Abstract:
A bearing seal particularly suitable for bearings in a direct acting end link of a vehicle suspension system includes a wiper seal between first and second bearing races of the bearing. The wiper seal is secured to one bearing race and extends radially outwardly toward and against the other bearing race.

Description:
RELATED APPLICATIONS 
     The present application is National Phase of PCT/US2012/034425, filed Apr. 20, 2012, and claims priority to U.S. Provisional Application Ser. No. 61/477,818, filed Apr. 21, 2011. 
    
    
     FIELD OF THE INVENTION 
     The present invention relates generally to suspension systems in automobiles, and, more particularly to end links associated with stabilizer bars, control arms and struts in automobile suspension systems, and most particularly to lubricant seal arrangements provided on the bearing assemblies thereof. 
     BACKGROUND OF THE INVENTION 
     It is known to provide automobile suspension systems with a variety of different suspension system configurations for controlling handling, comfort and performance. For example, it is known to provide vertical struts to counteract vertical deflection from bumps, body roll and the like. In some configurations the strut is attached within the overall steering system whereby the strut also rotates as the vehicle is steered. Such configurations are known as “steerable strut suspensions”. 
     Stabilizer bars are known in many configurations for vehicle suspension systems and may be connected to the suspension system in various ways. When connected to the strut to act directly against the strut the system is commonly referred to as a “direct acting” suspension system in that the stabilizer bar acts directly on the strut. When a direct acting stabilizer is provided on a steerable strut the connection is somewhat complicated in that the end link used to connect the stabilizer bar to the strut must withstand and accommodate not only vertical movement of the strut, but also rotational movement of the strut when the vehicle is steered right or left, in addition to the twisting moment provided on the stabilizer bar during operation. The link may experience significantly different articulation at opposite ends thereof, with the strut end connection experiencing primarily rotation, and the stabilizer end connection experiencing primarily angulation. Ball joint links have been used in such configurations to accommodate the multidirectional articulations and forces acting on the connections. 
     A ball joint link includes a rotatable ball held in an attachment which accommodates rotational movement of the connecting end, normally at right angles to the link stud itself. Ball joint links require lubrication, which is held in place by ball joint boots. The boot, which is required for sealing, retains grease in the ball joint structure. However, boots are sometimes easily worn, cut or cracked, and can allow the ingress of contaminants and thereafter trap the contaminants when present in the joint. Ball joint link boots have proven to be components of frequent and regular service or repair. Further, due to the rotational nature of the end of a ball joint link, assembly and installation have been difficult in that the fastened end must be driven into place, and rotation of the end makes it difficult to hold in proper position. Further, ball joint links have been susceptible to corrosion due to wear, and when worn or corroded tend to fail or operate poorly, resulting in noise or other problems. 
     Conventional grommet end links are also known for use in linear attachments, such as between a stabilizer bar and a control arm. Such end links can be simple in nature with linear threaded components at either end. However, simple linear end links can not be used in many installations of direct acting suspensions on steerable struts due to the rotational movement at the connecting joint. 
     Accordingly, a grommet end link suitable for direct acting suspension systems having steerable struts has been proposed. The end link includes grommets on opposite sides of a suspension pad and bearing assemblies adjacent each grommet. One side of each bearing assembly is connected to rotate with the grommets and suspension pad, and the other side of each bearing assembly is connected to move with the rod of the end link. Connection via the end link enables the stabilizer system to reduce body roll during vehicle cornering by transmitting force from the stabilizer bar to the suspension. A direct acting end link decouples the rotation experienced at the link during steering while providing a better leverage ratio by connecting to the strut. The improved leverage allows for a smaller diameter bar for reduced mass while providing similar body roll reduction. In such a link, it is necessary to maintain adequate lubrication along bearing surfaces and packed within the bearing to prevent or substantially block the ingress of water or other contaminants into the bearing area. This will reduce wear caused by contaminants getting between the contact surfaces of the bearing as the surfaces rotate with respect to each other repeatedly during operation and use. Wear can cause increased torque, stick, slip or noise as the surfaces become rougher. Further, wear can result in the loss of lubrication. This can potentially cause the link to become less effective and increase grommet wear as the bearing no longer rotates as it should. Without proper bearing lubrication, the grommets can be abraded by the suspension pads, increasing wear and reducing durability. 
     A labyrinth seal can be used to retain grease in the bearing, and will provide minimal drag and therefore low bearing torque in that, when packed with grease, a labyrinth seal has minimal contact surface areas. Bearing torque is considered to be the rotational torque about the central axis of the bearing assembly. In general, drag created from friction at contact areas and additional areas further out on the diameter of the bearing assembly will increase bearing rotational torque. However, a labyrinth seal does not provide a positive contact seal, and contaminants can follow along an ingress path defined by the labyrinth seal from outside the seal to the inner volume of the bearing assembly. The winding path of a labyrinth seal provides only a passive seal even when fully packed with grease. Further, the non-contacting ribs of a labyrinth seal can allow some side to side movement during normal operation in a multi-directional rotating connection as necessary when used in direct acting suspensions systems having steerable struts. Side to side movement of the bearing components is undesirable in that it can lead to increased wear. 
     A more positive contact seal can be provided through the use of an O-ring compression type seal to establish a physical barrier; however, a compression type seal creates high bearing torque due to the increased drag of the contacting surfaces. An O-ring seal requires pre-compression to seal properly, to account for its own wear and to account for manufacturing part tolerances to ensure a positive contact seal throughout the life of the part. Pre-compression creates drag on the bearing race as a result of the amount of normal force needed to compress the O-ring. The bearing rotational torque increases since the O-ring contacts at a large radius from the axis of rotation of the bearing and also as a result of the drag force created by friction. Increased bearing torque is undesirable in a multi-directional rotational system of a direct acting end link for a steerable strut system. 
     Accordingly, for more effective operation of a grommet end link for direct acting suspensions systems having steerable struts it is desirable to provide a more positive seal than a labyrinth seal, but a seal having less drag than a compression O-ring seal. 
     SUMMARY OF THE INVENTION 
     A bearing is provided with a wiper seal having a main body secured to one bearing race and a flexible tail extending angularly radially outward from the main body and slidingly received against a bearing surface of the other bearing race. 
     In one embodiment of one form thereof, a wiper seal is provided in a bearing for a direct acting end link of a vehicle suspension system, the wiper seal including an enlarged body affixed to one bearing race and a thinner tail extending angularly outward radially from the main body and slidingly received against a bearing surface in the other race. 
     Other features and advantages of the invention will become apparent to those skilled in the art upon review of the following detailed description, claims and drawings in which like numerals are used to designate like features. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a perspective, exploded view of an end link having an end link seal; 
         FIG. 2  is a cross-sectional view of the fully assembled end link shown in  FIG. 1 ; 
         FIG. 3  is a perspective view of the seal shown in  FIGS. 1 &amp; 2 ; 
         FIG. 4  is an enlarged cross-sectional view of the seal shown in  FIG. 3 , taken along line  4 - 4  of  FIG. 3 ; 
         FIG. 5  is an enlarged, fragmentary cross-sectional view of the installed seal shown in  FIGS. 1-4 ; 
         FIG. 6  is a perspective, exploded view of an end link having an end link seal of a second embodiment; 
         FIG. 7  is a is a cross-sectional view of the fully assembled end link shown in  FIG. 6 ; 
         FIG. 8  is a perspective view of the seal shown in  FIGS. 6 &amp; 7 ; 
         FIG. 9  is an enlarged cross-sectional view of the seal shown in  FIG. 8 , taken along line  9 - 9  of  FIGS. 8 ; and 
         FIG. 10  is an enlarged, fragmentary cross-sectional view of the installed seal shown in  FIGS. 6-10 . 
     
    
    
     Before the embodiments of the invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangements of the components set forth in the following description or illustrated in the drawings. The invention is capable of other embodiments and of being practiced or being carried out in various ways. Also, it is understood that the phraseology and terminology used herein are for the purpose of description and should not be regarded as limiting. The use herein of “including”, “comprising” and variations thereof is meant to encompass the items listed thereafter and equivalents thereof, as well as additional items and equivalents thereof. 
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     Referring now more specifically to the drawings, and to  FIG. 1  in particular, and an end link  100  is shown on a link rod  102 . End link  100  includes grommets  104 ,  106  and a bearing assembly  108  adjacent each grommet  104 ,  106 . It should be understood that while only one bearing assembly  108  is shown adjacent grommet  104  in the fragmentary view of  FIG. 1 , a second bearing assembly on the opposite side of grommet  106  is included, but not shown, the second bearing assembly being similar to bearing assembly  108  to be described herein. In use of end link  100 , grommets  104 ,  106  are installed on opposite sides of a mounting pad or other point of attachment to a strut. Grommets  104 ,  106  may include confronting, projecting collars  110 ,  112  of reduced a diameter that are received in and engage opposite sides of a through hole in a mounting pad or other point of attachment. 
     Bearing assembly  108  includes an upper bearing race  120 , a lower bearing race  122  and a bearing disk  124 . An inner open bearing volume  126  and an outer open bearing volume  128  are provided between upper bearing race  120 , lower bearing race  122  and bearing disc  124 . An annular lip seal  130  establishes a physical barrier extending from upper bearing race  120  to lower bearing race  122  and establishes a physical separation between inner bearing volume  126  and outer bearing volume  128 . Accordingly, annular lip seal  130  establishes a barrier to the ingress of contaminants into inner bearing volume  126  from outer bearing volume  128 . Inner open bearing volume  126  is filled with grease during assembly and use for lubrication of the confronting surfaces. Outer bearing volume  128  may be filled with grease also, as a deterrent to ingress of water, grit or other contaminants. 
     Lip seal  130  includes a main body  132  and a thinner, angular tail  134 . Main body  132  is a block-like body in cross-section and is engaged against upper bearing race  120 . In the embodiment shown in  FIGS. 1-5 , as can be seen most clearly in the enlarged cross-section of  FIG. 5 , block-like main body  132  resides in and against a base surface  136  of a well  138 , and is supported against radial inward movement by an inner annular flange  140  of upper bearing race  120 . The block-like square body structure of main body  132  provides improved rigidity for ease of handling and automation of assembly. 
     Tail  134  extends from an inner edge area  142  of main body  132 , is thinner than main body  132 , and extends from main body  132  in an angular direction that is both radially outwardly and axially away from main body  132 . In an installed condition, tail  134  extends to and resides against a bearing race surface  144  of bearing race  122 . The angular outward orientation of tail  134  allows grease from inner bearing volume  126  to deflect and squeeze past tail  134  if necessary, allowing the grease to flow into outer bearing volume  128 , thereby minimizing the potential for grease compression in the bearing. However, tail  134  establishes a physical barrier to the ingress of contaminants into inner bearing volume  126 , due to the angular orientation of tail  134 . Lip seal  130 , and particularly tail  134  thereof, is installed with and resides at an angle with respect to the opposing bearing race which is canted to allow sealing in one direction and not in the other. As shown, the angled tail  134  is not supported and is allowed to flex outwardly allowing grease out of the bearing race. Angled tail  134  is prevented from flexing inwardly and is supported by the bearing race surface  144 , thereby providing a seal from contaminant ingress to inner bearing volume  126 . 
     The distal end surface  150  of tail  134  is defined at an angle to establish a thin wiper edge  152  for riding against bearing race a surface  144 . The thin wiper edge  152  reduces contact friction against bearing race surface  144  relative to wider flatter seal components. 
     While lip seal  130  is shown as a drop in, discrete part, it should be understood that it can also be provided as an overmolded component of bearing race  120 . Overmolding can be provided in a two shot mold or in a two-step process whereby a previously molded race is inserted into a new mold cavity and the seal molded over the top of it or through it. The overmolded seal can be chemically bonded to compatible plastics or can be mechanically bonded to incompatible plastics by way of undercuts, tapers and/or flow channels. 
       FIGS. 6-10  show a second embodiment of a lip seal  230 . An end link  200  is shown on a link rod  202 . End link  200  includes grommets  204 ,  206  and a bearing assembly  208  adjacent each grommet  204 ,  206 . It should be understood that while only one bearing assembly  208  is shown adjacent grommet  204  in the fragmentary view of  FIG. 6 , a second bearing assembly on the opposite side of grommet  206  is included, but not shown, the second bearing assembly being similar to bearing assembly  208  to be described herein. In use of end link  200 , grommets  204 ,  206  are installed on opposite sides of a mounting pad or other point of attachment to a strut. Grommets  204 ,  206  may include confronting, projecting collars  210 ,  212  of reduced a diameter that are received in and engage opposite sides of a through hole in a mounting pad or other point of attachment. 
     Bearing assembly  208  includes an upper bearing race  220 , a lower bearing race  222  and a bearing disk  224 . An inner open bearing volume  226  and an outer open bearing volume  228  are provided between upper bearing race  220 , lower bearing race  222  and bearing disc  224 . Annular lip seal  230  establishes a physical barrier extending from upper bearing race  220  to lower bearing race  222  and establishes a physical separation between inner bearing volume  226  and outer bearing volume  228 . Accordingly, annular lip seal  230  establishes a barrier to the ingress of contaminants into inner bearing volume  226  from outer bearing volume  228 . Inner open bearing volume  226  is filled with grease during assembly and use for lubrication of the confronting surfaces. Outer bearing volume  228  may be filled with grease also, as a deterrent to ingress of water, grit or other contaminants. 
     Lip seal  230  also can be provided as a discrete drop in part, or as an overmolded component of one of the bearing races as described previously for lip seal  130 . Lip seal  230  is a hoop-like structure having a thicker main body  232  and a thinner tail  234 . Thicker main body  232  is held by one bearing race, upper bearing race  220  in the exemplary embodiment, in a restricted well  238  and is supported against radially inward movement by an annular flange  240 . Tail  234  extends angularly outward radially and axially from main body  232  and operates against a bearing race surface  244  of the other bearing race  222 . Lip seal  230  functions similarly to lip seal  130  in allowing grease to flow out of the bearing assembly while establishing a physical barrier to the ingress of contaminants. 
     Thicker main body  232  can be provided with a bump out or protrusion  246  to insure proper placement in a tool or fixture for consistent ejection and handling for automated assembly. 
     The distal end surface  250  of tail  234  is defined at an angle to establish a thin wiper edge  252  for riding against bearing race a surface  244 . The thin wiper edge  252  reduces contact friction against bearing race surface  244  relative to wider flatter seal components. 
     Lip seals  130 ,  230  can be made of, for example and not limitation, flexible rubber, TPE or flexible plastics such as LDPE. Seals  130 ,  230  thereby provide low friction and further reduce torque beyond that resulting from lower seal compression forces. The drop in designs for seals  130 ,  230  provide ease and efficiency for assembly, in addition to reduced manufacturing cost. It should be understood that seals  130 ,  230  also can be designed for a slight interference fit against annular flanges  140 ,  240 , with an additional sealing rib if necessary, for durability. Each can be provided as an overmolded part on one of the bearing races, further simplifying assembly. 
       FIGS. 5 &amp; 10  illustrate further modifications for improved performance. Larger outer bearing volumes  128 ,  228  discourage contaminants from abrading seals  130 ,  230  by providing increased volume for containing contaminants away from seals  130 ,  230  even after contaminants reach the general areas of seals  130 ,  230 . Catch troughs  160 ,  260  are provided for capturing and accumulating debris in areas more remote from seals  130 ,  230 . Either of the lip seals  130  or  230  rides on a horizontal face of the opposite bearing component to maintain a sealing relationship even if horizontal or side shift occurs. The catch troughs  160 ,  260  include curved surfaces  161 ,  261  connected to canted passages  163 ,  263 . As shown, the catch troughs  161 ,  261  are radially outward from the seals  130 ,  230 . The curved surfaces  161 ,  261  are at closed-ended areas  165 ,  265  of the bearing races  120 ,  220 . The closed-ended areas  165 ,  265  are distally located from openings  167 ,  267  connected to the canted passages  163 ,  263 . 
     The placement of lip seals  130 ,  230  in the bottoms of wells  138 ,  238  provides a degree of assembly proofing. If a seal  130 ,  230  is not properly seated in the bottom of well  138 ,  238  the distal edge of the seal will be too high and may be visibly notable to the assembler while perhaps further inhibiting completed assembly of the component parts. 
     Advantages of the seals disclosed herein include lower compression force and reduced friction, which improve wear and performance characteristics. The wiper orientation prevents pressurization in the bearing cavity in that it yields readily if grease is pushed from the bearing assembly. However, the angular orientation establishes a firm physical barrier to the ingress of contaminants. The wiper seal designs illustrated herein provide lower bearing torque then known O-ring designs requiring pre-loading. Further, the seal is maintained even during horizontal shift of the bearing assembly. Manufacturing and installation are simplified. 
     Variations and modifications of the foregoing are within the scope of the present invention. It is understood that the invention disclosed and defined herein extends to all alternative combinations of two or more of the individual features mentioned or evident from the text and/or drawings. All of these different combinations constitute various alternative aspects of the present invention. The embodiments described herein explain the best modes known for practicing the invention and will enable others skilled in the art to utilize the invention. The claims are to be construed to include alternative embodiments to the extent permitted by the prior art. 
     Various features of the invention are set forth in the following claims.