BEAM MOUNTED BEARING PAD AND METHODS OF MAKING SAME

Abstract: A hydrodynamic bearing and methods of manufacturing the same. The bearing includes a bearing pad structure that may change shape and move in any direction (six degrees of freedom) to form a converging wedge for hydrodynamic operation, and to adjust for any shaft (5) misalignment. The pad (12) is separated from the support member by one or more beam-like members. The beams (14) extend substantially parallel to the plane of the face of the pad (12). The beams (14) allow defection of the pad (12) by either deflecting or twisting in a torsional mode. The bearings may be made of a wide variety of materials including plastics, ceramics, powdered metals, composites and metals. The bearings may be manufactured by injection molding, casting, powdered metal die casting, extrusion, electric discharge or laser cutting.

Description: BEAM MOUNTED BEARING PAD AKD METHODS O F MAKING SAME BACKGROUND OF THE INVENTION This application claims the benefits of 35 U.s.C. § 120 with respect to the applicant's copending U.S. Patent Application No. 07/055,340, filed May 29, 1 9 87. The present invention relates to hydrodynamic bearings that are also sometimes known as swing pad bearings and methods of making the same. Generally these be^i-ngs are mounted in such a way that they can move to permit the formation of a wedge-shaped film of lubricant between the relatively moving parts. Essentially the pad displaces with a pivoting or a swing-type motion about a center located in front of the pad surface, and bearing friction tends to open the wedge_ In the Hall patent, U.S. No. 2,137,487, there is shown a hydrodynamic moveable pad bearing that develops its hydrodynamic wedge by sliding of its pad along spherical surfaces. In many cases the pad sticks and the corresponding wedge cannot be developed. In the Greene Patent, U.S. No. 3,930,691, the rocking is provided by elastomers that are subject to contamination and deterioratio . There is shown in the Ide patent, U.S. No. 4,496,251 a pad which deflects with web-like ligaments so that a wedge shaped film of lubricant is formed between the relative moving parts. It has also been noted in Ide U.S. Patent No. 4,676,668, that bearing pads may be spaced from the support member by at least one leg which provides flexibility in three directions. To provide flexibilit in the plane of motion, the legs are angled inward to form a conical shape with the point of intersection in front of the pad surface. Each leg has a section modulus that is relatively small in the direction of desired motion to permit compensation for misalignment SUMMARY OF THS INVENTION The present invention discloses a pad type bearin and methods of making the same. The pad type bearing consists of a, preferably unitary, cylindrical journal that has been machined or formed with small grooves an slits or cuts through or on the journal wall to define flexible pad and a support structure capable of supporting the pad for movement in the six degrees of freedom (i.e., movement in the tx, -x r +y, -y, +s and directions.) The support structure is preferably unita and comprises support stubs, beams, and/or membranes connected to a housing which is defined by the radiall outermost portion of the bearing. The inventor has discovered that in many specific applications such as in high speed applications, it is necessar to examine and evaluate the dynamic flexibility of the entire system consisting of the sha or rotor, the hydrodynamic lubricating film and the bearing. In computer analysis of this system using a finite element model, it has been determined that it is necessary to treat the entire bearing as a completely flexible member that changes shape under operating loads. By adding more or less flexibility via machinin of the basic structure, bearing characteristics.may be achieved that provide stable low friction operation ove wide operating ranges. A number of variables have been found to substantially affect the bearing's performance characteristics. Among the most important variables ar the shape, size, location and material characteristics (e.g. modulus of elasticity etc.) of the pad and suppor members defined by the slits or cuts and grooves formed in the bearing. The shape of the support members has been found to be particularly important. Also by providing a fluid backing to the flexible members, a high degree of damping may be achieved that further add to system stability. In some instances, this damping has replaced secondary squeeze film dampening that is present when the oil film is present between the casing of the bearing and the housing. Specific applications of the bearing of the present invention include turbochargers, turbines and compressors/ expanders. Test speeds have exceeded 300,000 r.p.m. It is noted that the machining cuts, in addition to allowing the bearing pad to move to form a converging wedge for hydrodynamic lubrication, allow the pad itself to deflect and change shape by for example flattening. This improves operating performance by, among other things, changing the eccentricity of the bearing. The bearings may be formed of metals, powdered metals, plastics, ceramics or composites. When manufactured in small quantities, the cuts are typically ade by electrical discharge or laser machining methods and allow total design flexibility to tune the bearing to provide desired characteristics. Tuning will essentially change the stiffness that in turn eliminates vibration. Manufacture of large quantities of a single type bearing is ^ pre erably accomplished through injection molding, casting, powdered metal die casting with sintering and extrusion or the like. Unli e prior pad type bearings which have a suppor structure that is essentially oriented in the direction of load, the present invention provides an orientation that allows for comparable deflections within a smaller envelope (i.e., the difference between the radially inner journal surface and the radially outer journal surface) allows for movement of the bearing pad in any direction (i.e„, six degrees of freedom) to form a converging wedge shape; allows for the pad itself to change shape (e.g., flatten) to improve performance, an allows for development of a membrane damping system for improved stability. While there are numerous arrangements of grooves, cuts, or slits there are primarily two modes of deflections, namely one or more ligaments or membranes which deflect in the general direction of load in a bending mode and secondly by torsional deflection in a beam or member in a direction extending away from the pad along the longitudinal axis of the shaft. The degree of deflection in the bending mode is, in part, a function of the stiffness of the support structure in the radial direction. The pad itself may be made to deflect under a load to form a different shape by providing internal cuts beneath the pad or via undercutting the edges of the pad. In either case the cuts are specifically made to result in a predetermined shape under load. By surrounding or backing certain ligaments or membranes with lubricating fluid, a damping element may be added to the design. The bearing of the present invention includes a pad that may change shape and move in any direction (i.e., is supported for movement with six degrees of freedom) . The bearing-also may have a built-in damping system and is preferably of unitary or single piece construction for high volume economical manufacture. The bearing also fits in a relatively small envelope (i.e., spacing between the housing outer diameter and the pad inner diameter) , Further, the need for close tolerances between the bearing inner diameter and shaft outer diameter can be obviated by dimensioning the bearing so as to eliminate the spacing between the bearing inner diameter and shaft outer diameter while at the same time dimensioning the support structure such that the radial stiffness of the bearing is less that the radial fluid- film stiffness of the supporting fluid. In such an instance, an appropriate spacing between the pad and the shaft will be established instantaneously upon rotation of the shaft by virtue of the stiffness of the fluid- film. In the bearing of the present invention, the pad movement may be directed towards the shaft to hold shaft location and to give the pad the ability to adjust for misalignment of the shaft and unequal loading among pads. Of course, the present invention may apply to any radial, thrust or combined radial and thrust forms of bearings and may be one or two directional in nature, depending on the configuration of the bearing. In accordance with the present invention, a number of methods of manufacturing the bearings of the present invention are also contemplated. The selection of a particular method of manufacturing depends largely on the volume of the particular bearing to be manufactured and the materials used. In low volume applications, or when it is desired to produce prototypes for testing and/or production of molds or the like, the bearings are preferably manufactured from metallic cylindrical blanks -<5- or journals which are machined to provided radial and/o facing grooves and formed with radial cuts or slits through either numerically controlled electrical discharge manufacturing techniques or numerically controlled laser cutting technique , In high volume applications, the bearings of the present invention can be manufactured using a wide variety of materials such as plastics, ceramics, powdered and non~powdβred metals and composites. In high volume applications, a number of manufacturing methods including injection molding, casting, powdered metal die casting, and extrusion can be employed. BRIEF DESCRIPTION OF THE DRAWINGS The details of the invention will be described in connection with the accompanying drawing, in which; Fig. 1 is a sectional view of a journal bearing illustrating a sector thereof embodying one for of the invention? Fig. 2 is a schematic view of a single pad made in accordance with the example illustrated in Fig, 2 * ' Fig. 3 is an edge view of the pad of Fig. 2 illustrating the pad orientation with the support structure in the loaded state? Fig. 4 is a sectional view of a sector of a second exa le of a journal bearing made in accordance with the present invention; Fig. 5 is a view partly in section of a singl pad of Fig * • ; Fig. 5A is a perspective view of a section a modified form of the bearing of Fig, 4; Fig. 5B is a perspective view of a modified form of the bearing shown in Fig. 4; Fig.- 6 is an end view of the bearing of Fig. 4; Fig. 7 is a diagramatic view of the torsional. deflection of a beam, greatly enlarged? Fig. 8 is a sectional view of a journal bearing illustrating an example of a bearing incorporating the features of the present invention which includes two beams; Fig, 9 is an edge view of the pad of Fig. 1 illustrating local deflection of the pad surface withou support structure deflection, greatly exaggerated; Fig. 10 is an edge view of the pad of Fig. 8 illustrating the pad orientation with the support structure in the loaded state. Fig. 10A is an edge view of the pad of Fig. 8 illustrating local deflection of the pad surface greatly exaggerated. Figs. 11A and 11B are cross sectional views of a cylindrical journal or blank prior to machining; Figs. 12A and 12B are cross sectional views of a machined journal or blank; Figs. 13A and 13B are cross-sectional views of a further machined journal or blank; Figs. 14A and 14B are cross sectional view of a modified machined journal or blank; and Figs. 14C and 14D are cross sectional views o a bearing constructed from the modified machined journa or blank Figs, 14A and 14B. DETAILED DESCRIPTION OF THE ILLUSTRATIVE EMBODIMENTS Referring first to Figure 1, the structure therein illustrated is a sector of a bearing assembly having grooves and slits formed therein so as to define a housing 10 and a plurality of circumferentially arrange bearing pads 12 each of which is supported from the housing by a beam 14 and a stub section 16. The bearin illustrated is a radial unidirectional bearing, i»e., i is adapted for radially supporting a shaft for rotation in only one direction. In the illustrated embodiment, the bearing supports the shaft 5 only for rotation in the counter-clockwise direction illustrated by the arrow. Each bearing pad 12 includes a leading edge 15 and a trailing edge 17. The leading edge is defined as the edge irst approached by a point on the circumference of the shaft as it continues to rotate. Similarly, the trailing edge is defined as the edge approached circumferentially later by the same point on the shaft as it continues to rotate, when the shaft 5 is rotating in the proper direction, it moves, on a fluid film, from the leading edge across the bearing pa and off the trailing edge, optimum performance is obtained when the stub-section 16 supports the bearing pad 12 and hence any load, at a point 16a (Fig. 3) between the circumferential center line 13a of the pad 12 and the trailing edge 17 preferably, closer to the center line 13a. The beam 14 should also pivot about a point 14a which is located angularly between the leadin edge and the trailing edge so that as a result of deflection of the beam 14, the trailing edge 17 deflec inwardly, of course, the degree of deflection depends on, among other things, the shape of the beam and the length of the cuts or slits formed in the bearing. Referring now to Figs. 2 and 3, it will be seen that the pad 12 is provided with an arcuate face 13 which corresponds essentially to the radius or arc of the outer diameter of the shaft which the pad will be supporting (via the fluid film) and each pad is defined by aκially extending and radially extending edges. The axially extending edges comprise the leading and trailing edges. The beam is shown both in a static position (solid lines) and in a deflected position (phantom lines) in Fig. 3. The basic construction as illustrated in Fig. l, is created by the use of small slits or cuts through the wall. Typically these slits or radial cuts are between 0.002 to 0.063" wide. The degree of deflection can be varied by varying, among other things, the length of the cuts. Longer cuts provide a longer moment arm which yields greater deflection. Shorter cuts yield beams having less flexibility and higher load carrying ability. In selecting a length of cut or slit, care must be taken t avoid resonance. By locating the end of beam 14 as shown, the deflection downward about the connection point 16a will result in inward movement of the trailing edge 17 of th pad 12 outward movement of the leading edge 15 and a slight flattening of the pad 12 as seen in the dotted lines of Fig. 9,. As a result of this deflection, the gap between the pad face 13 and the outer surface of th shaft 5, through which fluid flows, becomes wedge shape to yield the well-known hydrodynamic support effect. Ideally the ratio of the spacing between the trailing edge and the shaft versus the spacing between the leading edge and shaft is between It2 to 1:5. In other words, the spacing between the leading edge and shaft should be between 2 to 5 times greater than the spacing between the trailing edge and the shaft. In order to attain this ideal spacing or wedge ratio for any specific application, appropriate deflection variables including number, size, location, shape and material characteristics of the unitary element must be selected. A computer aided finite element analysis has proven to be the most efficacious means of optimizing these variables. Computer aided analysis is particularly useful in a bearing such as the type described above which permits movement in all six directions (six degrees of freedom). Referring to Figs. 4 and 5, there is shown a secon illustrative example of a bearing incorporating feature of the present invention in which the bearing is formed with slits or cuts and grooves to define a bearing housing 30 with a bearing pad 32 that is supported from the housing by a beam having a pair- of beam portions 34a, 34b which extend substantially in a single line away from the pad. Moreover, the pad may be undercut s that it is supported by the beams only on a pad support surface 34ps. Referring to Fig. 5, it will be seen tha the beams 34, 34a have a convenient stub beam end as is 36, 36a which acts as a cantilever support for the beam As is evident from Fig. 4, the perspective view of Fig. 5 shows only a portion of the pad 32. The complet pad is illustrated in Figs. 5A and 5B which show possible modifications of the bearings illustrated in Fig. 4. As is clear from the drawings, the pad support surfaces 3 ps is located closer t© the trailing edge 37 than the leading edge 35. with this construction, twisting of the beam, as illustrated in Fig. 7 , will take place intermediate the beam and creat the torsional deflection illustrated, Again the primary flexibility is developed by small cuts or slits through the bearing housing wall. These cuts provide the bearing pad with six degrees of freedom (i.e., the pad can translate in the +x,-x, +y,-y, +2 and -z directions as well rotate about the x, y and z axes) . If the cuts or slits were terminated before breaking through to for beam portions 34a and 34b, the pad 32 would be supporte by a continuous cylindrical membrane 34m as shown in Fig. 5A. The membrane acts as a fluid damper upon whic the pad 32 is supported. The termination of the cuts would occur at Point A and Point B of Fig. 4. The flexibility of the membrane combined with the fluid lubricant, provides a means to vary the damping action and to isolate the pad from the housing. The damping takes the form of a dashpot that exhibits high damping characteristics. As with the bearing illustrated in Figs. 1-3, the bearing illustrated in Figs. 4-7 is a unidirectional bearing. Accordingly, the bearing has a leading edge 35 which deflects outward and a trailing edge 37 which deflects inward to form a wedge. Again, the wedge ratio (ratio of spacing between the trailing edge and the shaft to the spacing between the leading edge and the shaft) should be between 1;2 to 1:5. Moreover, the location of the center of action of the load which is primarily determined by the location of pad support portion 4ps of the beam 34 with respect to the pad should, again, be between the circumferential center of the pad face and the trailing edge, preferabl closer to the circumferential center of the pad face. As shown in Fig. SB, the beam may be defined more simply than shown in Fig. 5 by simply extending the cuts or slits downward from points A and B. 1:2 to 1:5, have a defor able bearing surface the shap of which can be modified, allow six degrees of freedom of the pad, can provide a dashpot type damping action, and are of a unitary construction. Sy virtue of the wedge formed by deflection of th bearing pad and the ability of the pad to move with si degrees of freedom, the bearing of the present inventi exhibits exceptional performance characteristics. Specifically, the bearing dimensions and deflection variables including number, size, shape, location and material characteristics of the elements defined in the unitary bearing can be tailored for any specific application to support a wide variety of loads. Of these variables, the shape of the support members is particularly important. The impact of shape of the support members on the deflection characteristics of th support structure can be appreciated when the variable formula for moment of inertia bh /12 (English units) (the main component of sectional modulus for rectangula 2 section, z **** - I/c **** - bh /6) used in an example. Moreover the ability of the pad to move with six degrees of freedom allows the bearing to compensate for and correc shaft misalignment. In this regard it is noted that th bearings of the present invention have a self correctin characteristic resulting from the tendency of the bearing to return to its non-deflected state due to the stiffness of the bearing. Of course, the stiffness of the bearing is primarily a function of the shape of the support structure, and to a lesser extent the other deflection variables including number, size, location, and material characteristics of the elements defined by the grooves and cuts or slits formed in the unitary element, stiffer bearings have a greater self- correcting tendency but are less able to adjust for shaft misalignment. ■ " ***" >f..3C..ST radial stiffness of the fluid and the bearing are in equilibrium. Thus, it has been found that if the bearing is designed such that the radial stiffness of the bearing is less than the radial stiffness of the fluid film, it is not necessary to provide a precise spacing between the shaft and the bearing because the radial stiffness of the fluid film will automatically and instantaneously, upon rotation of the shaft, cause appropriate radial deflection of the bearing. The radial stiffness of the bearing is, of course, primaril a function of the section or flexure modulus of the support structure which depends on the shape of the support structure. The radially stiffness of the pad also depends on the length of the slits or cuts formed in the bearing. Accordingly, with the present invention, it is possible to achieve high performance without the close manufacturing tolerances typically required of hydrodynamic bearings. This aspect of the present invention is particularly useful in high volume production of the bearings and with bearings using gas lubricating fluids. In small quantities, the bearings disclosed herein are preferably constructed by electrical discharge machining or laser cutting methods. The double lines shown in the drawings are the actual paths of the wire or beam which is typically 0.002-0.060"(0.50-1.52mm) in diameter. The lubricant that flows into the electrical discharge machined paths, acts as a fluid da pener that reduces any vibration or instability at resonant frequencies, in the situations described above where a continuous cylindrical membrane is formed, the damping takes the form of a dashpot that exhibits high damping characteristics. A significant consideration in the design is that the support structure length and direction be oriented to provide the inward deflection shown in Fig. 3. Also minute deflections of the pads themselves in the direction of load as shown in Fig. 9, result in eccentricity changes which further improve bearing performance, it is noted that in Faires, Desig of Machine Elements the distance between the center of the bearing and the center of the shaft is called the eccentricity of the bearing. This terminology is well known to those skilled in bearing design. With the nov approach of tuning o modifying the stiffness of the bearing configuration or structure and particularly th beam to suit a particular bearing application, optimum performance is readily obtained. Recent computer analysis has demonstrated that virtually any stiffness or deflection may be accomplished. As noted above, when manufacturing low volumes or prototypes of the bearings of the present invention, t bearings are preferably constructed by electrical discharge machining or laser cutting methods. Such small volumes or prototypes are usually constructed of metal. However, when high volume production of a particular bearing is contemplated, other methods of manufacture such as injection molding, casting, powder metal die casting and extrusion are more economical. connection with such manufacturing methods, it may be more economical to employ plastics, ceramics, powdered metals or composites to form the bearings of the prese invention. It is believed that methods such as injection molding, casting, powdered metal die casting with sintering and extrusion are sufficiently well kno that the processes need not be detailed herein. It is also believed that once a prototype bearing is constructed, the method of producing a mold or the lik for mass production of the bearing is well known to those skilled in the molding and casting art. Moreove it is to be understood that only certain types of the bearings of- the present invention are adapted to be ma in high volumes through extrusion. Generally, these a the bearings that are formed only through the provisio of circumferential grooves and radial and circumferential cuts or slits which extend axially throughout the entire bearing. With the foregoing in mind, it is believed sufficient to describe the method of making a single bearing through the use of electrical discharge manufacturing and machining. It is believed that a description of such manufacture demonstrates the ease with which the relatively complex bearing shapes of th present invention can be achieved. Each bearing is initially in the form of a cylindrical blank having a cylindrical bore as shown i Figs. HA and 11B. The blank is then machined to provide a radial lubricating fluid groove as shown in Figs. 12A and 12B. For certain applications, it is desirable to further machine the blank to include faci grooves which are preferably symmetrically disposed on the radial faces of the bearings as shown in Figs. 13 and 13B. The provision of such facing grooves ultimate results in a bearing which is easily torsionally deflected. While the groove shown in Figs. 13A and 13B are cylindrical, it is possible to provide tapered grooves as shown in Figs. 14A and 14B. As will become evident below, this yields a bearing which exhibits improved deflection characteristics by virtue of the angled alignment of the support beams. In this context it should be noted that it is preferable that the support beams as viewed in Fig. 14A are tapered along lines which converge at a point proximate the center line of the shaft. This ensures that flexibility occurs about the shaft center line by establishing a center o action for the entire system such that the pads may adjust to shaft misalignment. In essence, the tapering of the support beams causes the bearing to act in a aπner similar to a spherical bearing by concentrating the support forces on a single point about which the shaft may pivot in all directions to correct any misalignment. The arrows in Fig. 14A illustrate the lines of action of the deflection. After the cylindrical blank is properly machined shown in Figs, 12A and 12B, Figs. 13A and 13B, or Fig 14A and 14B radial and/or circumferential slits or grooves are formed along the radial face of the machin blank to define the bearing pads, the beam supports an the housing. Figures 14C and 140 illustrate such grooves formed in the machined blank of Figs. 14A and 14B. When manufacturing low volumes of the bearings o prototypes of the bearings for use in the construction of a mold, the cuts or slits are preferably formed through electrical discharge manufacturing or through the use of a laser. The machining of the cylindrical blanks to achieve the configurations illustrated in Figs. 12A and 12B, Figs. 13A and 13B, Figs. 14A and 14 or a similar shape can be done through conventional machine tools such as lathe or the like. The performance characteristics of the bearings o the present invention results from the relative shape, size, location and material characteristics of the bearing pads and the beam supports defined by the cuts or slits formed in the machined blank. These paramete are largely defined by the dimensions and location of the radial circumferential cuts or slits formed in the bearing in conjunction with the shape of the machined blank in which the slits ar formed to yield the bearing. As noted above, while the construction of the bearings of the present invention is most easily understood by reference to the machining process, larg scale production of the bearings contemplated by the present invention could be more economically performed through injection molding, casting, powdered metal, d casting, extrusiσn-σr the like. In extruding a large number of bearings from a pipe-like cylindrical blank, radial lubricating fluid grooves as shown in Figs. 12A and 12B can be provided along the length of the pipe-like cylindrical blank prior to extrusion. However, if facing grooves were desired in the bearing, these can be individually defined after slicing the individual bearings from the extruded and machined blank. For this reason, extrusi might not be a preferred method producing bearings whi require facing grooves to enhance torsional flexibilit -- * S_ ? S~izs-.~-—trτ a

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A bearing as in claim 1 wherein said unitary support structure supports said pad along a pad suppor surface, said pad support surface being spaced from sa axially extending and radially extending edges. 7. A bearing as in claim 1 wherein said at least one beam-like member is connected to the pad by a stub section that is at right angles to said beam-like member. S. A bearing as in claim 1 wherein the bearing pad i supported by the unitary support structure so as to flatten under load, 9. A bearing as in claim 1 wherein the pad is defined by said radial and circumferential cuts so as to deflec under loading said deflections modifying the eccentricity of the bearing. 10. A bearing as in claim 1 further comprising a fluid lubricant located within the support structure. 11. A bearing as in claim 1 wherein a plurality of sai beam-like members extend in a circumferential direction and are radially spaced from the pad. 1 . A bearing as in claim 1 wherein a plurality of sai beam-like members extend in an axial direction and are spaced from the pad. 13. The bearing as in claim 1 wherein said pad is supported for deflection about a point located circumferentially between said leading edge and said trailing edge. deflection and torsional twisting. IS. The bearing of claim 17, wherein said bearing pa means, said unitary support structures and said housi are formed from a unitary member, 19. A hydrodynamic bearing supporting a shaft comprising a unitary cylindrical body having a centra bore, said body having a plurality of radial cuts extending radially outward of the inner surface of th housing and a plurality of circumferential cuts in continuance thereof to define a plurality of σircu ferentially arranged bearing pads, each said bearing pad being supported on a flexible cylindrical membrane, said cylindrical membrane permitting the pa to move in any direction, and said membrane providing fluid damping in at least one direction. 20. The bearing of claim 19 wherein a single cylindrical membrane supports all of said plurality o bearing pads. 21. A unitary bearing for supporting a shaft, said bearing comprising a plurality of circumferentially spaced bearing pads, each said pad including a leadin edge, a trailing edge and a circumferential curved pad face extending between said leading edge and said trailing edge; a support structure comprising a beam-like suppo member located radially outwardly of said bearing pad, stub portion connecting said bearing pad to said beam¬ like member and supporting said bearing pad for a movement with respect to said beam member and a housin said beam supported on said housing for movement with respect thereto. 22. The bearing of claim 21 wherein said bearing pad construσted of bronze. 31. The bearing of claim 21 wherein said bearing is formed from a sintered powdered metal. 32. The bearing of claim 21 wherein said beam is supported for pivoting movement with respect to said housing about a point which • is located angularly betwe said leading edge and said trailing edge. 33. A bearing for supporting a shaft, said bearing comprising a plurality of circu ferentially spaced bearing pads, each said bearing pad comprising a leadi edge, a trailing edge and a circumferentially curved face; a unitary support structure for supporting each said bearing pads, said support structure supporting said pads for movement with six degrees of freedom suc that under normal loading said trailing edge of said p is deflected radially inward towards such shaft and sa leading edge of each said pad is deflected radially outward so that said trailing edge is between two to five times closer to said shaft than said leading edge is to said shaft. 34. A bearing of claim 33 wherein said bearing pads a unitary with said support structures. 35. A bearing for supporting a shaft, said bearing comprising a plurality of circumferentially spaced bearing pads, said bearing pads comprising a leading edge, a trailing edge and a circumferentially curved bearing face extending between said leading edge and said trailing edge, each said bearing pad being supported by a unitary support structure for movement with six degrees of freedom, said support structure supporting said bearing pad such that said bearing pad has predetermined radial stiffness, a fluid film 42. The method of claim 36 wherein said central bore and said slits are formed by injection molding. 43. The method of claim 36 wherein said central bore and said slits are formed by powdered metal die casti with sintering. 44. The method of claim 36 wherein said slits are formed by extrusion. 45. The method of claim 36 further comprising the st of forming a radial groove around the circumference o said cylindrical blank. 46. The method of claim 36 further comprising the st of forming symmetrical facing grooves on the opposed circular faces of said cylindrical blank.

Inventors: IDE RUSSELL D, IDE, RUSSELL, D.
Applicants: IDE RUSSELL D, IDE, RUSSELL, D.
Application year: 1988
Main classification: F16C17
IPC codes: F16C17, F16F15