Mogul Corporation | Heat conducting wear sleeve assembly for lubricant seals |
US5098112A (en) * | 1990-10-01 | 1992-03-24 | Petrak Gregory H | Unitized dynamic facial seal |
EP0483071B1 (de) * | 1990-10-26 | 1995-03-01 | Sodick Company, Ltd. | Funkenerosive Drahtschneideinrichtung |
US5286232A (en) * | 1992-04-10 | 1994-02-15 | Borg-Warner Automotive Diversified Transmission Products Corporation | Slip yoke assembly for output of power transmission device |
GB2267293A (en) * | 1992-07-08 | 1993-12-01 | Chen Chun Chung | Bearing and lubricating structure for a knitting machine |
US5421592A (en) * | 1993-02-08 | 1995-06-06 | Petrak; Gregory H. | Unitized radial and facial seal |
US5687972A (en) * | 1996-11-26 | 1997-11-18 | Petrak; Gregory H. | Unitary oil seal assembly |
US6279914B1 (en) * | 1997-10-24 | 2001-08-28 | Eagle Industry Co., Ltd. | Sealing apparatus |
US6632022B2 (en) * | 2001-08-23 | 2003-10-14 | Bill Lee | Coupling structure for bearing and bushing |
JP4180829B2 (ja) * | 2002-01-21 | 2008-11-12 | イーグル工業株式会社 | シール装置 |
US7470066B2 (en) * | 2006-03-22 | 2008-12-30 | Gm Global Technology Operations, Inc. | Pump bearing assembly with seal |
US8336887B2 (en) * | 2006-05-02 | 2012-12-25 | Petrak Gregory H | Seal assembly |
JP2008055560A (ja) * | 2006-08-31 | 2008-03-13 | Fanuc Ltd | ロボットの関節部の密封装置及び関節ロボット |
CN103635707B (zh) * | 2011-04-05 | 2016-05-11 | 蒂森克虏伯罗特艾德有限公司 | 油润滑耐磨轴承 |
US10337617B2 (en) * | 2015-03-10 | 2019-07-02 | Trelleborg Sealing Solutions Us, Inc. | Canned seal assembly |
CN104976234B (zh) * | 2015-06-30 | 2017-07-11 | 国家电网公司 | 一种轴承密封 |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH85926A (de) * | 1919-10-24 | 1920-07-16 | Suter Jakob | Stopfbüchse für umlaufende Wellen. |
US2403520A (en) * | 1945-07-23 | 1946-07-09 | Theodore C Gerner | Drive shaft bushing assembly |
US3761099A (en) * | 1970-12-10 | 1973-09-25 | Hanson L | Seals for rotary and axially movable shafts |
US4213513A (en) * | 1978-06-26 | 1980-07-22 | Mcgill Manufacturing Company, Inc. | Ignition control system with safety switches |
DE2839816A1 (de) * | 1978-09-13 | 1980-03-27 | Imre Veres | Abdichtungsbuchse fuer die durchfuehrung einer schraubenwelle durch den schiffskoerper, insbesondere fuer sportboote und yachten |
US4693699A (en) * | 1985-09-24 | 1987-09-15 | Deere & Company | Seal assembly for rotary and reciprocating motion |
-
1986
- 1986-12-10 EP EP87900118A patent/EP0289498A1/de not_active Withdrawn
- 1986-12-10 WO PCT/EP1986/000735 patent/WO1987003946A1/de not_active Application Discontinuation
- 1986-12-10 DE DE19863642082 patent/DE3642082A1/de not_active Withdrawn
-
1988
- 1988-06-21 US US07/264,275 patent/US4861172A/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO8703946A1 * |
Also Published As
Publication number | Publication date |
---|---|
US4861172A (en) | 1989-08-29 |
WO1987003946A1 (en) | 1987-07-02 |
DE3642082A1 (de) | 1987-06-25 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0289498A1 (de) | Flüssigkeitsdichtung für zueinander rotations- und axialbewegliche maschinenteile | |
EP1039161B1 (de) | Wellenabdichtung | |
DE3639315C1 (de) | Vorrichtung zum Abdichten eines Waelzlagers,insbesondere von Lagerbuechsen eines Kreuzgelenkes | |
DE2430027C2 (de) | Gleichlaufdrehgelenk | |
EP1406025A2 (de) | Wellenlippendichtung | |
DE3505464A1 (de) | Kassettendichtung fuer wellen | |
DE3833690C2 (de) | ||
DE602004001084T2 (de) | Kreuzgelenk mit entlüftender Dichtung | |
DE3035884A1 (de) | Dichtungsanordnung | |
DE2548722A1 (de) | Lagerungsanordnung einer ueber ein gleichlaufdrehgelenk antreibbaren radnabe | |
DE3031870C2 (de) | Kassetten-Dichtung | |
DE3338487A1 (de) | Presswalze | |
DE3025947C2 (de) | Gleitringdichtung | |
DE19925895A1 (de) | Kreuzgelenk für eine Kardangelenkanordnung | |
EP0298995B1 (de) | Dichtungring zur Anordnung zwischen zueinander axial-und drehbeweglichen Maschinenteilen | |
DE2810942B2 (de) | Dichtungsanordnung | |
DE2403111A1 (de) | Gelenkverbindung | |
DE2917012A1 (de) | Schutzvorrichtung fuer eine gelenkverbindung | |
DE19637813C2 (de) | Gleitringdichtung | |
DE602005004709T2 (de) | Dichtungs-Manschette einer homokinetischen Kupplung | |
DE2942480A1 (de) | Dichtung fuer waelzlager, insbesondere fuer foerderbandrollen | |
DE69727935T2 (de) | Radnabe mit wälzlager mit einer dichtung mit integriertem kodierer | |
DE3920482C2 (de) | ||
DE3534130C2 (de) | ||
WO2018086808A1 (de) | Radlageranordnung für ein kraftfahrzeug |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 19880427 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE GB IT |
|
17Q | First examination report despatched |
Effective date: 19890713 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 19910619 |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: MAURER, DIETER Inventor name: SCHUSTER, MAX Inventor name: ANNAST, RUDOLF Inventor name: RAUTER, JUERGEN |