Abstract:
A bearing comprising a body of polymeric material and a reinforcing member embedded in the body and having a plurality of perforations throughout which are affixed in the reinforcing member. The polymeric material extends through the perforations. The bearing may have various configurations. The reinforcing member may comprise a thin metal sheet having perforations therein, a woven metal body defining the perforations, or adjacent woven metal bodies each having perforations. In one form, a backing member is adhered to on one side of said reinforcing member. Where a thin metal sheet is used, it has a roughened surface finish at the interface with the plastic body.

Description:
This application is a continuation-in-part of patent application Ser. No. 328,065 filed Mar. 23, 1989, now abandoned, which is, in turn, a continuation-in-part of patent application Ser. No. 150,933 filed Feb. 1, 1988 now U.S. Pat. No. 4,862,789. 
    
    
     This invention relates to bearings which carry varying loads such as found in hydraulic pumps and motors, and particularly to such motors including bearings. 
     BACKGROUND AND SUMMARY OF THE INVENTION 
     Hydraulic pumps and motors of the piston type utilize a plurality of axially extending pistons and associated cylinders and a yoke engaged by the pistons and pivoted by annular bearings in a housing. 
     In another type of hydraulic pump or motor, the bearing form is that of a partial journal bearing often termed a &#34;saddle bearing&#34;. The use of this bearing form gives the advantage of a reduction in overall size and in utilizing fewer parts in the bearing area thereby making it more reliable, easier to maintain, involving less deflection on the yoke. The saddle bearing can be either a rolling element or a non-rolling element bearing format. This invention deals with a non-rolling element form of saddle bearing. 
     In hydraulic pumps and motors journal bearings generally function through hydrodynamic, hydrostatic or hybrid oil filmgeneration processes. There are, however, circumstances when normal lubrication mechanics are insufficient to correctly form a fluid film for the journal bearing to function, typical cases are extreme load, quasi-steady state operation or poor lubrication. Such is the case with a non hydrostatic form of a saddle bearing. Under these circumstances surface to surface contact can and does occur with resulting high coefficients of friction and wear rates. In an attempt to overcome this problem a self lubricated material is used for one of the surfaces in contact. Self lubricated bearings, thus formed however, do have limitations; temperature, load, speed of operation, etc. Many of the self lubricated bearing forms utilize a polymer as the self lubricated material. While these polymers impart a low coefficient of friction for the bearing pair they have a relatively low load capacity due to the yield strength of the polymer. Other materials possessing a higher yield strength cannot achieve a suitably low coefficient of friction. Attempts have been made to increase the yield strength of the polymer by the use of a filler material intimately mixed with the polymer to form a composite material. These composites have, however, failed due to an increase in the coefficients of friction. These higher coefficients of friction are due to the wear process exposing the filler material so that the mating surface no longer rides on a true polymer interface. Another technique, which has been used to attempt to increase the yield strength of the polymer is the incorporation of a woven metal screen to form a composite. This also fails as the friction between the metal threads is insufficient to prevent yielding of both the polymer and the lateral movement of the screen wires across each other. Further, the yielding of the screen wire can be preferential depending on the direction of the shear force and the &#34;lay&#34; or &#34;bias&#34; of the woven screen. Attempts to further increase the strength of the composite by adhesively bonding the screen to a metal backing has failed as the area open to bonding is small due to the roundness of the screen wires and the fill of the polymer in the mesh. 
     Accordingly, among the objectives of the present invention are to provide a positive displacement pump or motor which has a non-rolling element saddle type bearing of increased load capacity; which would withstand the normal forces on the bearing on the pump or motor; and which can be relatively easily manufactured; and bearings which can be utilized in other force conditions involving radial and axial loads. 
     In accordance with the invention, a bearing comprising a body of polymeric material and a reinforcing member embedded in the body and having a plurality of perforations throughout which are affixed in the reinforcing member. The polymeric material extends through the perforations. The bearing may have various configurations. The reinforcing member may comprise a thin metal sheet having perforations therein, a woven metal body defining the perforations, or adjacent woven metal bodies each having perforations. In one form, a backing member is adhered to one side of said reinforcing member. Where a thin metal sheet is used, it has a roughened surface finish at the interface with the plastic body. 
    
    
     DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a longitudinal part sectional view of a positive displacement pump or motor embodying the invention. 
     FIG. 2 is a sectional view taken along the line 2--2 in FIG. 1, parts being taken away. 
     FIG. 3 is a sectional view similar to FIG. 1, parts being taken away. 
     FIG. 4 is a plan view of the yoke of the pump or motor. 
     FIG. 5 is a plan view of the bearing. 
     FIG. 6 is a side view of the bearing. 
     FIG. 7 is a fragmentary sectional view on a greatly enlarged taken along the line 7--7 in FIG. 6. 
     FIG. 8 is a plan view of a portion of the bearing. 
     FIG. 9 is an exploded view of the parts of the bearing prior to their being assembled. 
     FIG. 10 is a fragmentary sectional view of a modified form of bearing. 
     FIG. 11 is a fragmentary plan view on an enlarged scale of a portion of the bearing shown in FIG. 12. 
     FIG. 12 is a fragmentary sectional view on enlarged scale of another portion of the bearing shown in FIG. 10. 
     FIG. 13 is a fragmentary sectional view showing the bearing portion of FIG. 12 after it is formed to arcuate form. 
     FIG. 14 is a further modified form of bearing. 
     FIG. 15 is another form of the bearing. 
     FIG. 16 is a fragmentary sectional view on an enlarged scale of a portion of the bearing shown in FIG. 7. 
     FIG. 17 is a fragmentary sectional view on an enlarged scale of a modified form of bearing. 
     FIG. 18 is a perspective view of a modified form of bearing. 
     FIG. 19 is a perspective view of a further modified form of bearing. 
     FIG. 20 is a perspective view of another form of bearing. 
     FIG. 21 is a perspective view of further form of bearing. 
     FIG. 22 is a perspective view of another form of bearing. 
    
    
     DESCRIPTION 
     Referring to FIGS. 1-4, the invention relates particularly to a pressure energy translating device in the form of a pump or motor that is of generally well known construction and comprises a housing 20 with a housing cover 21. A drive shaft 22 is mounted in the pump housing and cover and supports a rotor 23 which houses an annular series of pump cylinders 24, each of which incorporates an axially movable pump piston 25. Each pump cylinder 24 has an opening 26 and these openings function, as the rotor turns, in a manner like that of a slide valve with the pump housing cover 21. The pistons 25 in the cylinders 24 work in unison with an obliquely set yoke 27 in such a manner that as the rotor revolves, the pistons produce an axial back-and-forth motion. The yoke 27 has arcuate bearing surfaces of seats 28 that are engaged by arcuate saddle bearings 30 mounted in recesses 31 in the housing 20. A spring 33 yieldingly urges the yoke 27 to an oblique position, as shown, when under no pressure. The yoke 27 can be moved under pressure from a piston 34 to vary the pump displacement. Pressure regulators and other controls are provided in the head 21 as is well known in the art. 
     In accordance with the invention, the bearing 30 comprises an arcuate body of thermoplastic material, preferably polytetrafluoroethylene, and an arcuate reinforcing member at least partially embedded in the plastic body. 
     Referring to FIGS. 5-9, a preferred form of bearing comprises the plastic body 35, an arcuate metal shim 36 having openings 37 through which a portion of the plastic extends, and an arcuate metal backing member 38 adhered to the shim and plastic by adhesive 39. 
     The bearing is made initially in flat form. By using a film form of adhesive that is cured by heat and pressure, the three piece bearing can be formed into one unit by the application of pressure in a heat box. In this process, the plastic 35 is formed through the openings 37 and the metal member 36 is adhered to the backing member 38. After curing, the bearing is formed to the required shape. Alternatively, the body 35 and metal member 36 may be formed and shaped prior to applying to the previously curved backing member 38. In a typical example, the thickness of the thin member 36 is 0.381 mm, the assembled thickness of the bearing is 3.00 mm and the thickness of the backing member 38 is 1.9 mm. The openings in the thin member 36 have a diameter of 1.00 mm and are provided in rows spaced apart 2.00 mm. 
     The openings 37 in metal member 38 are preferably formed such that they are not of the same cross section in order to increase the shear strength. More specifically, if the openings 37 are photochemically etched, they have an hourglass shape, as shown in FIG. 16, including a narrow intermediate portion 37a, and flared end portions 37b, 37c which serve to more effectively lock the plastic body 35 and metal member 36. This increases the shear strength. If the openings 37 are formed by punching, the punching operation results in a narrow portion 37d, a sharp edge 37e at one end and a flared portion 37f at the other end. This also serves to increase the shear strength. 
     In the form shown in FIGS. 10-13, the bearing comprises an embedded member in the form of a specially fabricated metal wire mesh provided adjacent one surface of the body 35a. As shown in FIG. 11 on a greatly enlarged scale, the interwoven wires 40, 41 of the reinforcing member 36a are flattened as at 42 by passing through rollers and are sintered to one another so that the wires 40, 41 are bonded and fixed relative to one another prior to embedding in the body 35a. The bearing can be utilized with or without a backing member 38a adhered to the bearing. As shown in FIG. 12, the body is first fabricated in flat form and then rolled and curved to the desired arcuate configuration as shown in FIG. 13. 
     In the form shown in FIG. 14, the backing member 38 has been replaced with a second coarser form of screen 45. In this form, it is possible to fill the rear of the bearing with a polymer material 35b to form a compliant bearing. The wires 40a, 41a are flattened and sintered first screen as by sintering. 
     In the form shown in FIG. 15, a backing plate 38c also has openings 46 through which the plastic of the body extends to form a compliant bearing which will accommodate tolerances in the surfaces 38c. 
     In can thus be seen that in each of the forms of the invention, the effective yield strength of the plastic polymer is increased by utilization of an embedded thin member which has the effect of minimizing the yielding under load by mechanically locking the polymer in place. 
     In the form where the embedded member comprises woven metal screening, the welding or bonding of the strands together with the flattening of the strands increases the mechanical bonding and prevents the strands from sliding relative to one another. 
     In the form of bearing shown in FIG. 18, the bearing 50 is cylindrical such as may be used to support the ends of a rotating shaft subjected to radial loads. The bearing 50 comprises an inner elastomeric body 51, an intermediate embedded reinforcing member 52 and an outer metal backing member 53 adhered to the reinforcing member. 
     In the form of bearing shown in FIG. 19, the bearing 55 is frustoconical and can be utilized in arrangements wherein the bearing is subjected to both radial and axial loads. The bearing 55 includes an inner elastomeric body 56 in which a frustoconical reinforcing member 57 is embedded and an outer metal frustoconical backing member 58 on the exterior adhered to the reinforcing member. 
     In the form of bearing shown in FIG. 20, the bearing 60 is annular for use in arrangements that are subjected to thrust loads. The bearing 60 comprises an elastomeric body 63 in which a reinforcing member 62 is embedded and a metal backing member 61. The bearing has parallel planar surfaces 64 which contact the surfaces that apply the load. 
     In the form of bearing shown in FIG. 21, the bearing 65 is for use under axial loads and comprises an elastomeric body 68 in which a reinforcing member 67 is embedded and a backing member 66 of metal is provided on one side. As in the form shown in FIG. 20, the bearing has parallel planar surfaces 69. 
     In the form of bearing shown in FIG. 22, the bearing 70 combines a cylindrical bearing 50a like that shown in FIG. 18 with a thrust bearing 60a like that shown in FIG. 20. 
     In each of the forms of bearing shown in FIGS. 18-22, the reinforcing members 52, 57, 62 may comprise a metal body having perforations therein, as shown in FIGS. 7-9; or a specially fabricated metal wire mesh such as shown in FIGS. 10-13; or a backing member with a coarser form of screen as shown in FIG. 14; or a reinforcing member with perforations and a full fabricated metal wire mesh as shown in FIG. 15. In addition, in each of the bearings, where the reinforcing member comprises perforations, the openings may be conformed in the manner shown in and described in connection with FIGS. 16 and 17. 
     It has been found that in each of the forms comprising a metal body with perforations, such as shown in FIGS. 7-9 and 15, the metal body should have a roughened surface finish at the interface with the plastic body. This is typically achieved by sandblasting, giving a surface finish between an Ra value of 40 to 125 microinches. It has been found that such a roughened surface finish adds significantly to the life of the bearing in the environment in which it is used.