Abstract:
An improved seal configuration for use primarily with a spherical plain bearing wherein the sealing member includes a base with two outwardly extending lips, one extending in an inner direction and one extending in an outer direction. Both of the lips engage the bearing surface of an inner race member. The seal base member of the seal is mounted within a seal mounting groove defined in the bearing surface of the outer race member. The seal is preferably circular and includes a downwardly flexibly resilient inner and outer lip configuration which provide dual sealing and enhanced contaminant control for a spherical plain bearing.

Description:
BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The present invention deals with the field of spherical plain bearings generally and with means for sealing thereof for retaining lubrication between the generally spherical bearing surfaces and for preventing the movement of contaminants therebetween. Such spherical plain bearings normally include an inner and outer race member wherein the inner race member defines a spherically convex inner race bearing surface. Also the outer race member defines a cavity therein with an outer race bearing surface which is concave and generally spherical therein. These two surfaces are mated to one another and have complementary profiles. The present invention provides a unique configuration for sealing of these bearing surfaces to minimize contamination thereof and to enhance retaining of lubrication therebetween. Such seals can be of any material such as rubber, however the present invention contemplates the use of plastic. 
     2. Description of the Prior Art 
     Numerous prior art patents have been granted on various configurations of spherical plain bearings with different types of seal configurations for use therewith such as shown in U.S. Pat. No. 2,631,906 patented Mar. 17, 1953 to W. H. U. Brock and assigned to Automotive Products Company Limited on a “Sealing Device For Fluid Pressure Apparatus”; and U.S. Pat. No. 3,769,672 patented Nov. 6, 1973 to P. R. Eklund and assigned to The United States of America as represented by the Secretary of the Air Force on a “Method Of Making An Improved Teflon-Lined Spherical Bearing; and U.S. Pat. No. 3,832,022 patented Aug. 27, 1974 to H. L. Reinsma et al and assigned to Caterpillar Tractor Co. on a “Dual Seal Arrangement For A Spherical Joint”; and U.S. Pat. No. 3,848,938 patented Nov. 19, 1974 to L. Stella et al and assigned to The Torrington Company on a “Bearing And Bearing Seal”; and U.S. Pat. No. 3,947,075 patented Mar. 30, 1976 to H. P. Ewertz and assigned to Valley-Todeco, Inc. on a “Bearing System”; and U.S. Pat. No. 4,080,013 patented Mar. 21, 1978 to H. W. Kock and assigned to Roller Bearing Company of America on a “Sealed Self-Aligning Spherical Bushing”; and U.S. Pat. No. 4,080,015 patented Mar. 21, 1978 to D. F. Greby et al and assigned to Lear Siegler, Inc. on a “Bearing And Method For Manufacturing Same”; and U.S. Pat. No. 4,435,023 patented Mar. 6, 1984 to T. E. Bolner and assigned to Thiokol Corporation on an “Internally Actuated Spherical Bearing”; and U.S. Pat. No. 4,522,411 patented Jun. 11, 1985 to T. J. Burgan and assigned to Chicago Rawhide Mfg. Co. on “Fluid Seals With Self-Venting Auxiliary Lips”; and U.S. Pat. No. 4,531,747 patented Jul. 30, 1985 to T. Miura and assigned to Nippon Oil Seal Industry Co., Ltd. on an “Extended Wear Annular Oil Seal”; and U.S. Pat. No. 4,836,694 patented Jun. 6, 1989 to P. R. Schmehr et al and assigned to SKF Gleitlager GmbH on a “Bearing Seal”; and U.S. Pat. No. 5,002,406 patented Mar. 26, 1991 to J. R. Morton et al and assigned to Emerson Electric Co. on a “Sealing Structure For A Spherical Bearing Assembly”; and U.S. Pat. No. 5,125,672 patented Jun. 30, 1992 to H. Wycliffe and assigned to The BOC Group plc on “Shaft Sealing Arrangements”; and U.S. Pat. No. 5,385,352 patented Jan. 31, 1995 to I. Kurose and assigned to Uchiyama Manufacturing Corp. on a “Sealing System For Bearings, Particularly Radial-Type Bearings”; and U.S. Pat. No. 5,573,336 patented to M. E. Maroney on Nov. 12, 1996 on a “Seal For A Spherical Plain Bearing”; and U.S. Pat. No. 5,909,880 patented Jun. 8, 1999 to W. P. Waskiewicz and assigned to The Torrington Company on a “Polymer Bearing Seal And Sealed Bearing”; and U.S. Pat. No. 5,967,899 patented Oct. 19, 1999 to B. Schierling and assigned to Mannesman Sachs AG on a “Centrifugal Mass Device With An Axial Slide Bearing As Seal”; and U.S. Pat. No. 5,980,115 patented Nov. 9, 1999 to S. C. Hoeting and assigned to Setco Sales Co. on a “Bearing Seal With Uniform Fluid Purge”; and U.S. Pat. No. 6,000,854 patented Dec. 14, 1999 to M. Kellstrom et al and assigned to Aktiebolaget SKF on a “Sealed Bearing”; and U.S. Pat. No. 6,003,876 patented Dec. 21, 1999 to T. Yamagishi et al and assigned to Koyo Seikl Co., Ltd. on a “Sealing Member And Capped Bearing”; and U.S. Pat. No. 6,024,495 patented Feb. 15, 2000 to M. Loos et al and assigned to Asea Brown Boveri AG on an “Axial Sliding Bearing”; and U.S. Pat. No. 6,026,917 patented Feb. 22, 2000 to A. F. Zabradnik et al and assigned to Baker Hughes Incorporated on an “Earth-Boring Bit With Improved Bearing Seal”; and U.S. Pat. No. 6,030,124 patented Feb. 29, 2000 to R. Moseberg et al and assigned to INA Walzlager Scvhaeffler oHG on a “Linear Rolling Bearing With Longitudinal Sealing Elements”; and U.S. Pat. No. 6,036,435 patented Mar. 14, 2000 to R. A. Oklejas and assigned to Pump Engineering, Inc. on a “Thrust Bearing”; and U.S. Pat. No. 6,042,272 patented Mar. 28, 2000 to M. Nagase and assigned to NSK Ltd. on a “Rolling Bearing With A Sealing Device”; and U.S. Pat. No. 6,062,734 patented May 16, 2000 to A. Bundgart and assigned to SKF Sverige AB on a “Bearing Seal”; and U.S. Pat. No. 6,065,879 patented May 23, 2000 to N. Mitsue et al and assigned to NSK Ltd. on a “Rolling Bearing With Seal”; and U.S. Pat. No. 6,068,407 patented May 30, 2000 to E. Kobayashi et al and assigned to Minebea Kabushiki-Kaisha on a “Seal For An Anti-Friction Bearing”; and U.S. Pat. No. 6,073,933 patented Jun. 13, 2000 to D. E. Johnson and assigned to Freudenberg-NOK General Partnership on a “Load Bearing Washer And Dirt Excluder”; and U.S. Pat. No. 6,082,901 patented Jul. 4, 2000 to T. N. Arvidsson and assigned to Andritz Inc. on an “Hydraulic Axial Bearing”; and U.S. Pat. No. 6,082,905 patented Jul. 4, 2000 to A. Vignotto et al and assigned to SKF Industrie S.p.A. on a “Sealing Assembly For A Rolling Bearing”; and U.S. Pat. No. Re. 36,804 patented Aug. 1, 2000 to K. Kajhara et al and assigned to Koyo Seiko Co., Ltd. on a “Bearing Sealing Device And Bearing Sealing Mechanism Capable Of Preventing The Leakage Of Grease”; and U.S. Pat. No. 6,102,575 patented Aug. 15, 2000 to R. Obara and assigned to Minebea Co., Ltd. on a “Compound Bearing Apparatus”; and U.S. Pat. No. 6,103,164 patented Aug. 15, 2000 to S. Bebjak et al and assigned to Firma Druckgusswerk Mossner GmbH on a “Method For Manufacturing A Seal In A Bearing Groove Of A Cylinder Head”; and U.S. Pat. No. 6,123,338 patented Sep. 26, 2000 to L. Edelmann and assigned to SKF Linearsysteme GmbH on a “Radial Seal For Ball Bearing”; and U.S. Pat. No. 6,126,321 patented Oct. 3, 2000 to M. W. K. Fetty et al and assigned to Brenco Incorporated on a “Shaft Journal Bearing And Seal Wear Ring Assembly”; and U.S. Pat. No. 6,132,096 patented Oct. 17, 2000 to P. Damour et al and assigned to Glyco-Metal-Werke Glyco B.V. &amp; Co. KG on a “Bearing Bush And Method For The Production Thereof”; and U.S. Pat. No. 6,132,099 patented Oct. 17, 2000 to P. Olszewski et al and assigned to INA Walzlager Schaeffler OHG on a “Radial Bearing For A Vehicle Drive Shaft”. 
     SUMMARY OF THE INVENTION 
     The present invention provides a uniquely configured spherical plain bearing which utilizes a dual spread lock sealing device for preventing contamination of the bearing surface and for maintaining lubrication thereover. The plain bearing itself includes an inner race member which defines an inner race bearing surface extending externally therearound. This inner race bearing surface is preferably of a generally spherically convex shape. 
     An outer race member is also included which includes an outer race body which defines a bearing cavity therein which is adapted to receive the inner race member positioned therein in such a manner as to be movable to form the rotational and spherical capability of movement of the relative bearing pieces. The outer race member further includes an outer race bearing surface defined within the bearing cavity. This outer race bearing surface is generally spherically concave and is positioned in abutment with and movable with respect to the inner race bearing surface of the inner race member whenever the inner race member itself is positioned within the bearing cavity of the outer race member. This outer race body will preferably define a seal mounting groove extending therearound at a position adjacent to the outer race bearing surface to facilitate sealing of the mated concentric spherical bearing surfaces. 
     In the preferred configuration the seal of the present invention is capable of being positioned within the seal mounting groove in such a manner as to retain lubrication between the inner race bearing surface of the inner race member and the outer race bearing surface of the outer race member. This seal will also have the effect of minimizing the flow of contaminants therebetween. 
     The particular construction of the seal includes a seal base member adapted to be positioned within the seal mounting groove defined in the outer race body for retaining therewithin. The seal may also preferably include an outer lip of flexibly resilient material which is attached to the seal base member and extends outwardly therefrom toward the inner race bearing surface. This outer lip member preferably is flexibly resiliently biased into abutment with this inner race bearing surface. The outer lip is also preferably oriented at an acute angle relative to the inner race bearing surface. 
     An inner lip is also included in the seal means formed of flexibly resilient material which is attached to the seal base member and extends outwardly therefrom toward the inner race bearing surface and resiliently biased into contact therewith. This inner lip will preferably be oriented at an acute angle relative to the inner race bearing surface. 
     In the preferred configuration of the present invention the seal base member, the outer lip and the inner lip will all be configured as a single integral member formed preferably of plastic and more particularly preferably formed of white nitrile. 
     Furthermore the inner lip of the present invention is preferably positioned extending inwardly toward the area of abutment between the inner race bearing surface and the outer race bearing surface. Also in the preferred configuration the outer lip of the seal is positioned extending outwardly away from the area of contact between the inner race bearing surface and the outer race bearing surface in order to maintain double lubrication sealing therebetween and to enhance positioning of the seal base member into the seal mounting groove by flexibly resilient force exerted thereon through the outer and inner lips. 
     In another preferred configuration the outer lip and the inner lip will be oriented at approximately sixty degrees with respect to one another, one oriented toward the mated bearing surfaces and one oriented away from the bearing surfaces. Also the outer lip means will be oriented at approximately sixty degrees relative to the inner race bearing surface in one direction and the outer lip means will be oriented at approximately sixty degrees relative to the inner race bearing surface in the other direction. 
     To achieve effective sealing it is preferred that the seal mounting groove be positioned extending along the outer periphery of the outer race bearing surface to facilitate retaining of lubrication between the bearing surfaces and to minimize contamination thereof. To further facilitate lubrication the inner lip means may defined one or more and preferably four individual lubrication holes extending therethrough to facilitate movement of lubrication over the inner race bearing surface between the outer lip and the inner lip. 
     It is preferable that the seal means be formed of a material sufficiently flexibly resilient in order to allow the outer lip and the inner lip to flex outwardly with respect to one another in order to temporarily increase the angular relationship therebetween whenever force is exerted on the seal base member directed downwardly approximately perpendicular to the inner race bearing surface. In this manner insertion of the seal into the groove by compression of the overall seal and movement toward the seal mounting groove is greatly facilitated. 
     It is preferable that the outer lip means and the inner lip means also act for the purpose of wiping the bearing surface over which they are caused to move during the normal range of movement of the inner race member relative to the outer race member. This wiping will maintain the lubrication within the inner and outer lips and across the bearing surfaces within the inner lip such that the outer lip will be formed to include an outer pointed end oppositely located from the seal base member thereon for facilitating sealed contact and wiping of the inner race bearing surface. Similarly it is preferable that the inner lip include an inner pointed end oppositely located from the seal base member to facilitate maintaining of sealed contact and wiping of the bearing surface. 
     The configuration of the seal mounting groove of the present invention can be symmetrical or asymmetrical and it has been found that the present invention is workable with both configurations as long as the properly mated configuration for the seal base member of the seal is chosen for use with that particular application. That is, the seal base member must define an external groove engaging surface which has a complementary shape mated to the mounting channel section defined in the seal mounting groove into which the seal base member is adapted to be positioned. 
     In the preferred configuration of the present invention the inner race member will be formed as an inner ring member and the outer race member will be formed as an outer ring member. With this configuration the inner race bearing surface and the outer race bearing surface will be formed as complementary concentric spherical surfaces. 
     With the outer race member formed ring shaped it will preferably define a first outer race opening and a second outer race opening on opposite sides of the outer race bearing surface. Each of these openings will preferably be in fluid flow communication with respect to the bearing cavity and, as such, require the positioning of a first sealing member around the first outer race opening and a second sealing member positioned about the second outer race opening for maintaining a lubrication between the first and second outer race openings. 
     The seal device as disclosed in the present invention can also be usable in sealing the inner race member with respect to a movable member which may be positioned protruding therethrough. Normally with such bearings as in the present invention a movable member will extend through a channel defined in the ring-shaped inner race member. As such, this channel means will include a first inner race opening and a second inner race opening. A first channel groove will be defined in the channel means adjacent the first inner race opening. Similarly a second channel groove will be positioned in the channel means adjacent the second inner race opening. This will necessitate the inclusion of a sealing device defined herein as the first supplemental sealing device to be mounted in the first channel groove for sealing between the movable member and the inner surface of the channel of the inner race member. Similarly a second supplemental sealing device will be mounted within the second channel groove for sealing of the channel therebetween responsive to this same movable member being positioned extending therethrough. 
     The configuration of the first supplemental sealing device will include a first supplemental seal base member adapted to be positioned in the first channel groove defined in the channel. A first supplemental outer lip of flexibly resilient material will preferably be integrally formed with the first supplementary seal base member and will extend outwardly therefrom away from the channel. This first supplementary outer lip means will preferably be oriented at an acute angle relative to the channel. The first supplementary outer lip means will be integrally formed with the first supplementary seal base member. Furthermore the first supplementary sealing device will include a first supplementary inner lip of flexibly resilient material attached to the first supplementary seal base member and extending outwardly therefrom away from the first supplementary outer lip. The first supplementary inner lip will be oriented at an acute angle relative to the channel. This first supplementary inner lip will be integrally formed preferably with respect to the first supplemental seal base member. 
     A second supplementary sealing device will be similarly constructed to the first supplementary sealing device and will include a second supplementary seal base member, a second supplementary outer lip and a second supplementary inner lip and will be positioned within the second channel groove means defined in the channel for sealing of the second inner race opening extending therethrough. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which effectively prevents the movement of contaminants between the bearing surface. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which effectively minimizes the loss of lubrication from the area of contact between the mated bearing surfaces. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which can include a hole extending through the seal for lubricating of an area between the inner and outer lips of the dual sealing members. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means wherein an inner and outer lip are each included extending in opposite directions to facilitate flexible resilience of sealing and to enhance seal in the seal mounting groove. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which is particularly usable for spherical plain bearings including two concentric spherical bearing surfaces. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which maintains firm securement between the dual sealing lips and the bearing surfaces even after substantial wear has occurred from use. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which includes flexibly resilient lip members engaging the bearing surface for wiping and sealing thereof made from plastic or white nitrile. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which is usable with symmetrical or asymmetrical seal mounting grooves. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which allows full flushing of lubrication. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which is of minimal cost. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which requires a minimum amount of maintenance. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which can be easily installed by compressing and sliding into the seal mounting groove. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which effectively seals in both directions to prevent the escape of lubrication and prevents the inflow of contaminants. 
     The present invention provides a spherical plain bearing with a spread lock dual sealing means which can use the identical sealing system for sealing between a movable member penetrating through the channel in the inner ring for lubrication between this movable member and the inner ring securement surface. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     While the invention is particularly pointed out and distinctly claimed in the concluding portions herein, a preferred embodiment is set forth in the following detailed description which may be best understood when read in connection with the accompanying drawings, in which: 
     FIG. 1 is a cross-sectional view of an embodiment of the spherical plain bearing with spread lock dual sealing means; 
     FIG. 2 is close-up of the embodiment of the seal mounting groove and seal means located therein and being compressed for placement therein; 
     FIG. 3 side cross-sectional view of an alternative embodiment of a seal means of the present invention symmetrically configured; 
     FIG. 4 is a close-up of the upper right hand corner of the embodiment shown in FIG. 1 showing the sealing means used simultaneously for sealing against the lubrication surfaces and for sealing between the inner member and the movable member; 
     FIG. 5 shows an alternative embodiment of the seal means of the present invention shown positioned within an alternative embodiment of the configuration of the seal mounting groove; 
     FIG. 6 is further embodiment of the seal means of the present invention shown positioned within a further embodiment of the configuration of the mounting groove; 
     FIG. 7 is further embodiment of the seal means of the present invention shown positioned within a further embodiment of the configuration of the mounting groove; 
     FIG. 8 is a further alternative configuration of the seal means and seal mounting groove of the present invention which shows a basic configuration with both lips extending in the same direction; 
     FIG. 9 is a further alternative configuration of the seal means and seal mounting groove of the present invention which shows an alternative configuration for both lips extending in the same direction; and 
     FIG. 10 is a further alternative configuration of the seal means and seal mounting groove of the present invention which shows a still further embodiment with both lips extending in the same direction with an asymmetrical seal cross section. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     The present invention provides a spherical plain bearing with spread lock dual sealing capability. The configuration of the spherical plain bearing includes an inner race bearing member  10  preferably in the form of a ring which defined an inner race bearing surface  12  on the exterior surface thereof preferably of a spherically convex shape. 
     The bearing of the present invention also includes an outer race bearing member  14  preferably in the shape of a ring which includes an outer race body  16 . Outer race body  16  defines a bearing cavity  18  therewithin. This bearing cavity  18  defines an outer race bearing surface  20  therein preferably of a spherically concave shape. When assembled the inner race member or ring  10  will be positioned within the bearing cavity  18  of the outer race member or ring  14  with the spherically concave outer race bearing surface  20  concentrically located around the spherically convex inner race bearing surface  12  to thereby form the spherical plain bearing configuration. 
     The present invention provides a unique seal mounting groove  22  extending around the edges of the mated bearing surfaces. A lubrication means  24  is adapted to extend across the inner race bearing surface  12  and the outer race bearing surface  20  for lubrication thereof to minimize wear and enhance rotational characteristics and decrease rotational friction of the overall bearing construction. 
     A seal  26  will be adapted to be placed within the seal mounting groove  22  to prevent the loss of lubrication from the area of contact between the inner race bearing surface  12  and the outer race bearing surface  20 . This seal means  26  will preferably comprise a seal base member  28  itself of a mated configuration adapted to be placed within the seal mounting groove  22 . Seal means  26  will preferably include an outer lip means  30  extending downwardly and outwardly from the seal base  28  away from the area of mating of the bearing surfaces  12  and  20 . Preferably the outer lip means will extend through an acute angle  32  indicated as angle A relative to inner race bearing surface  12  and will extend to contact thereof for sealing thereagainst and wiping of that surface. 
     An inner lip means  34  will also preferably extend outwardly from the seal base member  28  and in the preferred configuration shown in FIGS. 1 through 7 will extend in a direction oppositely from the direction of extension of the outer lip  30 . This inner lip  34  will be at an acute angle  36  indicated as angle B extending inwardly toward the area of engagement between the inner and outer race bearing surfaces  12  and  20 . As such, in this particular configuration the outer lip member  30  and the inner lip member  34  will form a downwardly facing V-shape which engages the spherically convex inner race bearing surface  12  for sealing thereof against the movement of lubrication passed either of the lips  30  or  34  and also provides double protection against the flow of contaminants inwardly to the lubricating area. Preferably an acute angle  38  indicated as angle C will be positioned between numbers  30  and  34 . In the most particular configuration shown in FIG. 3 angles  32 ,  36  and  38  shown as angles A, B and C will all be approximately sixty degrees. However, these values can vary as shown in the other drawings for the purposes of providing asymmetrical configurations for the individual seals  26  most particularly as shown in FIGS. 5,  6  and  7  as well as FIG.  2 . 
     To further enhance lubrication a lubrication hole  40  may be defined extending through the inner lip  34 . This lubrication hole  40  can be located at multiple locations about the generally round seal  26 . This hole allows lubrication to flow from the area of engagement between the inner race bearing surface  12  and the outer race bearing surface  20  to the portion of the outer race bearing surface  20  located between the inner lip means  34  and the outer lip means  30  to facilitate lubrication thereof. This hole also allows for overflow lubrication during normal maintenance re-lubrication of the bearing. 
     Placement of the seal  26  into the seal mounting groove  22  is greatly enhanced by the flexible resilience thereof. The position of insertion and the position after insertion is shown best in FIG.  2 . FIG. 2 shows the compressed position  42  of the seal means  26 . In this compressed position shown in the right of FIG. 2 the angle  44  referred to as angle D between the inner and outer lips  34  and  30  will be significantly increased when compressed downwardly by the exertion of force as indicated by the arrow of reference number  48 . The exertion of a downwardly directed fore such as by automated installation means for merely a user&#39;s hand or finger will compress the seal means  26  to the position shown on the right, namely compressed position  42 . In this position the outer lip means  30  and the inner lip means  35  will be compressed to a position almost parallel to the inner race bearing surface. This will allow the insertion personnel to slide the seal  26  upwardly till it is in position immediately beneath the seal mounting groove  22  whereafter the user can release the force exerted along arrow  45  to allow the seal  26  to snap into place as shown in the left portion of FIG.  2 . Insertion of seal  26  occurs along the insertion direction arrow  96 . 
     Engagement between the outer lip means  30  and the inner lip means  34  relative to the generally spherically convex inner race bearing surface  12  is greatly enhanced by use of pointed ends thereon. In particular the outer lip  30  will preferably define an outer pointed end  46  at the extreme outwardly most portion thereof which greatly facilitates flexible resilience of the lip and wiping of the inner race bearing surface  12  as desired. In a similar manner the inner lip  34  will preferably include an inner pointed end means  48  thereon which facilitates flexible resilience and slight bending or flexing of the inner lip  34  during insertion and after insertion to maintain contact with the bearing surface even after significant wear occurs. 
     The present invention is usable with symmetrical sealing mounting groove means  52  such as shown best in FIGS. 2 and 4. However, the seal  26  of the present invention is also usable with respect to asymmetrical seal mounting groove means  50  as shown in FIGS. 6,  7 ,  8 ,  9 , and  10 . 
     The seal mounting groove  22  will define a mounting channel section  56  which is adapted to directly engage the seal  26 . The seal  26  will define an external groove engaging surface  54  which is adapted to directly engage the mounting channel section  56 . It is preferable that the groove engaging surface  54  and the mounting channel section  56  be of a complementary mated configuration to maintain full contact for holding of the seal base member  28  firmly within the seal mounting groove  22  under all operating conditions. 
     In a preferred configuration of the present invention the inner race member  10  will be generally ring-shaped and the outer race member  14  will be generally ring-shaped. As such, the bearing cavity  18  will define a first outer race opening  58  and a second outer race opening  60 . Each of these openings will require the placement of a sealing configuration therearound. As such, a first sealing member  62  will be positioned extending around the first outer race opening  58 . This first sealing member will be chosen of a configuration as shown in the present invention for the seal  26 . Similarly the second sealing member  64  will be positioned about the second outer race opening  60  for sealing thereof and will be chosen from any configuration disclosed in the present invention for the seal means  26 . 
     It is also possible that a sealing configuration similar to the above-described sealing means could be used to seal between the inner race member  10  and a movable member  94  which may extend therethrough. In the preferred configuration for a spherical bearing the inner race member  10  which is ring-shaped will define a channel means  66  extending therethrough. This channel means will define a first inner race opening means  68  at one end thereof and a second inner race opening means  70  at the opposite end thereof. Adjacent the first inner race opening means  68  a first channel groove  72  will be defined for receiving of a sealing means. Similarly a second channel groove means  74  will be defined adjacent the second inner race opening  70  for facilitating sealing thereof. 
     A first supplementary sealing device  76  will preferably be positionable in the first channel groove  72  for sealing of the first inner race opening  68 . This first supplementary sealing device  76  will include a first supplementary seal base member  78  to be directly placed within the first channel groove  72 . A first supplementary outer lip  80  will be integral with an extend outwardly from the first supplementary seal base member  78 . Also a first supplementary inner lip  82  will be integral with and extend outwardly from the first supplementary seal base member  78 . As so constructed this first supplementary sealing device  76  will effectively seal between the movable member  94  and the first inner race opening  68 . 
     Similarly a second supplementary sealing device  86  will be included comprising a second supplementary seal base member  88  with a second supplementary outer lip  90  integral therewith and extending outwardly therefrom. Also a second supplementary inner lip means  92  will be integral with and extend outwardly from the second supplementary seal base member  88 . As such, this configuration of the second supplementary sealing device  86  will be placed within the second channel groove  74  to seal the second inner race opening  70  between the inner race member  10  and the movable member  94 . 
     One of the primary inventive characteristics of the present invention is the ability to have effective full sealing and wiping of a bearing surface even after an extensive time period of use. This is achievable due to the enhanced wear characteristics of this design. This configuration allows a significant amount of wear to occur on the outer lip  30  and inner lip  34  of the seal  26  of the present invention without seriously effecting sealing and wiping. This is achieved due to the flexible resilience of the material from which the seal member  26  is formed. As shown in FIG. 2 after insertion is made along arrow  96  the inner and outer lips  30  and  34  will still be flexibly compressed to a slight extent. This slight compression will enhance sealing with the bearing surface while at the same time will allow wear to occur while still maintaining this seal. Thus the construction of the inverted V-shaped downwardly facing seal provides a self-adjusting characteristic not present in constructions heretofore. 
     It also should be appreciated that the apparatus of the present invention will work well without a downwardly facing V-shape along as there is still two lips extending outwardly from the seal base member  28  of the individual seal means  26 . These configurations are shown best in FIGS. 8,  9  and  10  where there are downwardly directed two sealing lips however the lips are not in the form of a V-shape since they both extend in the same direction, namely, both lips extend outwardly away from the engaging area of the bearing surfaces  12  and  20 . 
     Most prior art designs include asymmetrical configurations with only a single sealing lip. These configurations have a natural tendency to be easily removed after wear has occurred or to be difficult to position in place initially. The present invention overcomes these difficulties by providing an inner lip means  34  as well as an outer lip means  30 . This dual sealing means enhanced lubrication, further minimizes contamination of the bearing and at the same time provides a self-adjusting characteristic not present in designs at this time. 
     While particular embodiments of this invention have been shown in the drawings and described above, it will be apparent, that many changes may be made in the form, arrangement and positioning of the various elements of the combination. In consideration thereof it should be understood that preferred embodiments of this invention disclosed herein are intended to be illustrative only and not intended to limit the scope of the invention.