JPS58203223A - Packing for roller bearing and/or plain bearing - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a packing for rolling bearings and/or sliding bearings according to the prerequisite concept of the first claim.

The task of the packing of a rolling bearing is, for example, to retain the lubricant in the rolling bearing and to prevent the ingress of impurities. The rolling bearing has an outer rolling bearing race (σ) and an inner rolling bearing race (+), of which the outer rolling bearing race is fixed in the casing, and the inner rolling bearing race is fixed through the casing (11). It is non-rotatably coupled to the extending axis. Bread
The following σ) 1: A buffer-like sealing plate is well known.
There is C. That is, the sealing plate fixed between the outer rolling bearing race σ) and the casing wall, =iQit between the inner rolling bearing race and the shaft groove. Each free end is supported on the end face of the other rolling bearing race, so that the area between the two rolling bearing races is sealed against the outside.The tightly clamped part of the sealing plate is , which forms the retaining part of the seal and whose unidirectional edge serves as a sealing part which joins under damping prestress to the end face of the rolling bearing race. Direct bonding to the casing wall, as a result of which the noise generated during rotation of the shaft is transmitted into the casing, creating an unpleasant noise.Due to the direct bonding of the outer rolling bearing race to the casing wall, a considerable amount of heat is generated during operation. flows from the casing to the rolling bearing, resulting in faster wear.Furthermore, it is difficult to install a cushioning sealing plate.

SUMMARY OF THE INVENTION The object of the invention is to design a seal that takes into account simple installation and long service life, and which reduces the operating noise of a rolling bearing to a high degree.

The above object is achieved according to the invention by the characteristic features of claim 1.

The seal according to the invention surrounds, by means of its dome-shaped holding part, a bearing which abuts on the contact surface of the holding part. This prevents direct contact between the outer surface of the bearing and the casing in which the nozzle is mounted, and the transmission of noise to the casing receiving the bearing is significantly reduced. A sealing part located transversely to the holding part seals the outer surface of the inner race of a rolling bearing or, when used for a plain bearing, against the shaft. Furthermore, the packing according to the present invention can effectively suppress vibrations of the entire bearing structure. The dome-shaped retaining portion also acts as an insulator that prevents large amounts of heat from flowing from the casing to the bearing, so that the bearing does not fail prematurely due to wear.

The seal according to the invention only needs to be attached to the bearing using a dome-shaped holding part, and is therefore easily installed. Thereby, the bearing can already be provided with a seal before it is installed in the respective housing, so that the installation of the bearing is considerably simplified.

Due to its hardness, the holding part can be reliably pressed onto the bearing, so that a secure fit and a perfect seal are guaranteed.

In particular, the sealing portion joins the attached opposing surface by a sealing edge. The jacket according to the invention can therefore not only be used for sealing against dirt, but also be installed for sealing against oil, for example.

Other features of the present invention will become apparent from the following claims, the description, and the drawings.

The invention will now be explained in more detail with reference to some embodiments and with reference to the accompanying drawings.

The seal according to the invention can be installed on rolling bearings as well as sliding bearings. The packing illustrated in FIG. 1 is provided for a rolling bearing that has an inner race 1 and an outer race 2, and between these races a rolling element 6, in this embodiment a rolling ball, is supported. There is. The seal has a retaining part 4 and a sealing part 5 which rests tightly on the outer surface 6 of the inner race 1. The sealing part 5 is a lip-like seal which rests on the outer surface 6, in particular by a sealing post 7. □゛"□: 11"The holding part 4 is
It has a cylindrical support 8 which is of cylindrical design and rests on the outer surface 9 of the outer race 2 over substantially the entire axial length of the outer race. The holding part 4 is integrally formed with a bottom part 10 having a centrally located through hole 10' extending perpendicular to the axis of the holding part. The support 8 is bent arcuately in cross section and transitions into the bottom part 11 . The bottom portion 11 joins the end face 12 of the outer race 2 and projects radially beyond the outer race 2 towards the inner race 1 . The bottom portion 11 is formed into a disk shape, and its end surface 13 is formed into a hypothetical cylindrical portion 14 that includes the center M of the rolling element 6.
It's within. There is therefore a sufficiently large fastening surface in the bottom part 11 for the sealing part 5, while the bottom part is in such a way that the inner race 1 can be deformed elastically without any hindrance by the bottom part. A sufficiently large distance from the outer surface 6 is maintained.

The seal rests directly on the outer surface 9 and on the end face 12 of the release 7 2 by means of the contact surface 68 formed by the inner wall of the support 8 and the bottom part 11 of the support 8 . The radius of curvature of the transition region 15 from the cylindrical part 8' of the support 8 to the bottom part 11 of the holding part 4 is smaller than the radius of curvature of the bending transition from the outer surface 9 to the end surface 12 of the outer ring 2. By doing so, when attaching the packing to the outer race, the bottom part 1
1 is always in contact with the end face 12.

The support 8 has a constant outer diameter over its axial length and a uniform thickness over approximately its axial length. However, only in the area of the free end face 16 the support 8 has a larger internal diameter than in the other areas. The support 8 therefore does not rest directly on the outer surface 9 of the outer ring 2 in the region of its end face 16 . The support 8 thus has a thinner wall portion 17 whose axial length corresponds to approximately y9 of the overall axial length of the support. Similarly, bottom part 1
1 has a constant thickness over its entire radial width, which is equal to the thickness of the cylindrical part of the support 8.

The support 8 provides the necessary stiffness to the packing and is preferably made of metal, but can also be made of other suitable materials. The thickness of the carrier 8 is advantageously less than 0.61II11, so that the thickness of the seal is only small and only slightly increases the outer diameter of the rolling bearing. Therefore, large installations do not require space for installing rolling bearings with seals.

The support 8 is provided with a coating 18 made of elastomer on its outer surface. The covering part 18 includes a cylindrical part 19 placed on the cylindrical part of the support 8 and a disc-shaped covering part 20 that completely covers the bottom part 11 of the support 8 with its outer surface and is located in the radial direction. have. The cylindrical covering part 19 is connected to the wall part 1
7 and is joined to the inner wall of the wall section 17 by an annular section 21. The inner surface of the annular portion 21 is
It forms a continuous continuation of the inner surface of the cylindrical support part 8. The packing is an annular part 2 made of an elastomer material.
1 rests on the outer surface 9 of the outer race 2 in the area of the wall section 17 with the outer ring 2 . Cylindrical annular portion 21 of the covering portion 18
is considerably thinner than the coating resting on the outer surface of the support 8. That is, it is considerably thinner than a jacket which has a substantially constant thickness over its entire axial length and radial width. The annular end surface 22 of the covering portion 18 is flat and located perpendicular to the axis of the packing.

The end 22 is connected via a conical surface 26 to a cylindrical covering surface 24 of the covering part 18 . The cylindrical covering surface 24 transitions via a conical surface 25 into a planar outer surface 26 of the covering part 20 located radially relative to the axis of the packing. The conical surface 25.25 facilitates the installation of the rolling bearing in the annular groove of the casing that receives the bearing. The end 22 of the sheathing 18, which is spaced from the end 16 of the cylindrical support part, is located at a distance from the end 22 of the outer race 2 and the inner race 1.
7.28, so that in this area the seal does not protrude beyond the rolling bearing, thus facilitating installation.

The cylindrical cover surface 24 is provided with a profile 29 so that mounting tolerances can be easily compensated for without impairing the sealing properties. This profile 29 has a corrugated design in axial section, so that grooves are formed which extend over the periphery of the cylindrical covering surface 24 and are in each case separated from one another by ridges. When the rolling bearing is inserted into the annular groove of the casing, the raised part is deformed in the axial direction according to the mounting tolerance and is pushed away in the axial direction so as to fill the adjacent groove, so that the covering part 18 is , the mounting results in a state with a smooth cylindrical outer surface.

The outer surface 26 of the radial disc-shaped covering part 20 is of flat design and lies perpendicular to the axis of the packing.

The covering part 20 transitions into a sealing part 5 which is located at an acute angle to the axis of the packing and projects into the space enclosed by the cylindrical packing part. The outer surface 26 of the covering part 20 transitions into the outer surface 30 of the sealing part 5 in an arc-shaped manner.

This outer surface 30 transitions approximately perpendicularly to the end surface 31 of the sealing part 5 under the formation of a sealing wave 7 . Furthermore, the end portion 31 has an inner surface 62 converging towards the bottom portion 11 in relation to the outer surface 30.
It transitions in an arc shape to . Due to this configuration, the sealing part 5 is formed in the shape of a truncated cone and its cross section tapers from the end face 61. The inner surface 32 transitions in an arcuate manner into an inner surface 36 of the disc-shaped covering part 64, which is located perpendicularly to the axis of the seal. Disc-shaped covering part 6
4 joins the inner surface of the bottom portion 11 of the support 8 and terminates at a distance from the inner wall 35 of the outer race 2. The thickness of the covering portion 34 is thinner than the thickness of the covering portion 20 and approximately equal to the thickness of the annular portion 21 of the covering portion 18. The bottom part 11 is surrounded by a covering part 18 at its end face 13 in accordance with the above-described arrangement.

During installation, the rolling bearing is joined to the bearing groove of the casing by means of a covering 18. As a result, the introduction of noise into the housing is significantly prevented, so that only very low noise is generated during operation. moreover,
Since the covering portion 18 is made of an elastomer material, vibrations of the entire bearing structure can be effectively suppressed. The elastomeric composite also prevents unduly high thermal blockage from the casing to the rolling bearing, so that the rolling bearing does not heat up excessively during operation.

The packing shown in FIG. 2 is provided on a cylindrical plain bearing 66 in which a shaft 67 is rotatably supported. This packing, like the packing of FIG. 1, is of cylindrical design and has a support 8a which projects axially beyond the plain bearing 66 at one end. At this end, the support 8a is bent downwards at right angles in the direction of a bottom part 11a which is perpendicular to the axis A of the packing and is formed in the form of a disc. The support 8a and its bottom portion 11a have a constant thickness over their entire length and around their circumference. The radial width of the bottom part 11a is considerably less than the axial length of the cylindrical support part.

The support 8a forms part of the holding part 4a of the packing. The sealing part 5a of the seal is formed as a lip seal and rests on the shaft 67 at an axial distance from the plain bearing 66 by a sealing wave 7a. The sealing part 5a is formed in the same way as in the embodiment of FIG.

The holding portion 4a has a covering portion 18a made of an elastomer material on the outside of the support 8a. The covering portion 18a is provided on the outer surface and the inner surface of the support 8a, and completely covers the support 8a. Thereby, the packing is supported by the support 8a.
It rests on the outer surface 40 of the plain bearing 36 by a cylindrical covering part 39, which is joined to the inner wall 38a of the cylindrical support part, rather than by the cylindrical support part. Outer surface 4 lb of the cylindrical support part: The joining cylindrical outer covering part 19a is designed similarly to the covering part 19 of the packing in FIG. The inner covering part 69 has on its inner wall a deformed part 42 having a corrugated cross-section in the axial direction. This irregularly shaped portion 42 is formed in the same manner as the irregularly shaped portion 29a on the outer surface of the outer covering portion 19a.

When attaching the seal to the plain bearing 66, the inner profile 42 makes it possible to easily compensate for tolerances in the construction of the plain bearing 36. If the plain bearing 66 has a suitably large outer diameter, the ridges of the profile 42 extending beyond the curved surface of the sheathing 18a are pushed aside in the axial direction, so that these ridges are in contact with the adjacent grooves. fill in. Outer quality 2,8□6,6ゎc yt h”□・:,
□...'f, = a15%! 111LM L As explained above, the tolerance on the casing side can be corrected during installation to the casing.

The covering part 34a, located radially with respect to the axis A of the packing and adjoining the inner surface of the bottom part 11a, transitions into an inner cylindrical covering part 39 which extends over the entire axial length of the cylindrical holding part.

Both cylindrical covering parts 19a, 39 have the same thickness, while the thickness of the covering part 54m is only approximately half the thickness of these cylindrical covering parts. Support body 8a is covered part 18a
Since it is completely embedded inside, this embodiment also allows for considerable noise reduction during operation. Furthermore, since the covering portion 18a is made of an elastomer material, the vibration of the sliding bearing 36 is suppressed to a high degree by the covering portion 18a. Heat transfer from the casing to the plain bearing is
The complete embedding of the support 8a in the sheath 18a ensures that the plain bearing is not heated too strongly and that the sliding friction properties are not impaired to a considerable extent.

The fittings shown in FIG. 3 are formed similarly to the fittings shown in FIG. This packing is similarly used for rolling bearings, but differs from the embodiment shown in Fig. 1 in the following points:
．． The cylindrical part 8b' of the support 8b is also covered on its inner surface by a cylindrical covering part 39b. The end surface 22b of the covering portion 18b is connected to the cylindrical inner covering portion 39 via the conical surface 43, as in the case of the packing shown in FIG.
Moving on to the inner wall 44 of b. The inner wall 44, corresponding to the embodiment of FIG. 2, has a profile 42b with a corrugated cross section, so that the seal can be mounted on a rolling bearing without armor, even if the tolerances of the outer circumference of the rolling bearing are relatively large. Can be installed. The cylindrical inner covering portion 39 extends to the inner surface 45 of the bottom portion 11b of the support 8b. The packing is similar to both the packing mentioned above, but the holding part 4 of the packing is
Since b is formed into a dome shape, it can be easily attached to a rolling bearing. The installation condition of the packing is as follows.
This is obtained when the bottom part 11b of the support 8b is joined by its inner surface 45 to the end face 12b of the outer race 2 of the rolling bearing.

The packing shown in FIG. 4 has, as a holding portion 4C, a cylindrical support 8C and a layer 46 of lacquer covering the inner surface of the support 8C over substantially its entire axial length. Support 8C
is in particular made of metal and has a constant thickness over its entire length and circumference. Thereby, the support is simply produced by cross-cutting the tube. The lacquer layer 46 is considerably thinner than the thickness of the support 8C and is used to improve the adhesion of the support on the outer race 2 of the rolling bearing. The end surface 16C of the support body 8C is the end surface 27, 2 of the outer race 2 and the inner race 1.
8, so that the end faces of both races form one end of a rolling bearing with a seal. The support 8C projects beyond the rolling bearing in the axial direction at the other end. The protruding portion 47 is used to fix the sealing portion 5C. The sealing part 5C is formed as a lip-like seal and rests on the outer surface 6 of the inner race 1 of the rolling bearing by means of a pivoting seal 7C. The sealing part 5C is also arranged at an acute angle to the axis of the seal and projects into the space surrounded by the support 8'c, corresponding to each of the previously described embodiments. Sealing part 5
C transitions into a disc-shaped coupling member 48 located perpendicular to the axis of the packing. This coupling member 48 is located at a distance from the end faces 12, 49 of the outer race 2 and inner race 1. Furthermore, the coupling element 48 is designed to increase in thickness at the outer edge 50 in the direction of the support 8c, which engages the thickened outer edge 50 by means of the protrusion 47. The support 8C is therefore surrounded by a thick outer edge 50 at its end face over its entire circumference. The lacquer layer 46 extends to the outer edge 50. The sealing part 5c and the connecting member 48 consist of an elastomeric synthetic material. The sealed portion 5c is the fourth
In the axial section shown, it has a rectangular cross section that tapers slightly towards the free end. After sealing 7
The outer surfaces 50c and 31c forming c are located at obtuse angles to each other and are each located obliquely to the axis of the packing.

1) In the embodiment of FIG. 5, the support 8d is designed similarly to that of the embodiment of FIG. The support 8d likewise has a cylindrical portion 8d'. This cylindrical portion 8d' is
It transitions flexibly into a bottom portion 11d which is formed in the shape of a disk and is located perpendicular to the axis of the packing. Support body 8d
is in particular made of metallic material, so that the retaining part 4d of the seal is sufficiently hard. The thickness of the support is preferably 0.3 mm or less, as in the previous embodiments. Therefore, the thickness of the holding part is only small, so that the outer diameter of the rolling bearing is not significantly increased by the packing. The cylindrical support part 8d' has two covering parts 19d which, over its entire axial length and over its entire circumference, engage with the end face 16d of the cylindrical support part 8d' and which transition into each other; 59d. Both covering portions 19d, 39d include irregularly shaped portions 29d, 42d whose cross sections are formed in a waveform. Thereby, in accordance with the embodiment of FIG. 6, tolerances in space and rolling bearings can be easily compensated for when installing the seal. Furthermore, the irregularly shaped part also ensures a secure fit of the nokutsukin. Cylindrical support portion 8d
The covering part 59d adhering to the inner surface of the cylindrical support part 8d' extends to the bottom part 11d, - the covering part 19d resting on the outer surface of the force support part 11d'
It extends to a transition area 15d to 1d. The sealed portion 5d is
It is formed similarly to the sealing part of FIG. 4 and transitions to the coupling member 48d. However, the connecting member 48d only extends over half the radial width of the bottom portion 11d and is not connected to the covering portions 19d, 39d.

The coupling member 48d consists of two disc-shaped parts 51 and 52 which cover the bottom part 11d with their inner and outer surfaces and are integrally formed with the sealing part 5d. Therefore, the bottom part 11d
The radially inner edge of is surrounded all around by a coupling member. Since the sealing part 5d and the covering part 18d are not connected to each other, they can be made of different materials. It is therefore possible to optimally adapt the material to the respective intended use.

In the embodiment of FIG. 6, the support 8m consists of a cylindrical support section 8m' as follows. That is, the arc-shaped transition region 1
It consists of a support part 8m' which transitions via 5m to a bottom part 11m which projects radially inwardly from the outer race 2 of the rolling bearing. The cylindrical support part 8m' has a covering part 39 which rests on the outer surface 9 of the outer race 2 of the rolling bearing and which transitions into the outer covering part 19m of the covering part 18m.
It is completely covered inside by m. The covering part 18m has a profile 42m with a corrugated axial cross section and covers the cylindrical support part 8m' approximately up to the transition region 15m. Further, the covering portion 18m covers the entire circumference of the end surface 16m of the support portion. The holding part 4m is outer race 2
It reaches the end face 27 of. The inner covering portion 39m is a portion 51 of the coupling member 48m that covers the inner surface of the bottom portion 1tm.
Move to m.

The lower part of the bottom part 11m is covered by the part 52m of the coupling member 48m up to the dowel transition area 15m.

The seal rests directly on the outer race 2 of the rolling bearing by means of covering parts 59m and 51m.

The coupling member 48m is frustoconically shaped and extends outwardly from the bottom portion 11m. In addition, the connecting member 48m is
It ends at approximately half the radial width of the inner race 1 of the rolling bearing. The radially inner edge 55 of the coupling member 48fh is connected to a portion 56 located in the radial direction of the sealing portion 5m.
surround. The sealing part 5m has a cylindrical part 57 located parallel to the axis of the seal, which cylindrical part 57 transitions into a radial disk-shaped part 56 in an arc.

The cylindrical part 57 joins with its end face to the end face 49 of the inner race 1 of the rolling bearing at a position approximately half the radial width of the inner race. The integrally formed sealing part 5m can consist of metal, but can also consist of synthetic material.

The coupling member 48m connects the sealing portion 5m to its cylindrical portion 5.
7 so as to be pressed against the end surface 49 of the inner race 1. It is advantageous to design the connecting element 48m relatively thin, so that it can exert sufficiently high prestressing forces on the sealing part 5m.
The disc-shaped part 56 is oriented outwardly from the cylindrical part 57 in the direction of the outer race 2 of the rolling bearing.

The embodiment shown in FIG. 7 is constructed similarly to the seal of FIG. 4. In this embodiment as well, the sealed portion 5f is
It is connected to a cylindrical support 8f via a flat connecting member 48f located perpendicular to the axis of the packing.

The projecting part 47f of the support is embedded with its free end in the thickened edge 50f of the coupling member 48f, so that the projecting part 47f is surrounded on the outside and on the inside by the outer edge. However, the inner surface portion 53 of the outer edge 50f is
An inner covering portion 39f is formed which extends to the end face 16f of the support 8f and thus surrounds the support over its entire circumference with its inner surface. The covering portion 39f includes, on its inner surface, a deformed portion 42f whose cross section in the axial direction is formed in a waveform. Furthermore, the covering portion 59f is integrally formed with the coupling member 48f and the sealing portion 5f. Due to the irregularly shaped portion 42f,
Easy mounting of the seal onto the bearing is guaranteed.

The difference between the packing shown in FIG. 8 and the embodiment shown in FIG. 7 is that the outer surface portion 54 of the thick outer edge 50g is
An outer covering part 19 which extends to the end face 16g of the cylindrical support part 8g and is provided on the support over its entire length.
It has been extended to g. The covering portion 19g includes a deformed portion 29g having a corrugated cross section in the axial direction, and is integrally formed with the coupling member 48g and the sealing portion 5g. The profile 29g ensures easy attachment of the packing to the casing receiving the bearing. According to the embodiment shown in FIG.
9g, and the tolerance of the outer periphery of the rolling bearing can be corrected by the deformed portion 42f using the packing shown in FIG. Since the inner or outer covering portion 59f or 19g is made of the same material as the sealing portions 5f, 5g, a seal can also be obtained on the outer surface of the rolling bearing or on the outer surface of the packing. Sealing parts 5f, 5g, which rest on the outer surface of the inner race of the rolling bearing, seal the rolling bearing and also prevent dirt from entering the rolling elements.

In the packing shown in FIG. 9, the image portion 53h of the outer edge 50h
, 54h extend into inner and outer covering portions 59h, 19h which cover the cylindrical support 8h over its entire circumference and over its entire axial length on the inside and outside. ,<A portion 19h that covers the radial surface of the
, an end face 16h that is shared with the end of 39h and lies within its plane.
only is free. Both covered parts each have a deformed part 29.
h. Due to this irregularly shaped portion 29h, radial mounting is optimized when space can be fully utilized.

The packing shown in FIG. 10 includes a cylindrical support portion 8L',
It consists of a bottom part 11i which is located radially with respect to the axis of the packing and which transitions flexibly into a support part 81'. The support therefore corresponds to the support illustrated in FIGS. 1, 5, 5 and 6. The support has a generally uniform thickness and in particular consists of metal. The sealing portion 51 is formed as in the embodiment of FIGS. 4 to 9 and transitions directly into the coupling member 48t. Outer part 5 of the coupling member
2i joins the lower surface of the bottom part 11i and covers the bottom part 11i approximately up to the transition region 15i.

The part 51i of the coupling member 48i, which rests on the inner surface of the bottom part 111, completely covers the bottom part 1, 11 with its inner surface and transitions flexibly into the inner covering part 39i.

The inner covering part 691 covers the inner surface of the cylindrical support part 8i' and transitions into the outer covering part 19i, which rests on the outer surface of the cylindrical support part. The end face 16i of the cylindrical support part 81' is therefore covered by the covering 181 over the entire circumference of the support. The outer covering part 191 includes a cylindrical support part 8i' and a bottom part 11.
1 and end at a slight distance from the transition region 15i between 1 and 1. Thereby, the transition region 15i lies freely on the outer surface and is covered on one side by the covering. Therefore, a high degree of sealing is achieved between the packing and the outer race of the rolling bearing.

Corrosion occurring on the inside is prevented by completely covering the inside with a covering 18i, which advantageously consists of rubber. Furthermore, the transition area 151 not covered by the covering part 18i allows easy application of tools for attaching the gasket.

In all of the embodiments described above, the holding part of the seal is dome-shaped and open on one side, so that it can be easily mounted on a rolling bearing. Moreover, in all the embodiments, the support has a very thin thickness of less than 0.6 mm, so that the seal is not placed thickly on the rolling or sliding bearing, and moreover, There is no need for the installation space to be very large. The retaining portion of the packing attached to the rolling bearing acts as a type of insulator that prevents large amounts of heat from flowing from the casing to the bearing. Insofar as the holding part is provided with a covering made of elastic material, the vibrations of the entire bearing system are also considerably reduced. Furthermore, the retaining part that engages with the bearing is used as a sound deadening element which prevents at least to a considerable extent the transmission of noise from the bearing to the kennising that receives it. Therefore, no large noise is generated when installing a rolling bearing or a sliding bearing equipped with the above-mentioned packing. The coating can be adhered to the support, in particular baked onto the support, so that a firm bond is obtained between the coating and the support. Therefore, there is no fear that the covering portion will peel off from the support when it is attached to the bearing or when it is attached to the bearing casing. The seals described and illustrated can be installed both for rolling bearings and for plain bearings. In the case of plain bearings, the sealing part rests on the shaft to be sealed, as illustrated for the embodiment in FIG.

In the case of rolling bearings, the sealing part rests on the outer surface of the inner race and thus seals the space between the two races of the rolling bearing from the outside.

[Brief explanation of the drawing]

FIG. 1 is an axial sectional view of a first embodiment in which the packing according to the present invention is applied to a rolling bearing, FIG. 2 is a diagram showing a second embodiment in which the packing according to the present invention is applied to a sliding bearing, and FIG.
The figure is an axial sectional view corresponding to FIG. 1 of another embodiment in which the packing according to the invention is applied to a rolling bearing, and FIGS. 4 to 10 are views showing other embodiments of the packing according to the invention.

Claims (1)

[Claims] (1) In a packing for rolling bearings and/or sliding bearings comprising at least one sealing part provided in the holding part, the holding part (4) is formed in a dome shape, and has a bearing contact surface (38) extending over the entire circumference; the sealing part (5) has a lip-shaped seal extending over the entire circumference of the seal and is arranged transversely with respect to the retaining part; Patsukin is characterized by its hard parts. (2) the holding part (4) is formed in a cylindrical shape and has at one end a bottom part (10) extending transversely to the axis of the packing, the bottom part being formed in part by the sealing part (5);
The gasket according to claim 1, further having a through hole (10') in the center. (6) The packing according to claim 1 or 2, characterized in that the holding portion (4) has a support (8). (4) The packing according to claim 3, wherein the support (8) is made of a metal material. (5) Claim 6 or 4, characterized in that the support (8) is likewise dome-shaped.
Patsukin described in section. (6) The support body (8) is embedded in the elastic material of the sealing part (5) at least by its annular end region. Patskin as described in any one of the above. (7) The support body (8) has a cylindrical region, and this cylindrical region is provided with an elastic covering made of another elastic material different from the material of the sealing portion (5). The packing according to any one of claims 6 to 6. (8) Claims 1 to 7 characterized in that the thickness of the sealing portion (5) and the holding portion (4) are approximately equal.
The patch skin described in any one of the paragraphs. (9) The carrier (8) is provided with a lacquer coating on its inner and/or outer surface. Patsukin. (10) The sealing part (5c) is aligned with the axis of the packing.
The holding part (
Packing according to any one of claims 1 to 9, characterized in that it is combined with 4c) and in particular with a support (8c). (11) The coupling member (48) is formed in an annular shape, and the outer edge (50) surrounds the end face of the holding portion (4c) over the entire circumference of the holding portion. The patch skin according to item 10. (12) The sealing part (5d, 5m) is connected to the connecting member (48
d, 48 m) by a radially located support (
12. The packing according to any one of claims 6 to 11, characterized in that the bottom part (1id, 11m) of the inner part (sa, sm) is surrounded in the radial direction from the inner edge.