GB2123096A - A seal for an anti-friction or sliding bearing - Google Patents
A seal for an anti-friction or sliding bearing Download PDFInfo
- Publication number
- GB2123096A GB2123096A GB08313078A GB8313078A GB2123096A GB 2123096 A GB2123096 A GB 2123096A GB 08313078 A GB08313078 A GB 08313078A GB 8313078 A GB8313078 A GB 8313078A GB 2123096 A GB2123096 A GB 2123096A
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- GB
- United Kingdom
- Prior art keywords
- seal
- supporting element
- bearing
- sealing
- cylindrical
- 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.)
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Classifications
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- 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
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- 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
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- 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
- F16C33/74—Sealings of sliding-contact bearings
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- 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
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
- F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
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- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sealing Of Bearings (AREA)
- Rolling Contact Bearings (AREA)
- Sealing With Elastic Sealing Lips (AREA)
Abstract
To reduce shaft motion noise from, and heat transfer to, an anti- friction or sliding bearing, a seal for such bearing comprises a sealing part (5) of an elastic material into which is embedded a supporting element (8). <IMAGE>
Description
SPECIFICATION
A seal for an anti-friction or sliding bearing
The invention relates to a seal for an antifriction or sliding bearing comprising at least one sealing part provided on a retaining part.
In the case of anti-friction bearings, for example, the seals have the task of keeping the lubricant in the bearing and of preventing the penetration of contaminants. An anti-friction bearing has an outer race secured in a housing and an inner race connected, so as to be secured against rotation, to a shaft passing through the housing. Seals are known comprising resilient cover discs which are fastened either between the outer race and the housing wall or between the inner race and a shaft shoulder. The free end is supported on the front end of the respective other race so that the zone between the two races is sealed from outside. The clamped part of the cover discs forms the retaining part of the seal, whilst the free edge serves as the sealing part which bears against the front end of the face with a resilient bias.The outside of the outer race abuts a housing wall so that the noises arising during the shaft rotation are transmitted to the housing and become noticeable in a disturbing manner. There may also come about, in operation, an inadmissibly high heat flow from the housing to the anti-friction bearing so that it wears out prematurely. In addition, it is difficult to install the resilient cover discs.
The task underlying the invention is to design such a seal so that, taking into consideration an easy assembly and a long service life, it ensures a high degree of silencing of noises during the operation of the antifriction bearing.
According to the invention there is provided a seal for an anti-friction or sliding bearing, comprising at least one sealing part provided on a retaining part, wherein the retaining part is cap-shaped and has a contact surface which extends over the circumference of the bearing, the sealing part has a sealing lip which extends over the circumference of the seal, and is transversely arranged in relation to the retaining part, and the retaining part comprises stiffening means.
The seal according to the invention encircles, with its cap-shaped retaining part, the bearing which bears against the contact surface of the retaining part. By this means, a direct contact between the outside of the bearing and the housing, in which the seal is installed, is prevented and the transmission of noises into the housing receiving the bearing is largely avoided. The sealing part, which is transverse to the retaining part, can seal either the outer surface of the inner race of an antifriction bearing or, if it is used for a sliding bearing, against the shaft. Also, there is possible with the present seal an effective vibration damping of the entire bearing system.
Furthermore, the cap-shaped retaining part acts as an insulator which prevents an inadmissibly high heat flow from the housing to the bearing, so that the bearing does not fail prematurely as a result of wear. The seal can be easily fitted since it is simply placed on the bearing with the cap-shaped retaining part.
This allows the bearing to be provided with the seal before it is installed in the respective housing, the installation of the bearing thus being considerably simplified. Due to the stiffening, the retaining part can be reliably pressed on the bearing, thus ensuring a reliable fit and satisfactory sealing.
Preferably, the sealing part bears with a sealing edge against the associated countersurface. This allows the seal to be used not only for sealing from dirt but also for sealing from, for example, oil.
The invention will be explained in more detail with the aid of some constructional forms shown in the drawings, in which: Figure 1 shows, in an axial section, a first constructional form of a seal according to the invention for an anti-friction bearing,
Figure 2 shows a second constructional form of a seal according to the invention for a sliding bearing,
Figure 3 shows, in a representation like that of Fig. 1, another constructional form of a seal according to the invention for an antifriction bearing, and
Figures 4 and 10 show further constructional forms of seals according to the invention.
The seals can be used both for anti-friction bearings and for sliding bearings. The seal shown in Fig. 1 is intended for an anti-friction bearing, which has an inner race 1 and an outer race 2, between which there are mounted rolling elements 3, which are rolling balls in the exemplified embodiment. The seal has a retaining part 4 and a sealing part 5 which sealingly rests on an outer surface 6 of the inner race 1. The sealing part 5 is preferably a sealing lip which, with a sealing edge 7, rests on the outer surface 6.
The retaining part 4 is cylindrical in design and has a cylindrical supporting element 8 which rests on an outer surface 9 of the outer race 2 nearly over its entire axial length. The retaining part 4 is integrally formed with a base 10 which extends vertically to the axis of the retaining part and has a central passage port 10'. The supporting element 8 merges, curvedly in cross section, in a base part 11 which bears against a front end 1 2 of the outer race 2 and radially projects from the outer race 2 in the direction of the inner race 1. The base part 11 is designed in the shape of an annular disc and the front end 1 3 of the base part lies in an imaginary cylindrical surface 14 containing the centres M of the rolling elements 3.By this means, there is provided a sufficiently large fastening area for the sealing part 5 on the base part 11, while the base part is at a sufficient distance from the outer surface 6 of the inner race 1 so as to ensure that the sealing part 5 can be elastically deformed by the base part without hindrance.
The seal rests with a contact surface 38, which is formed by the inner wall of the supporting element 8, and its base part 11 directly on the outer surface 9 and the front end 1 2 of the outer race 2. The radius of curvature of the transition zone 1 5 from the cylindrical part 8' of the supporting element 8 to the base part 11 of the retaining part 8 is smaller than the curved transition from the outer surface 9 to the face 1 2 of the outer race 2. This ensures that, when the seal is placed on the outer race, the base part 11 comes in any event into abutting contact with the face 12.
The supporting element 9 has a constant outside diameter over its axial length and a uniform thickness over nearly its entire axial length. Only in the zone of the free front end 1 6 does the supporting element 8 have an inside diameter that it larger than in the other zone. By this means, the supporting element 8, in the zone of its front end 16, does not rest directly on the outer surface 9 of the outer race 2. As a result, the supporting element 8 has a thinner wall section 17, whose axial length corresponds to approximately 1/5 to 1/6 of the entire axial length of the supporting element. The base part 11 also has, over its entire radial width, a constant thickness which is equal to the thickness of the cylindrical part of the supporting element 8. The supporting element 8 imparts to the seal the necessary strength and preferably consists of metal.But it may consist of another suitable material. The thickness of the supporting element 8 is advantageously less than 0.3 mm, so that the seal has only a minimal thickness and increases the outside diameter of the anti-friction bearing only to a slight extent. As a result, no large installation space is necessary for the installation of the anti-friction bearing provided with the seal.
The supporting element 8 is provided on its outside with a coat 1 8 consisting of an elastomer. The coat 18 has a cylindrical part 19, which rests on the cylindrical part of the supporting element 8, and a radially disposed, annular-disc-shaped coating part 20 which completely covers the base part 11 of the supporting element 8 on the outside. The cylindrical coating part 1 9 engages over the front end 1 6 of the wall section 1 7 and bears with an annular section 21 against the inner wall of the wall section 17. The inside of the ring section 21 forms a continuation of the inside of the cylindrical supporting element part 8. In the zone of the wall section 17, the seal rests with the ring section 21 consisting of an elastomeric material on the outer surface 9 of the outer race 2.The cylindrical ring section 21 of the coat 1 8 is substantially thinner than the coat superimposed on the outside of the supporting element 8, which coat has a substantially constant thickness over its entire axial length and radial width.
The annular front end 22 of the coat 1 8 is flat and is perpendicular to the seal axis. The front end 22 is connected via a conical surface 23 to the cylindrical surface 24 of the coat 18i which surface, for its part, merges via a conical surface 25 in a flat coating part 20 outside 26 which is radial to the seal axis.
The conical surfaces 23, 25 ensure an effortless installation of the anti-friction bearing into an annular groove of the housing receiving the bearing. The front end 22 of the coat 18, which end has a distance from the front end 1 6 of the cylindrical supporting element part, is flush with the front ends 27, 28 of the outer race 2 and the inner race 1 respectively so that, in this zone, the seal does not project beyond the anti-friction bearing and thus renders possible a problem-free installation.
In order to allow installation tolerances to be compensated for in a simple manner and without impairing the tightness, the cylindrical surface 24 is provided with a profile 29. Seen in an axial section, it is undulatory in design so that there are formed grooves which extend over the circumference of the cylindrical surface 24 and which are separated by elevations. When the anti-friction bearing is inserted into the annular groove of the housing, the elevations are deformed, depending on the installation tolerance, in the axial direction and are axially dislodged in such a way that they fill the adjacent grooves so that, in the installed position, the coat 18 has a smooth cylindrical outer surface.
The outside 26 of the radial annular-discshaped coat part 20 is flat in design and is perpendicular to the seal axis.
The coating part 20 merges in the sealing part 5 which is at an acute angle to the seal axis and projects into the space surrounded by the cylindrical sealing part. The outside 26 of the coating part 20 merges curvedly in an outside 30 of the sealing part 5, which outside merges, while forming the sealing edge 7, approximately perpendicularly in a front end 31 of the sealing part 5, which front end, for its part, merges curvedly in an inside 32 which converges, in relation to the outside 30, in the direction of the base part 11. On account of this design, the sealing part 5 is frusto-conical and tapers in cross section from the front end 31.The inside 32 merges curvedly in an inside 33 of an annular-discshaped coating part 34, which inside is perpendicular to the seal axis, the coating part bearing against the inside of the base part 11 of the supporting element 8 and ending at a distance from the inner wall 35 of the outer race 2. The thickness of the coating part 34 is less than the thickness of the coating part 20 and is approximately equal to the thickness of the ring-shaped section 21 of the coat 18. On account of the described design, the base part 11 is embraced by the coat 18 at its front end 13.
In the installed position, the anti-friction bearing bears, with the coat 18, against the bearing recess in the housing. This largely prevents the transmission of noise into the housing so that there occurs only a very slight noise formation during operation. Over and above this, the coat 1 8 consisting of an elastomeric material renders possible an effective vibration damping of the entire bearing system. The elastomeric plastics material moreover prevents an inadmissibly high heat flow from the housing to the anti-friction bearing so that it is not excessively heated in operation.
The seal shown in Fig. 2 is intended for a cylindrical sliding bearing 36, in which a shaft 37 is rotatably mounted. The seal has again a supporting element 8a which is cylindrical in design and projects axially from the sliding bearing 36 at one end. At this end, the supporting element 8a is bent at right angles to the base part 11 a which is perpendicular to the seal axis A and has the shape of an annular disc. The thickness of the supporting element 8a and of its base part 11 a is constant over the entire length and the entire circumference. The radial width of the base part 11 a is substantially less than the axial length of the cylindrical supporting element part.The supporting element 8a forms one part of the retaining part 4a of the seal, whose sealing part 5a is designed as a sealing lip and, with a sealing edge 7a, rests on the shaft 37 at an axial distance from the sliding bearing 36. The sealing part 5a is designed in the same way as the sealing part in the constructional form shown in Fig. 1.
In addition to the supporting element 8a, the retaining part 4a comprises the coat 18a which consists of an elastomeric material and is provided both on the outside and the inside of the supporting element 8a and completely envelops this element. By this means, it is not with the supporting element 8a but with the cylindrical coating part 39, which bears against the inner wall 38a of the cylindrical supporting element part, that the seal rests on the outer surface 40 of the sliding bearing 36. The cylindrical external coating part 19a, which bears against the outside 41 of the cylindrical supporting element part, is designed in the same way as the coating part 1 9 of the seal shown in Fig. 1.The internal coating part 39 is provided on its inner wall with a profile 42 which is undulatory in an axial section and is designed in the same way as the profile 29a on the outside of the external coating part 19a. When the seal is placed on the sliding bearing 36, any tolerances in the design of the sliding bearing 36 can be easily compensated for with the inside profile 42. With a correspondingly large outside diameter of the sliding bearing 36, the elevations of the profile 42, which extend over the circumference of the coat 18a, are axially laterally dislodged so that they fill up the adjacent grooves. Since provision has also been made for the outside profile 29a, any tolerance at the housing end can be compensated for during the installation into the housing, as has been described with reference to
Fig. 1.
The coating part 34a, which is radial to the seal axis A and bears against the inside of the base part 11 a, merges in the inside cylindrical coating part 39 which extends over the entire axial length of the cylindrical retaining part.
The two cylindrical coating parts 19a, 39 have the same thickness, whereas the coating part 34a is approximately only half as thick as the cylindrical coating parts. With this constructional form, too, there is brought about considerable noise damping during operation since the supporting element 8a is completely embedded in the coat 18a. Over and above this, the coat 1 8a causes vibrations of the sliding bearing 36 to be absorbed to a high degree, as a result of the elastomeric material.
The heat transfer from the housing to the sliding bearing is so reduced, due to the complete embedding of the supporting element 8a in the coat 18a, that the sliding bearing is not heated to an inadmissibly high degree and the sliding friction properties thereof are not impaired.
The seal shown in Fig. 3 is again similar in design to the seal shown in Fig. 1. It also serves for an anti-friction bearing and differs from the constructional form shown in Fig. 1 only in that the cylindrical part 8b' of the supporting element 8b is also covered on its inside by a cylindrical coating part 39b. As provided for in the case of the seal shown in
Fig. 2, the frorit end 22b of the coat 1 8b merges via a conical surface 43 in the inner wall 44 of the cylindrical internal coating part 39b. Like the constructional form shown in
Fig. 2, the inner wall 44 is provided with a profile 42b which is undulatory in cross section, so that it is possible to fit the seal without any effort on the anti-friction bearing, even if there are fairly large variations in the external circumference of the anti-friction bearing.The cylindrical internal coating part 39b extends to the inside 45 of the base part
11 b of the supporting element 8b. As in the case of the two seals described previously, the seal can be easily placed on the anti-friction bearing since the retaining part 4b of the seal is cap-shaped. The installed position of the seal has been reached when the base part
11 b of the supporting element 8b rests with its inside 45 against the front end 1 2b of the outer race 2 of the anti-friction bearing.
The seal shown in Fig. 4 has, as the retaining part 4c, the cylindrical supporting element 8c and a varnish coat 46 which covers the inner surface of the supporting element 8c over almost the entire axial length thereof. The supporting element 8c preferably consists of metal and is constant in thickness over its entire length and over its circumference. By this means, the supporting element can be easily produced by cutting pipes to length. The varnish coat 46 is very thin compared to the thickness of the supporting element 8c and serves for improving the adhesion of the supporting element on the outer race 2 of the anti-friction bearing.The front end 1 6c of the supporting element 8c is slightly set back with respect to the front ends 27, 28 of the outer race 2 and the inner race 1 respectively so that the front ends of the two races form one end of the anti-friction bearing provided with the seal. The supporting element 8c projects axially from the antifriction bearing at the other end. The projecting part 47 serves for fastening the sealing part 5c, which is designed as a sealing lip and, with a circumferential sealing edge 7c, rests on the outer surface 6 of the inner race 1 of the anti-friction bearing. Corresponding with the previously described constructional forms, the sealing part Sc is arranged at an acute angle to the seal axis and projects into the space enclosed by the supporting element 8c.The sealing part merges in an annulardisc-shaped connecting piece 48 which is perpendicular to the seal axis and is at a distance from the front ends 12, 49 of the outer race 2 and the inner race 1 respectively.
On the outer edge 50, the connecting piece 48 is thickened in the direction of the supporting element 8c which engages in the thickened outer edge 50 with its projecting part 47. By this means, the supporting element 8c is frontally embraced by the thickened outer edge 50 over its entire circumference. The varnish coat 46 extends to the outer edge 50. The sealing part Sc and the connecting piece 48 consists of an elastomeric plastics material. Considered in an axial section according to Fig. 4, the sealing part has a rectangular cross section which tapers slightly in the direction of the free end. The outsides 30c and 31 c forming the sealing edge 7c are at obtuse angles to each other and are inclined to the seal axis.
In the constructional form shown in Fig. 5, the supporting element 8d is similar in design to that of the constructional form shown in
Fig. 3. It also has the cylindrical part 8d' which curvedly merges in the base part 11 d which is in the shape of an annular disc and is perpendicular to the seal axis. The supporting element preferably consists of a metallic material so that the retaining part 4d of the seal is sufficiently firm. As in the previously described constructional forms, the thickness of the supporting element is preferably less than 0.3mm. As a result, the thickness of the retaining part is only minimal so that the outside diameter of the anti-friction bearing is not substantially increased by the seal.The cylindrical supporting element part 8d' is covered by two coating parts 19d, 39d over its axial length and over its circumference, which engage over the front end 1 6d of the cylindrical supporting element part 8d' and merge one within the other. The two coating parts 19d, 39d are provided with profiles 29d and 42d respectively, which are undulatory in cross section. Like the exemplified embodiment shown in Fig. 3, this provides the possibility of compensating for any tolerances of both the installation space and the anti-friction bearing during the installation or the slidingon of the seal in a simple manner. Furthermore, the profiles ensure a reliable fit of the seal.The coating part 39d bearing against the inner surface of the cylindrical supporting element part 8d' extends to the base part 11 d, while the coating part 1 9d resting on the outer surface of the supporting element part extends to the transition zone 15d from the cylindrical supporting element part 8d' into the base part 11 d. The sealing part 5d is designed identically with the sealing part shown in Fig. 4 and merges in a connecting piece 48d which extends however only over half the radial width of the base part 11 d and is without a connection to the two coating parts 19d, 39d. The connecting piece 48d consists of two annular-disc-shaped sections 51 and 52 which cover the base part 11 d on the inside and outside and are integrally formed with the sealing part 5d.The radially internal edge of the base part 11 d is by this means embraced by the connecting piece over its entire circumference. Since the sealing part 5d and the coat 1 8d are not connected together, the two parts may consist of different materials. This allows the materials to be optimally adapted to their respective purpose of use.
In the constructional form shown in Fig. 6, the supporting element 8m consists of the cylindrical supporting elements part 8m' which merges via the curved transition zone
15m in the base part 11 m which projects from the outer race 2 of the anti-friction bearing radially inwardly. The cylindrical supporting element part 8m' is on the inside completely covered by the coating part 39m which rests on the outer surface 9 of the outer race 2 of the anti-friction bearing and merges in the outer coating part 1 9m of the coat 1 8m.It has a profile 42m, which is undulatory in an axial section, and covers the cylindrical supporting element part 8m' nearly to the transition zone 15m. The coat 1 8m covers the front end 1 6m of the supporting element part over the entire circumference thereof. The retaining part 4m extends to the front end 27 of the outer race 2. The inner coating part 39m merges in the transition piece 48m section 51 m which covers the inside of the base part 11 m. The base part 11 m is covered on the underside nearly to the transition zone 15m by the section 52m of the connecting piece 48m.The seal sits, with the coa parts 39m and 51m, directly on the outer race 2 of the anti-friction bearing. The transition piece 48 is frusto-conical in design and extends outwardly from the base part 11 m. It ends approximately at half the radial width of the inner race 1 of the anti-friction bearing. The radially internal edge 55 of the connecting piece 48m embraces a radial section 56 of a sealing part 5m which has a cylindrical section 57 which is parallel to the seal axis and merges curvedly in the radial annular-discshaped section 56. The cylindrical section 57 bears with its face against the front end 49 of the inner race 1 of the anti-friction bearing approximately- at half the radial width thereof.
The integrally formed sealing part 5m may consist of metal but also of plastics material.
The connecting piece 48m is so designed that it presses the sealing part 5m with its cylindrical section 57 against the front end 49 of the inner race 1. Advantageously, the connecting piece 48m is relatively thin in design so that it can exert a sufficiently high biassing force on the sealing part 5m. The annular-disc-shaped section 56 is outwardly directed from the cylindrical part 57 in the direction of the outer race 2 of the anti-friction bearing.
The constructional form shown in Fig. 7 is similar in design to the seal shown in Fig. 4.
Here, too, the sealing part 5f is connected to the cylindrical supporting element 8f via the flat connecting piece 48f which is perpendicular to the seal axis. The projecting part 47f of the supporting element, with its free end, is embedded in the thickened edge 50f of the connecting piece 48f so that the projecting part 47f is embraced by the outer edge on the outside and on the inside. The inside part 53 of the outer edge 50f has however been continued to the front end 1 6f of the supporting element 8f and by this means forms an internal coating part 39f which surrounds the supporting element on the inside over its entire circumference. The inside of the coating part is provided with a profile 42f which is undulatory in an axial section. The coating part 39f is integrally formed with the connecting piece 48f and the sealing part 5f.Due to the profile 42f, an easy fitting of the seal on the bearing is ensured.
The seal shown in Fig. 8 differs from the constructional form shown in Fig. 7 only in that it is not the inside part but the outside part 54 of the thickened outer edge 50g that has been lengthened to form the outer coating part 1 9g which extends to the front end 1 6g of the cylindrical supporting element part 89 and is provided over the entire circumference on the supporting element. The coating part 1 9g is provided with the profile 299, which is undulatory in an axial section, and is integrally connected to the connecting piece 489 and the sealing part 5g. The profile 299 ensures an easy installation of the seal in the housing receiving the bearing.This constructional form allows installation tolerances of the installation hole in the housing to be compensated for due to the profile 299, while the seal shown in Fig. 7 allows tolerances of the external circumference of the anti-friction bearing to be compensated for on account of the profile 42f. Since the inside and outside coating parts 39f and 1 9g consist of the same material as the sealing parts 5f, 5g, there is also brought about sealing on the outside of the anti-friction bearing and on the outside of the seal respectively. The sealing parts 5f, 5g resting on the outer surface of the inner race of the anti-friction bearing seal off the antifriction bearing and furthermore prevent the admission of dirt particles to the rolling elements.
The two parts 53h and 54h of the outer edge 50h of the seal shown in Fig. 9 have been lengthened to form the inside and outside coating parts 39h and 1 9h which cover the cylindrical supporting element 8h on the inside and outside over the entire circumference and the entire axial length thereof. Only the front end 1 6h is free, which lies with the ends of the coating parts 19h, 39h in a common radial plane of the seal. The two coating parts are each provided with the profile 29h. This construction renders possible an optimum assembly in cases where an adequate radial construction space is available.
The seal shown in Fig. 10 has the supporting element 8i which consists of the cylindrical supporting element part 8i' and the base part 11 i which is disposed radially to the seal axis and merges curvedly in the supporting element part 8i'. The supporting element is consequently equal to the supporting element constructions shown in Figs. 1, 3, 5 and 6. It has a constant thickness throughout and preferably consists of metal. The sealing part 5i is designed in the same way as in the constructional forms shown in Figs. 4 to 9. It merges directly in the connecting piece 48i, the outer section 52i of which bears against the underside of the base part 11 i and nearly covers this part to the transition zone 15i. The section 51 i of the connecting piece 48i, which rests on the inside of the base part 11 i, covers the base part completely on the inside and merges curvedly in the inner coating part 39i which covers the inner surface of the cylindrical supporting element part 8i' and merges in the outer coating part 1 9i which rests on the outer surface of the cylindrical supporting element part. The front end 1 6i of the cylindrical supporting element part 8i' is by this means covered by the coat 1 8i over the entire circumference of the supporting element.The outer coating part 1 9i ends, at a short distance from the transition zone 15i, between the cylindrical supporting element part 8i' and the base part 11 i. By this means, the transition zone 15i is free on the outside, whereas it is covered by the coat on the inside. By this means, a high degree of sealing between the seal and the outer race of the anti-friction bearing is brought about.
The complete internal lining with the coat 18i, which advantageously consists of rubber, prevents any corrosion being formed from the inside. The transition zone 1 ski not covered by the coat 1 8i renders possible in a simple manner the application of an assembly tool for the installation of the seal.
In all the constructional forms described, the retaining part of the seal is cap-shaped and open on one side so that it can be easily placed on the anti-friction bearing. In all the constructional forms, the supporting element has a minimal thickness of less than 0.3 mm so that the seal does not increase the thickness of the outer circumference of the antifriction bearing or sliding bearing to a considerable extent and the installation space provided for the anti-friction bearings has to be increased to only an inconsiderable extent.
The retaining part of the seal placed on the anti-friction bearing acts as a kind of insulator which prevents an inadmissibly high heat flow from the housing to the bearing. If the retaining parts are provided with coats consisting of elastic material, there is also brought about a high degree of vibration damping of the entire bearing system. Over and above this, the retaining part engaging over the bearing serves as a noise silencing element which at least largely prevents the transmission of noise from the bearing into the housing receiving it. By this means, there does not occur any considerable noise formation use of the anti-friction or sliding bearings provided with the described seals. The coats may be glued onto the supporting elements; however, preferably they are vulcanised on these so that a fixed connection between the coat and the supporting element is brought about. This eliminates the danger of the coat being pulled from the supporting element when the slidingon operation on the bearing or the installation into the bearing housing is effected. The described and shown seals can be used both for anti-friction bearings and sliding bearings. In the case of sliding bearings, the sealing part rests on the shaft to be sealed off, as shown in respect of the constuctional form of Fig. 2.
In the case of anti-friction bearings, the sealing part rests on the outer surface of the inner race and by this means seals off the space between the two races of the anti-friction bearings from the outside.
Claims (11)
1. A seal for an anti-friction or sliding bearing, comprising at least one sealing part provided on a retaining part, wherein the retaining part is cap-shaped and has a contact surface which extends over the circumference of the bearing, the sealing part has a sealing lip which extends over the circumference of the seal, and is transversely arranged in relation to the retaining part, and the retaining part comprises stiffening means.
2. A seal as claimed in Claim 1, wherein the retaining part is of cylindrical form and at one end thereof has a base which extends transversely of the seal axis and which is partly formed by the sealing part and has a centrally disposed passage port.
3. A seal as claimed in Claim 1 or Claim 2, wherein the retaining part has a supporting element.
4. A seal as claimed in Claim 3, wherein the supporting element consists of a metallic material.
5. A seal as claimed in Claim 3 or Claim 4,-wherein the supporting element is capshaped.
6. A seal as claimed in any one of Claims 3 to 5, wherein the sealing part is of an elastic material and the supporting element, at least with an annular end zone thereof, is embedded in said elastic material.
7. A seal as claimed in Claim 6, wherein the supporting element has a cylindrical zone which is provided with an elastic coat, and said coat consists of an elastic material which is different from that of the sealing part.
8. A seal as claimed in any one of Claims 1 to 7, wherein the thickness of the sealing part and that of the retaining part are substantially equal.
9. A seal as claimed in any one of Claims 3 to 8, wherein the supporting element is provided with a varnish coat on its inside and/or outside.
10. A seal as claimed in any one of
Claims 1 to 9, wherein the sealing part is connected to the retaining part via a connecting piece which is disposed transversely to the seal axis.
11. A seal as claimed in Claim 10, wherein the connecting piece is annular and with an outer edge embraces a front end of the retaining part over the circumference thereof.
1 2. A seal as claimed in any one of
Claims 3 to 11, wherein the sealing part, with a connecting piece, embraces a radially disposed base part of the supporting element from the radially inner edge thereof.
1 3. A seal for an anti-friction or sliding bearing substantially as hereinbefore described with reference to and as illustrated in any one of Figs. 1 to 10.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3219156A DE3219156A1 (en) | 1982-05-21 | 1982-05-21 | GASKET FOR ROLLING AND / OR SLIDING BEARINGS |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| GB8313078D0 GB8313078D0 (en) | 1983-06-15 |
| GB2123096A true GB2123096A (en) | 1984-01-25 |
| GB2123096B GB2123096B (en) | 1986-05-29 |
Family
ID=6164195
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08313078A Expired GB2123096B (en) | 1982-05-21 | 1983-05-12 | A seal for an anti-friction or sliding bearing |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS58203223A (en) |
| DE (1) | DE3219156A1 (en) |
| FR (1) | FR2527283B1 (en) |
| GB (1) | GB2123096B (en) |
| SE (1) | SE8302711L (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2167502B (en) * | 1984-11-09 | 1989-04-26 | Skf Gmbh | Journal box with inserted sealing ring |
| US5022770A (en) * | 1989-08-07 | 1991-06-11 | Bendix Espana S.A. | Rotating and sealed bearing assembly of a first member rotating in a second member |
| GB2256236A (en) * | 1991-06-01 | 1992-12-02 | Luk Lamellen & Kupplungsbau | Sealed rolling bearing |
| US5370404A (en) * | 1992-03-27 | 1994-12-06 | Firma Carl Freudenberg | Radial lip seal with interposed bearing |
| US5509667A (en) * | 1992-11-04 | 1996-04-23 | Firma Carl Freudenberg | Radial lip seal for a shaft in a housing |
| US5978986A (en) * | 1996-04-02 | 1999-11-09 | Wall Verkenhrsanlagen Gmbh | Public convenience unit |
| EP1058017A2 (en) * | 1999-06-01 | 2000-12-06 | Firma Carl Freudenberg | Sealing device |
| EP1072450A2 (en) * | 1999-07-30 | 2001-01-31 | Firma Carl Freudenberg | Strut support bearing |
| US8702314B2 (en) * | 2012-03-15 | 2014-04-22 | Jtekt Corporation | Rolling bearing unit |
| EP3672032A1 (en) * | 2018-12-21 | 2020-06-24 | Bühler Motor GmbH | Electric motor |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ES2001268A6 (en) * | 1986-08-27 | 1988-05-01 | Bendix Espana | Supporting and sealing means for a first element rotatably mounted in a second element. |
| IT223159Z2 (en) * | 1991-03-22 | 1995-06-13 | Skf Ind Spa | SUPPORT AND HOLDING COMPLEX FOR THE INCLUSION BETWEEN TWO BODIES IN RELATIVE ROTATION |
| FR2688836B1 (en) * | 1992-03-19 | 1996-06-07 | Skf France | SUSPENSION STOP BEARING FOR VEHICLE AND MOUNTING METHOD THEREOF. |
| DE19648602C2 (en) * | 1996-11-23 | 2000-01-05 | Freudenberg Carl Fa | Sealing arrangement |
| JP2007040484A (en) * | 2005-08-04 | 2007-02-15 | Nsk Ltd | Soft rubber wound bearing |
| JP2007309389A (en) * | 2006-05-17 | 2007-11-29 | Nsk Ltd | Hub unit bearing |
| FR2921016B1 (en) * | 2007-09-19 | 2009-12-18 | Skf Ab | SUSPENSION STOPPER DEVICE AND FORCE LEG |
| DE102014204608A1 (en) * | 2014-03-12 | 2015-09-17 | BSH Hausgeräte GmbH | vacuum cleaner fan |
| CN112303107A (en) * | 2020-10-09 | 2021-02-02 | 贵州兴利旺轴承有限公司 | High-speed low-noise probing type bearing sealing assembly |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1054169A (en) * | ||||
| GB1119116A (en) * | 1965-07-20 | 1968-07-10 | Koyo Seiko Company Ltd | A grease sealed bearing |
| GB1167201A (en) * | 1966-03-18 | 1969-10-15 | Timken Roller Bearing Co | Bearing Seal Case Construction. |
| GB1181045A (en) * | 1967-10-14 | 1970-02-11 | Toyo Bearing Mfg Kabushiki Kai | Improvements in or relating to Sealing Device for Antifriction Bearing |
| GB1278386A (en) * | 1970-02-19 | 1972-06-21 | Federal Mogul Corp | Shaft seal with expandable outer periphery |
| GB1371341A (en) * | 1971-02-25 | 1974-10-23 | Skf Uk Ltd | Seals such as are used for a rolling bearing |
| GB1519048A (en) * | 1974-09-24 | 1978-07-26 | Skf Ind Trading & Dev | Hub bearing unit |
| GB1530987A (en) * | 1976-11-02 | 1978-11-01 | Koyo Seiko Co | Antifriction bearing including a seal assembly |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2173250A (en) * | 1938-05-19 | 1939-09-19 | Norma Hoffman Bearings Corp | Antifriction bearing |
| DE1008061B (en) * | 1954-04-27 | 1957-05-09 | Walter Pankratz | Shaft seal, in connection with roller bearings |
| GB1064133A (en) * | 1962-12-31 | 1967-04-05 | Rubber Plastics Ltd | Improvements in and relating to ball or roller bearings |
| FR1402261A (en) * | 1963-07-23 | 1965-06-11 | Goetzewerke | Rotary seal |
| NL6808207A (en) * | 1967-06-16 | 1968-12-17 | ||
| DE1917623A1 (en) * | 1969-04-05 | 1970-10-08 | Hans Guentner | Air-cooled freezing mixture condenser |
| DE1964998C3 (en) * | 1969-12-24 | 1979-02-15 | Bayer Ag, 5090 Leverkusen | Process for the production of polyurethane elastomers |
| ZA735737B (en) * | 1972-09-15 | 1974-06-26 | Federal Mogul Corp | Preloading and sealing system for clutch bearings |
-
1982
- 1982-05-21 DE DE3219156A patent/DE3219156A1/en active Granted
-
1983
- 1983-05-11 SE SE8302711A patent/SE8302711L/en unknown
- 1983-05-11 JP JP58081051A patent/JPS58203223A/en active Granted
- 1983-05-12 GB GB08313078A patent/GB2123096B/en not_active Expired
- 1983-05-17 FR FR8308161A patent/FR2527283B1/en not_active Expired
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1054169A (en) * | ||||
| GB1119116A (en) * | 1965-07-20 | 1968-07-10 | Koyo Seiko Company Ltd | A grease sealed bearing |
| GB1167201A (en) * | 1966-03-18 | 1969-10-15 | Timken Roller Bearing Co | Bearing Seal Case Construction. |
| GB1181045A (en) * | 1967-10-14 | 1970-02-11 | Toyo Bearing Mfg Kabushiki Kai | Improvements in or relating to Sealing Device for Antifriction Bearing |
| GB1278386A (en) * | 1970-02-19 | 1972-06-21 | Federal Mogul Corp | Shaft seal with expandable outer periphery |
| GB1371341A (en) * | 1971-02-25 | 1974-10-23 | Skf Uk Ltd | Seals such as are used for a rolling bearing |
| GB1519048A (en) * | 1974-09-24 | 1978-07-26 | Skf Ind Trading & Dev | Hub bearing unit |
| GB1530987A (en) * | 1976-11-02 | 1978-11-01 | Koyo Seiko Co | Antifriction bearing including a seal assembly |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2167502B (en) * | 1984-11-09 | 1989-04-26 | Skf Gmbh | Journal box with inserted sealing ring |
| US5022770A (en) * | 1989-08-07 | 1991-06-11 | Bendix Espana S.A. | Rotating and sealed bearing assembly of a first member rotating in a second member |
| GB2256236A (en) * | 1991-06-01 | 1992-12-02 | Luk Lamellen & Kupplungsbau | Sealed rolling bearing |
| GB2256236B (en) * | 1991-06-01 | 1995-12-06 | Luk Lamellen & Kupplungsbau | Rolling bearing |
| US5370404A (en) * | 1992-03-27 | 1994-12-06 | Firma Carl Freudenberg | Radial lip seal with interposed bearing |
| US5509667A (en) * | 1992-11-04 | 1996-04-23 | Firma Carl Freudenberg | Radial lip seal for a shaft in a housing |
| US5978986A (en) * | 1996-04-02 | 1999-11-09 | Wall Verkenhrsanlagen Gmbh | Public convenience unit |
| EP1058017A2 (en) * | 1999-06-01 | 2000-12-06 | Firma Carl Freudenberg | Sealing device |
| EP1058017A3 (en) * | 1999-06-01 | 2001-02-28 | Firma Carl Freudenberg | Sealing device |
| EP1072450A2 (en) * | 1999-07-30 | 2001-01-31 | Firma Carl Freudenberg | Strut support bearing |
| EP1072450A3 (en) * | 1999-07-30 | 2001-11-07 | Firma Carl Freudenberg | Strut support bearing |
| US8702314B2 (en) * | 2012-03-15 | 2014-04-22 | Jtekt Corporation | Rolling bearing unit |
| EP2639468A3 (en) * | 2012-03-15 | 2014-12-03 | Jtekt Corporation | Rolling bearing unit |
| EP3672032A1 (en) * | 2018-12-21 | 2020-06-24 | Bühler Motor GmbH | Electric motor |
Also Published As
| Publication number | Publication date |
|---|---|
| SE8302711L (en) | 1983-11-22 |
| FR2527283A1 (en) | 1983-11-25 |
| SE8302711D0 (en) | 1983-05-11 |
| DE3219156C2 (en) | 1992-03-05 |
| DE3219156A1 (en) | 1983-11-24 |
| GB2123096B (en) | 1986-05-29 |
| JPH0346688B2 (en) | 1991-07-17 |
| JPS58203223A (en) | 1983-11-26 |
| FR2527283B1 (en) | 1989-06-09 |
| GB8313078D0 (en) | 1983-06-15 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| 746 | Register noted 'licences of right' (sect. 46/1977) |
Effective date: 19980415 |
|
| PCNP | Patent ceased through non-payment of renewal fee |
Effective date: 19990512 |