KR940002801B1 - Hydrodynamic bearing and method of making same - Google Patents

Abstract

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Description

Fluid bearings and methods of manufacturing the same.

1 is a cross-sectional view of a journal bearing illustrating a sector embodying a form of the present invention.

2 is a schematic of a single pad made in accordance with the example described in FIG.

FIG. 3 is an edge view of the pad of FIG. 2 illustrating the pad direction of the support structure under load. FIG.

4 is a cross-sectional view of a sector of a second example of a journal bearing made in accordance with the present invention.

FIG. 5A is a section of the single pad of FIG. 4; FIG.

5b is a perspective view of a modified form of the bearing indicated in FIG.

5c is a perspective view of a modified form of the bearing indicated in FIG.

6 is an end view of the bearing of FIG.

7 is a diagram of the torsional deformation of a greatly enlarged beam.

8 is a cross-sectional view of a journal bearing illustrating an example of a bearing incorporating features of the present invention comprising two beams.

9 is an edge map of the pad of FIG. 1 illustrating local deformation of the pad surface without greatly exaggerating support structure deformation,

FIG. 10A is an edge map of the package of FIG. 8 illustrating the pad direction of the support structure under load. FIG.

FIG. 10B is an edge map of the pad of FIG. 8 illustrating the local deformation of the greatly exaggerated pad surface.

11a and b are cross-sectional views of a blank or cylindrical journal prior to machining.

12a and b are cross-sectional views of a cutting journal or blank.

13A and 13B are cross-sectional views of a cutting journal or blank.

14A and B are cross-sectional views of a modified cutting journal or blank.

14c and d are cross-sectional views of bearings constructed from the modified cutting journal or blank of FIGS. 14a and b.

* Explanation of symbols for main parts of the drawings

14: beam 16: stud section

12: pad

The present invention relates to a fluid bearing known as a rotating pad bearing and a method of making the same.

Generally such bearings are installed in such a way that they can move and allow formation of a wedge of lubricant between the relatively moving parts. Originally, the pads are displaced by near-center rotational movement or pivoting located in front of the pad surface and bearing friction tends to open the wedges. This application requires the application of section 120 of the US Patent Act with respect to Applicant US Application No. 07/0551340, filed May 29, 1987.

Hall patent, US No. In 2,137,487 a movable pad bearing of a fluid piping its fluid wedge is indicated by sliding its pad along a spherical surface. In many cases, pad sticks and mating wedges cannot be piped.

Greene patent, US No. In 3,930,691, fluctuations are caused by elastomers that are subject to contamination and degradation. Pads that are stretched in rows such as webs are formed in such a way that a wedge of lubricant is formed between the relevant moving parts. 4,496,251.

U.S. Patent No. It is also noteworthy that in 4,676,668 the bearing pads are placed at regular intervals in the support member by at least one leg providing flexibility in three directions.

To provide flexibility to the working surface, the legs are bent inward to form a conical shape at the front intersection of the pad surface. Each leg has a relatively small section modulus in the desired direction of motion to correct misalignment.

The present invention discloses padded bearings and the like.

Pad-type bearings have a support structure that can support the pads for movement of six degrees of freedom (bogie, tx, -x, + y, + z and -z directions), and on the journal walls that define the flexible pads. Or through a slit or cut and through a small groove or as a single cylindrical journal, if possible.

The support structure consists of a membrane and / or a beam, a support stub, preferably in a single, housing defined by the radially furthest position of the bearing. The inventors have found that in such particular applications, such as in heavy stone applications, it is necessary to test and evaluate the dynamic availability of the entire system consisting of bearings and fluid lubrication membranes, rotors or shafts.

Computer analysis of this system using a limited base model has necessitated the handling of a complete bearing as a flexible member that completely changes the phenomenon under operating loads.

By adding some flexibility through the machining of basic structures, bearing characteristics can be achieved by a stable low friction action over a wide operating range. Many variables substantially affect the performance characteristics of a bearing.

Among the most important variables are the support members and the physical properties of the pads (eg, modulus of elasticity, etc.) and their position, size and shape, defined by the grooves formed in the bearing and the cut or slit. Is especially important.)

In addition, by supporting the flexible member with fluid, a high degree of damping can be achieved by further adding to system stability. In some instances this damping has been replaced by secondary squeeze film damping when an oil film is present between the bearing and the casing of the housing.

The bearings of the invention are particularly applicable to turbochargers, turbines and compressors / expanders. The test speed exceeded 300,000 r, p, m. It is noteworthy that machining well with a bearing pad that operates to form a converging wedge for fluid lubrication causes the pad to change shape and bevel by way of flattening. This improves operating performance by varying the eccentricity of the bearing between other objects.

Bearings are formed of metal, powdered metal, plastic, ceramics or composites.

When produced in small quantities, the cut is typically made by electrical discharge or laser machining methods and makes the entire design soluble to make it the desired characteristics. Tuning essentially changes the stiffness that in turn eliminates vibration.

Mass production of single bearings is achieved through die-casting of metal powder, which is injection molding, casting, sintering and extrusion or otherwise. Unlike conventional pad bearings having a support structure that is oriented essentially in the direction of the load, the present invention provides a deflection and shrinkage wedge that is compared within a smaller envelope (difference between the radial inner journal surface and the radial outer journal surface). To actuate the bearing pad in any direction (eg, six degrees of freedom) to form a shape; Allowing the pads themselves to change shape (eg, flattening) to improve performance and provide a direction for the development of a membrane damping system for improved stability.

While there are multiple arrangements of grooves, cuts or slits, for the first time the load in both the white mode and the secondary is caused by the deviation of the two modes, ie the torsional deviation of the beam or member in the direction extending away from the pad along the longitudinal axis of the shaft. There is one or more bands or membranes that tilt in the general direction.

In the bending mode, the degree of deviation refers in part to the stiffness of the support structure in the radial direction. The pads themselves are inclined under load to make other shapes by undercutting the edges of the pads or internal cutting under the pads. In either case the cut is made into a predetermined shape under load. A damping element is added to the structure while supporting and enclosing any membrane or strip of lubricating fluid.

The bearing of the present invention includes a pad that changes shape and can operate in either direction. (Eg, support movement as 6 degrees of freedom). The bearings also have their own damping system and are preferably one or a single structure for large economic production. The bearings are also suitable for relatively small envelopes (there is a gap between the bore, the outside diameter of the housing and the inside diameter of the pad).

Further, the necessity of close tolerance between the inner diameter of the bearing and the outer diameter of the shaft is such that the radial stiffness of the bearing dimensions the support structure of which the radial stiffness of the bearing is smaller than that of the supporting fluid. This can be avoided by dimensioning the bearings to remove a certain distance between them. In such a case, the proper spacing between the pad and the shaft occurs instantaneously as the shaft rotates due to the rigidity of the fluid film.

In this bearing, the pad motion transfers the force between the unbalanced pads and the force that adjusts the misalignment of the shaft to the pad and also towards the shaft to maintain the shaft position. Of course, the present invention applies to a trust form of a bearing and to a trust or combination radial, any radial and naturally in one or two directions depending on the placement of the bearing.

Many methods of bearing manufacture of the invention in accordance with the invention have also been observed. The choice of a particular method of manufacture depends on the material used and the large quantity of special bearings manufactured. In small quantities or when the production of a test standard and / or the production of molds or the like is required, the bearings are numerically controlled laser cutting techniques or numerically controlled. Surface defects formed into radial cuts or slits and / or machined to a given radial through a numerically controlled eletrical discharge manufaturing technique are machined and produced from journal or metallic cylindrical blacks. In mass production, the bearings of the present invention can be manufactured using a wide range of materials such as plastics, ceramics, powders, non-powder metals and compositions. Many manufacturing methods can be used for mass production, including injection molding casting, powder metal die casting and extrusion.

The present invention will be described in detail with reference to the accompanying drawings.

The configuration described herein with reference to FIG. 1 firstly excites to define the housing 10 and the bearing pads 12 arranged in a plurality of phases supported in the housing by the beam 14 and the stub section 16. It is a sector of bearing assembly having a flaw and a slit formed in the groove. The bearing described is a radial unidirectional bearing and for example applies to radially supporting the rotating shaft only in one direction. In the described embodiment the bearing supports the shaft 5 which rotates only in the counter-clockwise direction described by the arrows. Each bearing pad 12 includes a leading edge 15 and a trailing edge 17. The leading edge is defined as the first approached edge by the circumferential point of the shaft as it continues to rotate.

Similarly the trailing edge is defined as an edge which is later circumferentially approached by the same point of the shaft as it continues to rotate.

When the shaft 5 rotates in its own direction, it leaves the trailing edge and moves over the bearing pad on the fluid film from the leading edge.

Optimal performance is achieved at a point 16a (FIG. 3) between the trailing edge 17 where the stub section 16 is closer to the centerline 13a and the circumferential centerline 13a of the pad 12. FIG. It is obtained when supporting the load and the bearing pad 12. The beam 14 also rotates around the point 14a positioned at an angle between the trailing edge and the leading edge such that the trailing edge 17 is inclined inward as a result of the deviation of the beam 14.

The degree of deviation, of course, depends on the cut or slit length formed in the bearing and the shape of the beam and other cuts.

Referring to Figures 2 and 3, the pad 12 consists of an arcuate face whose outer diameter of the shaft on which the pad is to be supported (via the fluid membrane) essentially corresponds to an arc or radius. Each pad is defined by radially and axially extending edges. The edge extending in the axial direction consists of the leading and trailing edge. The beams are shown in the static position (solid line) and inclined position (virtual line) in FIG.

The basic configuration as described in FIG. 1 is formed by small slits or cuts through the wall. Characteristically, these slits or radial cuts are between 0.002 and 0.063 '' wide. The degree of deviation can be varied by varying the length of the cut between the others. Longer cuts provide longer moment arms that produce greater deviations. Shorter cuts produce beams with smaller flexibility and higher load carrying capacity.

Care must be taken when selecting the length of the cut or slit to avoid resonance.

By positioning the ends of the beams 14 as indicated, the downward deviations around the connection point 16a may result in a slight flattening of the pads 12 as shown in the dashed line in FIG. It occurs in the internal movement of the trailing edge 17 of 12).

As a result of this deviation, the gap between the pad face 13 and the outer surface of the shaft 5 is wedge shaped to exhibit a well-known fluid support effect through the flow of the fluid. Ideally, the ratio of the gap between the leading edge and the shaft to the trailing edge and the shaft is between 1: 2 and 1: 5.

In other words, the spacing between the leading edge and the shaft should be between two and five times greater than the spacing between the trailing edge and the shaft. In order to obtain this ideal spacing or wedge ratio for any particular use, a variable of appropriate variation must be selected, including the material properties, shape, position, size and number of single elements.

Computers analyzing finite elements are the best way to optimize these variables. Computers for analysis are particularly useful in bearings of this type that allow movement in all six directions (6 degrees of freedom).

Referring to Figures 4 and 5a, the bearings are bearing pads 32 which are supported in the housing by beams having a pair of beam portions 34a and 34b which are substantially spread in a single line which is free of the pads. Formed with a dent and cut or slit to define the housing represents a second illustrative example of the bearing engagement characteristics of the present invention. Furthermore the pad must be undercut so that it is supported by the beam only on the pad support surface 34ps.

Referring to FIG. 5A, the beams 34, 34a appear to have convenient stub beam ends, such as (36,36a) acting as cantilever struts for the beam.

As is apparent from FIG. 4, the perspective view of FIG. 5A shows only one portion of the pad 32. The complete pad is illustrated in FIGS. 5B and 5C, indicating possible modifications of the bearing described in FIG.

As is apparent from the figure, the pad circumferential surface 34ps is located closer to the trailing edge 37 than the leading edge 35. With this structure the twisting of the beam as described in FIG. 7 is located in the middle of the beam and produces the described torsional deviation.

Again primary flexibility has been developed by small cut or slit through a bearing housing wall. These cuts provide a bearing pad with six degrees of freedom (eg, the pad rotates in the x, y, and z axes and rotates in the + x, -x, + y, -y, + z, and -z directions). can do).

If the cut or slit is finished before breaking through the formation of the beam portions 34a and 34b, the pad 32 must be supported by a continuous cylindrical membrane 34m as indicated in FIG. 5A. The membrane serves as a fluid damper on which the pad 32 is held. The end of the cut occurs at points A and B of FIG. The flexibility of the membrane combined with the fluid lubricant provides a way to isolate the pads from the housing and change the damping motion. Damping takes the form of dashpots that indicate high damping characteristics.

Like the bearings described in FIGS. 1 through 3, the FIGS. 4 through 7 are unidirectional bearings.

Thus, the bearing has a trailing edge 37 that leans inward to form a wedge and a leading edge 35 that leans out. Again, the wedge ratio (the ratio of the gap between the leading edge and the shaft to the trailing edge and the shaft) should be between 1: 2 and 1: 5.

Further, the position of the center of action of the load, primarily determined by the position of the pad strut portion 34ps of the beam 34 with respect to the pad, is located between the trailing edge and the circumferential center of the pad surface, rather than closer to the circumferential center of the pad surface. Should be

As shown in FIG. 5B, the beam is more simply defined than shown in FIG. 5A by simply stretching the cuts and slits downward at point A (B).

Referring to FIG. 8, the third illustrative example of the bearing engagement feature of the present invention is shown. In this example an internal slit or cut is provided for producing the beam on the beam support structure, in particular the bearing being scratched and slit or cut to define the pad 40 supported in the housing by the beams 42, 44. Is formed by.

The pad is connected to the beam at the support stubs 40a and 40b. The beam attached to the housing is at the support stubs 46 and 47. Again the bearing consists of a thin cut or cut slit through the bearing wall. The cut or slit 60 beneath the pad surface requires additional flexibility so that the pad changes its shape under load to create an airfoil for the inflow of lubricant. Thus, with the support of the two beams on the beam, the pad acts as a spring like membrane (membranin).

10B shows the inclined shape of the pad 40 under load. As indicated in the figure, the pad can be made and supported to tilt into the airfoil shape under load. As evident in the figure, the pad can be displaced in the x, y, z directions as well as the rotation about the x, y, z axis, where the pad has six degrees of freedom.

Referring to FIG. 9, a partial inherent deviation of the pad surface 50 where the pad is flat in load is indicated. This deviation is combined with the support structure deviations shown in FIGS. 3 and 10 but is not critical.

The end result is the shape shown in FIGS. 3 and 10a or a finely curved surface.

As described with respect to each of the above examples, the bearing of the present invention has a bearing surface to be deformed that can be formed and can be modified by providing a wedge ratio of 1: 2 to 1: 5 and also has 6 It allows for degrees of freedom and can provide a dashed port damping action and is unitary.

The bearing of the present invention marks a special performance feature by the function of the pad moving by six degrees of freedom and the wedge formed as the deviation of the bearing pad.

Especially in unitary bearings, bearing dimensions and deflection variables, including the material properties, position, shape, size and number of the confined elements, can be adapted to any particular use to sustain various loads. Of these variables the shape of the support member is of particular importance.

The impact of shape of the support structure deviated nature of the support member of the inertia (inertia) variable bh ^3/12 (English units) of Motor garment (the main component of sectional module for a right angle cross-section, z = I / C = bh 2/6) View Can be applied when used in

The pad's ability to move even more freely allows the bearing to correct and correct the misalignment of the shaft. Regarding this, it is noteworthy that the bearing of the present invention has a self-correction characteristic which arises from the tendency of the bearing to return to an inclined state due to the rigidity of the bearing. Of course, the stiffness of the bearing basically has the function of forming the supporting structure and has a small range of other deflection variables including the material properties, position, size and number of elements defined by the defects and cuts or slits formed in a single element. have.

Stiffer bearings have a larger self-correction tendency but can reduce the misalignment of the shaft. The tests show that bearings incorporating features of the present invention exhibit improved performance compared to the structures disclosed in my previous patent.

In recent years, a radial bearing was used as a bearing of the present invention as a radial envelope of 0.091 '' (2.31 mm). The inner deflection of the bearing pads was 0.003 '' (0.0076 mm), providing bearing performance and extraordinary stability.

A similar displacement using the arrangement shown in my previous patent number 4,496,251 requires a radial space of 0.30 '' (7.6 mm). In previous fluid journal bearings it was generally necessary to provide fluid film clearance between the bearing pad surface and the shaft outer diameter. This requires extremely precise manufacturing tolerances that are difficult for mass production.

However, the bearing of the present invention can be designed to eliminate the need for such precise manufacturing tolerances. In particular by providing suitable grooves and cuts or slits it is possible in practice to define bearings which have in fact some desired performance characteristics. One such property is the spring property or rigidity of the bearing pad in radial, eg radial stiffness.

It is known in the bearing technology that the fluid film between the shaft and the bearing can be shaped as a single spring when it has spring properties or a calculated radial fluid film stiffness. This is true for both compressible and non-compressible fluids but is particularly useful for gas fluid lubricants.

If the radial fluid film stiffness or the spring characteristic exceeds the radial stiffness or the spring property, the radial fluid film stiffness and the radial bearing stiffness operate opposite to each other and the bearing tilts in the radial direction until the radial stiffness of the fluid and the bearing are balanced. .

Thus, if a bearing is designed such that the radial stiffness of the bearing is less than the radial stiffness of the fluid film, the radial stiffness of the fluid film automatically simultaneously produces the appropriate radial deflection of the bearing on the rotation of the shaft.

The radial stiffness of the bearing is of course the primary function of the shock module or section of the support structure, which depends on the shape of the support structure.

The radial stiffness of the pad also depends on the length of the cut or slit formed in the bearing, so the present invention can achieve high performance without the precise manufacturing tolerances typically required for fluid bearings.

This feature of the invention is particularly advantageous for bearings using gas lubricating fluids and for mass production of bearings. In small quantities, the bearings disclosed herein are made by laser cutting methods or electrical discharge machining.

The double line shown in the diagram is a substantial passageway for the beam or wire, typically 0.002 to 0.060 '' (0.50 to 1.52 mm) in diameter.

Lubricants flowing through electrical discharge machining passages act as fluid dampers that reduce any vibration or instability at resonance frequencies.

In this position where a continuous cylindrical membrane is formed, damping has the formation of dashpots that exhibit high damping properties and it is important in the design that the support structure length and direction be done to provide the internal deviation shown in FIG.

The instantaneous deviation of the pads themselves in the loading direction as also indicated in FIG. 9 is also caused by the eccentric change which further improves the bearing performance.

In faires, mechanical element design, the distance between the center of the bearing and the center of the shaft is called the eccentricity of the bearing. This term is well known to those who are familiar with bearing design.

Optimum performance is obtained immediately by applying new modifications or adjustments to the rigidity of the beam and bearing arrangement or structure, in particular to suit specific bearing applications.

Recent computer analysis has proved that any stiffness or deviation can actually be set.

As described above, when manufacturing a circular or small amount of the bearing of the present invention, the bearing is rather constituted by a laser cutting method or an electric discharge machining. Such small amounts or circles usually consist of metal. However, when mass production of special bearings is planned, injection molding, mainly powder metal die casting and other manufacturing methods such as extrusion are more economical. It is more economical to use plastics, ceramics, metal powder, or compositions to form the bearings of the present invention with respect to such manufacturing methods. Powdered metal die casting by compression and sintering. Methods such as casting, and injection molding are well known, without requiring the process described above herein.

It is also well known to those skilled in molding and casting techniques to produce molds or the like for mass production of bearings once circular bearings are constructed.

Moreover, only certain types of bearings of the present invention are applied to mass production through compression.

In general, these are bearings which are formed only through the definition of a circumferential cut or slit and a circumferential groove and radial, which extend axially through the entire bearing.

As the above description, the description of the method of producing a single bearing through the use of the discharge manufacturing and machining is well known.

Each bearing is initially in the shape of a cylindrical blank having a cylindrical bore as indicated in Figures 11a and b. The blank is machined to provide an oiled radial to the fluid grooves as indicated in Figures 12a and b.

For special use it is desirable to further machine the blank to include a surface abutting symmetrically arranged grooves on the radial face of the bearing as shown in figures 13a and b.

Ultimate contact with the grooves results in an easy twisting.

When the grooves shown in Figs. 13A and 13B are cylindrical, it is possible to provide tapered grooves shown in Figs. 14A and 14B.

As will be apparent in the following, this produces a bearing that exhibits improved deviation characteristics by the angled alignment of the strut beam.

In this regard it should be noted that a strut beam such as that shown in Figure 14a is preferably tapered along a line that converges at the point nearest the centerline of the shaft.

This ensures that flexibility occurs in the vicinity of the shaft center line, making the center of operation for the entire system so that the pads adjust to shaft misalignment. Fundamentally, tapering of the strut beam causes the bearing to act in a manner similar to spherical bearings by concentrating the strut force on a point around the shaft turning in all directions to correct any misalignment.

Arrows in FIG. 14A illustrate the operating line of the deviation. After the cylindrical blank has been properly machined as indicated in Figs. 12a and b, 13a and b, or 14a and b, the radial and / or circumferential slit or groove shall be placed in the housing, beam holder and bearing pad. It is formed along the radial face of the machined blank to define a.

Figures 14c and d illustrate such grooves formed in the machined blanks of Figures 14a and b. In the manufacture of prototypes of bearings or small quantities of bearings for use in the structure of molds, cuts or slits are formed rather than through electrical discharge manufacturing or through the use of lasers.

Machining the cylindrical blanks to achieve the arrangement or similar shape described in FIGS. 12a and b, 13a and b, and 14a and b can be accomplished through lathes or such conventional machine tools. .

The performance characteristics of the bearings of the present invention come from the relative shape, size, position and material properties of the beam pads and bearing pads defined by the cuts or slits formed in the machined blanks.

These parameters are usually defined by the radial circumferential cut or dimension of the slit and position formed in the bearing, depending on the shape of the machined blank in which the slit is formed to produce the bearing.

As described above, when the configuration of the bearing of the present invention is very easily understood with respect to the machining process, the mass production of the bearing planned by the present invention can be carried out more economically through injection molding, casting, powder metal die casting, extrusion, or the like. There is a number.

In forming a large number of bearings in a cylindrical blank, such as a pipe, a radial lubricating fluid groove as shown in FIGS. 12A and B may be provided along the length of the cylindrical blank, such as a pipe, prior to forming.

However, if facing to the groove is desired in the bearings, these can be individually defined after cutting out individual bearings from the molded and machined blanks.

For this reason, molding is not a preferred method for producing bearings that require them to face the grooves in order to improve the flexibility of the torsion.

Claims (35)

The housing formed of a unitary cylindrical housing, the housing including a radially outer surface and a radially inner surface; The housing formed of a plurality of circumferential cuts that are continuous of the radial cuts and a plurality of radial cuts extending radially outward of an inner surface of the housing; The radial and circumferential cuts that together define a unitary support structure consisting of a member, such as at least one concentrated beam supporting each pad, and a plurality of circumferentially arranged bearing pads, wherein each pad in the direction of the axis An circumferential shaft that extends and also radially extends the edge and uses the surface, one of said axially extending edges of each pad consists of a leading edge and extends to another axial direction of each pad The edge is comprised of a trailing edge, the trailing edge of the surface of the pad moving radially to the shaft inner foot, and the leading edge to vibrate relative to the support member to move radially outwardly from the shaft To support the shaft with the face of the pads acting with friction and pressure on the surface Applied fluid bearings. The fluid bearing of claim 1 wherein a member, such as said at least one focused beam, is inclined with a torsional mode. The fluid bearing of claim 1 wherein a member, such as said at least one focused beam, is inclined with a curved mode. 2. A fluid bearing as claimed in claim 1, wherein a member, such as said at least one focused beam, consists of two beam portions extending away from the pad on the cavity axis. The fluid bearing of claim 1 wherein each said pad is supported by a member such as two beams extending away from the pad and extending on the cavity axis. The fluid bearing of claim 1 wherein the unitary support structure supports the pad along a pad support surface and the pad support surface is spaced at regular intervals at the axially extending and radially extending edges. The fluid bearing of claim 1 wherein said at least one beam-like member is connected to the pad by a stub section perpendicular to the beam-like member. The fluid bearing of claim 1 wherein the bearing pads are supported by a unitary support structure to be flat under load. The fluid bearing of claim 1 wherein a pad is defined by the radial and circumferential cuts to tilt under a biased load that modifies the eccentricity of the bearing. The fluid bearing of claim 1 further comprising a fluid lubricant located within the range of the support structure. The fluid bearing of claim 1 wherein a plurality of said beam-like members extend circumferentially and are radially spaced apart from the pad. The fluid bearing of claim 1 wherein a plurality of said beam-like members extend axially and spaced apart at a pad. The fluid bearing of claim 1 wherein said pad is supported for deflection of a point circumferentially located circumferentially between said leading edge and said trailing edge. The fluid bearing of claim 1 wherein the pad has a circumferential centerline that extends in an axial direction and the pad is supported to operate at a point where a load applied thereto is located between the circumferential centerline and the trailing edge. . The fluid bearing of claim 1 wherein each of said pads is supported by said support structure to allow movement of six degrees of freedom. The fluid bearing of claim 1 wherein the pad is inclined such that the trailing edge is between two and five times closer to the shaft than the leading edge and is supported under such normal load. A cylindrical journal having a cylindrical hole and a plurality of thin radial and cylindrical cuts formed therein, the holes defining the plurality of bearing pad means and the cut, and a unitary support structure for supporting each of the bearing pads In a fluid bearing supporting a shaft that rotates in a housing including; Each said pad means consists of a load which engages a member surface, said member surface being separated from said housing by a unitary support structure, said unitary support structure being in contact with at least one line in contact with said member surface. Consists of a member such as at least one beam having at least one portion thereof extending substantially parallel, the member surface having a load engaging the surface to operatively support the relatively opposite moving portion of the shaft and And the member surface is applied under the action of friction and pressure on the load engaging the moving surface in relation to the housing to form a converging wedge shape for operatively supporting the shaft portion in a bearing relationship. The bearing pads for at least one of deviation and torsion. Supporting fluid bearing. 18. The fluid bearing of claim 17 wherein said bearing pad means, said unitary support structure and said housing are formed in a unitary member. In a fluid bearing supporting a shaft comprising a unitary cylindrical body having a central hole, the cylindrical body defines a plurality of radial cuts and a plurality of circumferentially arranged bearing pads extending radially outward of the inner surface of the housing. With its successive plurality of circumferential cuts, each bearing pad is supported on a flexible cylindrical membrane, the cylindrical membrane allowing the bearing pad to move in either direction, and the membrane in at least one direction. A fluid bearing that provides a damping fluid. 20. The fluid bearing of claim 19 wherein a single cylindrical membrane bears all of the plurality of bearing pads. A unitary bearing for supporting a shaft, wherein the bearing includes a plurality of circumferentially spaced bearing pads, each pad having a circumferentially curved pad surface extending between the leading edge and the trailing edge, Including trailing edges and leading edges; The support structure consists of a support member such as a beam positioned radially outward of the bearing pad, and a stub portion connects the bearing pad to a member such as the beam and the bearing for movement relative to the beam member and the housing. Bearing a pad, the beam being supported on the housing for movement therewith, the fluid bearing being configured to have an opening space between each point on the bearing pad face and the support member. 22. The fluid bearing of claim 21 wherein the bearing pad is supported by the support structure such that the pad has six degrees of freedom. 22. The fluid of claim 21 wherein the bearing pad surface has a circumferential centerline extending in an axial direction and the support portion supports the bearing pad at a point between the circumferential centerline and the trailing. bearing. 22. The method of claim 21, wherein the leading edge is radially outwardly radially outward so that a bearing is two to five times closer to the shaft than the leading edge is to the shaft. A fluid bearing supported to incline to a load near the point between the training ring edge and the leading edge so as to radially inward. 22. The fluid bearing of claim 21 wherein the pad is formed to be flat under load by varying the eccentricity of the bearing. 22. The fluid bearing of claim 21 wherein the pad is formed and supported to tilt in an airfoil shape under load. 22. The fluid bearing of claim 21, wherein the pad supports the shaft for pivoting near the point closest to the centerline of the shaft to control misalignment of the shaft. The fluid bearing of claim 21 wherein said bearing is comprised of plastic. The fluid bearing of claim 21 wherein said bearing is comprised of a magnetic material. The fluid bearing of claim 21 wherein said bearing is comprised of copper. 22. The fluid bearing of claim 21 wherein the bearing is formed of sintered metal. 22. The fluid bearing of claim 21 wherein said beam is supported for pivoting about said housing about a point located at an angle between said leading edge and said trailing edge. A bearing for bearing a shaft, the bearing comprising a plurality of circumferentially spaced bearing pads, each bearing pad consisting of a leading edge, trailing edge and a circumferential curved surface; A unitary support structure supports the bearing pad and the trailing edge radially outwardly of the leading edge of each pad such that the leading edge is closer to the shaft by two to five times than that on the shaft. Supporting the shaft with the support structure such that the support structure bears the pad for six degrees of freedom movement such that the trailing edge of the pad is tilted and radially inwards toward such a shaft under normal load, A fluid bearing with an opening space between each point on the bearing pad face and the support member. The fluid bearing of claim 33 wherein said bearing pad is unitary by said support structure. In a bearing for supporting a shaft, the bearing consists of a plurality of circumferentially spaced bearing pads, the bearing pads having a circumferentially curved bearing surface and trailing edge extending between the trailing edge and the leading edge. And a leading edge, each bearing pad being supported by a unitary support structure for six degrees of freedom of movement, the support structure supporting the bearing pad such that the bearing pad has a predetermined radial stiffness, A fluid film is located between the bearing pad surface and the shaft, the fluid film having a special radial stiffness therein and the radial stiffness of the fluid film to cause the fluid film to cause the bearing pad to radially tilt outside the rotation of the shaft. Sharper configuration than the radial stiffness of the bearing pad A support, and a fluid bearing with an opening space between the support member and each point on the surface of the bearing pad.

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