US3814554A

US3814554A - Support means for rotating elements

Info

Publication number: US3814554A
Application number: US00244137A
Authority: US
Inventors: B Jansson; A Schmitz
Original assignee: JI Case Co
Current assignee: Case LLC
Priority date: 1970-04-13
Filing date: 1972-04-14
Publication date: 1974-06-04
Anticipated expiration: 1991-06-04

Abstract

The present disclosure relates to a method and apparatus for supporting a rotating element relative to a housing of a fluid translating device, by primary and secondary bearing means. The method contemplates supporting the rotating element for rotation about a fixed axis by the primary bearing means and diverting some of the pressured fluid in the high pressure port of the fluid translating device to chambers defined on a floating secondary bearing means adjacent an area of the rotor which is located adjacent the low pressure port to thereby balance the reaction forces produced on the rotor. The apparatus for defining the chambers receiving the diverted fluid includes first and second sleeves receiving the rotor supporting shaft with each of the sleeves having a plurality of outer recesses cooperating with the housing to produce pockets or chambers and a plurality of inner recesses cooperating with the shaft to produce inner pockets or chambers. Each outer pocket receives diverted pressurized fluid from the port which is in opposed relationship on the rotor or shaft and the outer pocket communicates with the inner pocket to direct this fluid into the area between the shaft and the bearing sleeve. The internal transverse dimension of the sleeves is slightly larger than the diameter of the shaft and the inner pockets are divided into first and second axially spaced portions so that any axial misalignment between the sleeves and the bearing will increase the flow path between the bearing and the shaft along one edge of the sleeve and decrease the flow path along the opposite edge to produce a pressure differential thereby automatically aligning the sleeve and shaft. The area of the sleeve between each of the portions of the inner recess has laterally offset segments so that all portions of the shaft will be exposed to the pressured fluid during each revolution of the shaft.

Description

United States Patent [191 J ansson et a1.

1 1 SUPPORT MEANS FOR ROTATHNG ELEMENTS [75] Inventors: Birger F. Jansson; Albert A.

Schmitz, both of Racine, Wis.

[73] Assignee: .1. 1. Case Company, Racine, Wis.

[22] Filed: Apr. 14, 1972 [21] Appl. No.: 244,137

Related US. Application Data [63] Continuation-impart of Ser. No. 27,722, April 13,

1970, abandoned.

Primary ExaminerCarlton R. Croyle Assistant Examiner.lohn J. Vrablik Attorney, Agent, or FirmDressler, Goldsmith, Clement & Gordon, Ltd.

[57] ABSTRACT The present disclosure relates to a method and apparatus for supporting a rotating element relative to a 51 June 4, 1974 The apparatus for defining the chambers receiving the diverted fluid includes first and second sleeves receiving the rotor supporting shaft with each of the sleeves having a plurality of outer recesses cooperating with the housing to produce pockets or chambers and a plurality of inner recesses cooperating with the shaft to produce inner pockets or chambers. Each outer pocket receives diverted pressurized fluid from the port which is in opposed relationship on the rotor or shaft and the outer pocket communicates with the inner pocket to direct this fluid into the area between the shaft and the bearing sleeve.

The internal transverse dimension of the sleeves is slightly larger than the diameter of the shaft and the inner pockets are divided into first and second axially spaced portions so that any axial misalignment between the sleeves and the bearing will increase the flow path between the bearing and the shaft along one edge of the sleeve and decrease the flow path along the opposite edge to produce a pressure differential thereby automatically aligning the sleeve and shaft. The area of the sleeve between each of the portions of the inner recess has laterally offset segments so that all portions of the shaft will be exposed to the pressured fluid during each revolution of the shaft.

15 Claims, 8 Drawing Figures PATENTEBJUH 41914 3814' 554 FIG. 4

SHEET 2 BF 2 I SUPPORT MEANS FOR ROTATING ELEMENTS REFERENCE TO RELATED APPLICATIONS This application is a continuation-in-part of our copending, now abandoned application, Ser. No. 27,722, filed Apr. 13, 1970.

BACKGROUND OF THE INVENTION The present invention relates generally to fluid translating devices and more particularly to an improved apparatus for supporting the rotating element in the isqtldst tent fsush,de s- HA n Fluid translating devices of the type to which this invention pertains are common in the prior art. One such device is commonly referred to as a vane type pump which includes vanes that are slidable in a rotor and in contact with the peripheral surface of a working chamber formed in a housing supporting the rotor. Generally, the rotor is supported within the working chamber by a shaft extending into a bore intersecting the working chamber in the housing.

in the vane pump of this type, it has been customary to have the working chamber movable relative to the fixed rotating rotor to be able to increase and decrease the flow of fluid between inlet and outlet ports respectively communicating with the working chamber, by moving the working chamber. In fact, it has been common to allow the circular working chamber to be moved radially on opposite sides of the axis of rotation of the rotor to thereby reverse the direction of flow of fluid between the respective ports.

While these types of pumps have found considerable commercial acceptance in recent years, their use has been restricted to comparatively small units in which the rotor can be carried by available commercial ball or roller bearings. in larger units the radial forces exerted on the rotor cannot be absorbed by ball or roller bearings because such bearings are subject to distortion when extreme radial forces are applied to the rotor shaft. Therefore, the use of other types of bearings, such as hydrodynamic or hydrostatic bearings, has been attempted.

While fluid bearings of the hydrostatic or hydrodynamic type have been known for years, these bearings have not found any degree of commercial success for utilization in pumps of the above-mentioned type. One of the problems encountered in hydrostatic bearings heretofore known is that the bearings required a separate source of pressurized fluid of considerable pressure and virtually no contamination so as to be operative for its intended purposes.

Fluid bearings of this type are discussed in an article entitled Practical Design Applications for Hydrostatic Lubrication" by T. L. Corey and E. M. Kipp appearing in the March, 1955 issue of Machine Design.

BRIEF SUMMARY OF THE INVENTION According to the present invention, a rotating element is supported within a housing of a fluid translating device in such a manner that the fluid translated by the device is utilized to help support the rotating element. According to the broadest aspect of the present invention, the rotating element or shaft is supported for rotation about a fixed axis by primary bearing means and the varying radial loads on the rotating element, resulting from reaction forces developed by the fluid, are absorbed by secondary bearing means. Stated another way, the reaction forces on the rotating element, from the fluid in the high pressure area are counteracted by diverting some of the fluid from the high pressure or outlet port to secondary bearing means positioned adjacent an area of the rotating element which is located adjacent the low pressure area or inlet port to pressure balance the rotating element.

The secondary bearing means or apparatus for producing the counterbalancing forces and auxiliary support for the rotating element within the fixed element of the fluid translating device is in the form of a bearing sleeve having an outer pocket formed between the housing and the bearing sleeve and a pair of axially spaced inner pockets formed between the bearing sleeve and the rotating element. The pressurized fluid from the high pressure port is directed to an outer pocket, which is located in opposed relationship to the pressurized area, and to the inner pockets to produce a counterbalancing force for the reaction forces on the rotating element at the high pressure area. The inner pockets communicate with the cavity adjacent the sleeves through small clearances or flow paths formed between the bearing sleeve and the rotating element or journal while the sleeve has an outer diameter smaller than the diameter of the bore so that the bearing sleeve is floatingly supported between the bore and the shaft by the fluid retained in the outer and inner pockets.

In order to provide a support mechanism for a reversible flow vane type fluid translating device, another aspect of the present invention contemplates that the bearing sleeve has a plurality of circumferentially spaced outer pockets and more particularly first and second pairs of diametrically opposed outer pockets that are respectively locatedadjacent the high and low pressure areas of the fluid translating device. The fluid from the low pressure port is directed to the pockets located adjacent the high pressure area while the fluid from the high pressure port is diverted to the pockets located adjacent the low pressure area. The arrangement provides a balancing force for any reaction forces produced in either of the ports.

The specific bearing construction is in the form of a sleeve formed integrally or in sections with the peripheral surface of the sleeve having four circumferentially spaced recesses. The internal surface of the sleeve has a pair of axially spaced recesses in opposed relation to each of the outer recesses and each pair of inner recesses is in communication with an outer recess. The inner recesses are separated by a portion of the bearing sleeve which has laterally offset circumferentially spaced segments. The laterally offset segments will insure that all portions of the shaft are exposed to lubrication. 1

Each sleeve also has a slot between at least some of the adjacent pairs of inner recesses. The slots extend axially between opposed edges of the sleeve and will prevent damage from thermal expansion of the metal between the inner pockets caused by a build-up in the temperature of the metals when the sleeve and shaft are close to each other or in contacting relation.

The communication between each pair of inner recesses and its respective outer recess is restricted so that fluid flow therethrough will not take place without a drop in the fluid pressure. Thus, the pressure in the outer recess will be higher than that in the inner recesses. With this arrangement, the sleeve will assume a balanced position between the bore and the shaft in which the flow of fluid out of the inner recesses through the clearance between the sleeve and rotating member will be equal to the flow into the inner recesses through the restricted communication from the outer recess. If the sleeve is moved radially relative to the shaft, the flow of fluid from the inner recesses on the high pressure side of the sleeve will be restricted resulting in an increase in pressure of the fluid in these inner recesses, while the flow of fluid from opposed recesses will increase and the pressure in these recesses will drop to near zero.

The rates of flow, the position of the sleeve, and the size of the clearances will vary according to the pressure in the translator and accordingly the support given to the rotating element will be that which is required to counterbalance the force thereon generated by this pressure.

The groups of inner first and second chambers formed between the bearing sleeve and the shaft will automatically compensate for any axial misalignment between the shaft and the sleeve. This necessarily results from the fact that when there is axial misalignment between the sleeve and the shaft, the flow from one of the inner chambers is greater than the flow from the other of the chambers to thereby produce a pressure differential between the chambers which will automatically cause the sleeve and shaft to assume an axially aligned position.

Thus, the sleeve having internal recesses is caused to automatically adjust its position relative tothe bearing journal to modify the flow of pressurized fluid supporting the ournal out of the recesses thus maintaining the pressure therein at the proper level to sustain a fluctuating load on the shaft without radial movement of the journal, carried by the shaft.

BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS FIG. ,1 is a side elevational view,'par tly in section, showing a fluid translating device having the present invention incorporated therein;

FIG. 2 is a fragmentary vertical sectional view taken generally along line 2-2 of FIG. 1;

FIG. 3 is an end view of the bearing constructed in accordance with the present invention;

FIG. 4 is a view, partly in section, taken generally along line 4-4 of FIG. 3;

FIG. 5 is a side elevational view of the bearing as viewed along line 5--5 of FIG. 3;

FIG. 6 is a projected view of a portion of the internal surface of the bearing shown in FIG. 3;

FIG. 7 is an enlarged fragmentary sectional view of the bearing in its assembledcondition between a rotating and a fixed element; and

FIG. 8 is an enlarged longitudinal sectional view of the bearing supported between the fixed element and the rotating element.

DETAILED DESCRIPTION FIGS. 1 and 2 of the drawings disclose a fluid translator unit or device, generally designated by the reference numeral 10. The unit or fluid translating device 10 is illustrated as a reversible flow vane type pump which includes a housing 12 having a working chamber 14 defined therein by a cam ring 16 which is supported in an opening in a camblock 18. The camblock is vertically shiftable in an opening 20 defined within the housing 12, for a purpose which will be explained later.

The fluid translating device further includes a rotor 22 keyed to a shaft 24 which is supported for rotation about a fixed axis in a bore or opening 25 by bearing journals 26 received in roller bearings or primary bearing elements 28. The rotor or rotating element has a plurality of circumferentially spaced radially extending slots 30 each of which slidably supports a vane 32. The rotating element also includes a pair of end plates 34 respectively keyed to the shaft 24 and adapted to cooperate with the cam ring and the camblock to seal the opposite ends of the chamber 14.

The working chamber 14 is adapted to receive fluid through a first or low pressure passage 36 formed in the housing 12, the camblock 18 and cam ring 16 and deliver the fluid at an elevated pressure to the second or high pressure passage 38. Such a condition occurs when the axis of the working chamber I4 is located above the axis of the shaft 24. However, if the working chamber is vertically shifted by the vertical movement of the camblock l8-and cam ring 16 so as to locate the working chamber below the axis of the shaft 26, the flow would be reversed and the passage 36 would become the outlet passage while the passage 38 would be the inlet passage.

As was indicated above, one of the problems encountered in producing large pumps of this type, which are capable of delivering fluid at relatively high outlet pressures, is that the bearings 28 tend to distort and render the pump inoperative. Furthermore, the limitations regarding close tolerances and the separate supply of pressurized fluid has limited the use of hydrostatic bearings for supporting the rotating element within the housing of the pump. It is well known that the necessity of having very close tolerances in commercial production machines greatly increases the costs thereof. Even assuming that the close tolerances could be formed for a hydrostatic bearing, the reaction forces produced in the outlet passage of the rotor 22 would create eccentricity between the shaft and bearing axes causing the rotating shaft to move closer to the bearing surface, which would result in metal-to-metal contact and produce increased temperatures resulting in destruction of the entire device.

According to the present invention,'the above problems encountered by normal roller type bearings or by hydrostatic bearings has been alleviated by utilizing a secondary bearing element which is floatingly supported between the housing and the rotating shaft with the fluid to the secondary element or bearing supplied by diverting fluid, which is translated by the device, in a manner to automatically compensate for the extreme reaction forces on the rotor resulting from the build-up of pressure in the outlet port.

According to the invention, first and second secon dary bearings 50 (FIG. 2) are respectively interposed between openings 52, which will be considered enlarged portions of the bore 25, and the bearing journals 26 supported on the shaft 24. The enlarged portions or openings 52, which are in axial alignment with the axis of the working chamber 14, are slightly larger than the peripheral size of the bearings and extend on opposide sides of the opening for receiving the bearing sleeves 50.

One bearing 50 is shown in detail in FIGS. 3-6 and includes a member or sleeve 54 having an outer surface 56 and an inner surface 57. The outer surface 56 has a plurality of circumferentially spaced recesses 58 with each of the recesses 58 being circumscribed by a groove 60 and the periphery of the sleeve is slightly smaller than the diameter of the enlarged portion 52 of the bore (FIG. 2), for a purpose which will be described later. The inner surface 57 likewise has a plurality of circumferentially spaced recesses 62 each of which is in opposed relationship to one of the outer recesses 58.

Each of the inner recesses 62 is divided into first and second axially spaced

portions

62a and 62b which are separated by a portion 64 of the internal surface 57 of the sleeve. The separating portion 64 is divided into Iaterally offset or axially spaced segments 64a and 64b,

.for a purpose to be described later. Each of the spaced portions 620 and 62b of the inner recess has its outer edge axially spaced from the edge of the sleeve or member 54 by a portion 66 of the internal surface 57 of the sleeve which defines what is termed as a sill area. Also, each of the outer recesses 58 is in communication with a pair of

inner recesses

62a and 62!) through openings 74 having orifices 76 therein.

The internal surface 57 of the bearing sleeve 54 has first and second diametrically opposed axially extending slots 68 and is divided into first and second portions 57a and 57h by cutout portion 70. Each of the

surfaces

57a and 57b define circular segments having radii of equal length. However, the centers of the respective

circular segments

57a and 57b are spaced from each other by a small dimension indicated by the reference numeral x" (FIG. 3), for a purpose which will be described later.

In the assembled condition, the bearing sleeves 54 are positioned within the opening 52 defined in the housing 12 so that the respective diametrically opposed slots 68 are located substantially in alignment with the respective passages or ports 36 and 38. This will locate the cutout portions 70 above and below the inlet and outlet ports and will provide a spacing between the bearing sleeves 54 and the bearing journal 26, for a purpose which will be described later. The

radial portions

57a and 57!; will, therefore, be located adjacent the respective ports 36 and 38.

Since the sleeves have a diameter slightly smaller than the diameter of the enlarged portion 52 of the bore 25, provision must be made for preventing rotation of the sleeves in the bore. The means for preventing rotation of the sleeves in the bore includes a screw 77 (FIG. 1) threaded into an opening 79 (FIG. 3) in the sleeve. The screws will prevent rotation of the sleeves but will accommodate radial movement of the sleeves relative to the bore and the shaft.

In the assembled condition, see FIG. 8, the grooves 60 receive O-rings 80 and anti-extrusion rings 82 with the O-rings 80 and the anti-extrusion rings 82 cooperating to seal the areas surrounding each of the outer recesses 58. Thus, each of the outer recesses 58 produces a sealed pocket or chamber between the wall of the bore or opening 52 in the housing 12 and the outer surface of the sleeve. Also, the internal surface 57 of the member 54 cooperates with the peripheral surface of the bearing journal 26 so that the recesses 62 define inner pockets or chambers, more specifically each of the

portions

62a and 62b, define pocket or chamber portions between the bearing journal 26 and the member 54.

As was indicated above, the respective pockets or chambers are adapted to receive pressurized fluid to produce forces on the shaft which counterbalance the reaction forces on the shaft resulting from the pressurized fluid in that area of working chamber 14 in communication with the outlet port of the pump. For this purpose, the pair of circumferentially spaced outer recesses or pockets 58, which are located adjacent the area of working chamber 14 in communication with the inlet port 36, are connected to the outlet port 38 through conduit means 86 (FIG. 2). Likewise, the remaining two circumferentially spaced outer pockets 58, which are located adjacent the area of working chamber 14 in communication with the outlet port 38, are connected through conduit means 88 to the inlet port 36 of the pump.

In this manner, the conduit means 86, as well as the pockets or chambers 58 and the openings, constitute means for supplying fluid from the outlet or second port 38 to the

inner pockets

62a and 62b to produce forces on the bearing journals 26 and thus the rotor 22, counterbalancing the reaction forces produced on the opposite side of the rotor 22 by the fluid at the elevated pressure in the area of working chamber 14 in communication with the port 38. Furthermore, the pressurized fluid at the inlet port is directed to the remainingpair of outer pockets for each of the bearing sleeves, which are located adjacent the outlet port 38 and produce a balancing force for any reaction forces resulting on the rotor from the fluid in the inlet port. With such an arrangement, the reaction forces in either of the ports are balanced by opposing forces on the bearing journals 26 regardless of the direction of flow of fluid through the pump or the pressure of the fluid in either of the ports.

Furthermore, the internal configuration of the sleeve 54 and the variation in diameters between the bore and the outer surface of the sleeve results in a self-centering of the sleeves between shaft 24, more particularly the bearing journals 26, and the bore 52. Since the circular segments of the internal surface 57 each have a radius substantially equal to one-half the diameter of the shaft, more particularly the bearing journal 26 forming part of the shaft 24, and the centers of the respective segments are spaced by the transverse dimension x, the bearing sleeve 54 is capable of being shifted transversely of the axis of the shaft as the forces resulting from the pressurized fluid reach an unbalanced state. The spacing x between the respective radii of the

portions

57a and 57b results in a small clearance between the internal surfaces of the sleeves and shaft which define flow paths from the

recess portions

62a and 62b across the sill areas while the sealing means 80, 82 prevent flow of fluid between the bore and the sleeve.

The configuration of the bearing sleeve is claimed in application Ser. No. 27,472, filed Apr. 13, 1970 now US. Pat. No. 3,671,155 and assigned to the assignee of this application.

As was stated above, the communication between each pair of inner recesses and its respective outer recess or pocket is restricted so that the pressure of the fluid in the outer pocket is always higher that the pressure of the fluid in the innerpockets. This is accomplished by the orifices 76 in the openings 74. When the sleeves are in a centered position, the flow of fluid into the inner recesses will be equal to the flow of fluid from the inner recesses, between the shaft and the sleeve.

Thus. assuming that there is an increase in the pressure of the fluid in the outer pockets resulting in an increase in the pressure of the fluid in the outlet port 38,

the size of the flow paths from the respective inner pockets formed by recess portions 620 and 62b adjacent the inlet port will decrease while the size of the flow paths from the pockets adjacent the outlet ports will increase. This will result in a decreased force between the shaft 24 and the sleeve adjacent the outlet port and an increased force between the shaft and the sleeve adjacent the inlet port. With such an unbalanced condition, the increased forces between the sleeve and the'shaft adjacent the inlet port will tend to move the sleeve towards the outlet port until a balanced condition is reached.

At the same time, the spacing between the sleeves and shaft adjacent the outlet port will be increased and the fluid will be flowing from the associated recesses more freely than thru the restrictions into the recesses so that the pressure of the fluid in these recesses may drop to near zero. The pressure ofthe fluid in the outer pocket adjacent the outlet port will assist in returning the sleeve to its centered position.

Another advantageous feature of the present invention is that the division of the pockets axially on the member will automatically maintain a true axial relationship between the sleeve 54 and the shaft 24. Thus, assuming for any reason, that the bearing sleeve 54 is tilted relative to the axis of the shaft 24, such a condition will cause an increase in the'size of the flow path from one of the inner pockets and a decrease in the size of the flow path of the adjacent inner pocket. Such a difference in the flow from the respective pockets will again cause a differential pressure in the respective adjacent pockets which will then tend to shift the sleeve relative to the bearing journal to ultimately result in axial alignment of the sleeve and shaft.

11he l9t s, described above, perform an important function in insuring that the inte rnal surfaee 57 of the bearing sleeve will not have a sufficient increase in temperature to result in distortion of the bearing which would result in ultimate failure of the entire pump. Assuming, for example, that one of the surfaces, surface 57a, were located in close proximity to the exterior surface of the shaft or bearing journal 26. Such a condition might result in a sufficient increase in temperature of the metal between the circumferentially spaced inner pockets 62 adjacent one of the ports to thereby result in an expansion of the metal of sufficient magnitude to produce a continuous surface-to-surface contact between the bearing sleeve and the bearing journal which would result in ultimate destruction of the shaft and/or the sleeve. However, by providing the axially extending slots 68 between each pair of internal pockets located on opposite side of he center of the pump, the slots 68 will allow expansion of the metal in this area without any distortion of the sleeve towards the bearing journal.

Another important feature of the bearing constructed in accordance with the present invention is that each portion of the bearing journal is assured of lubrication by the supporting fluid. This is accomplished by having the internal surface of the bearing, which devides the inner'recesses into sections 620 and 62b, comprised of segments axially offset from each other. Thus, the recess areas will have axially overlapping sections which permit the pressurized fluid contained therein to contact and'lubricate that portion of the bearing journal adjacent to the dividing sill. Pressure induced flow out of the recesses passing through the clearances will lubricate the bearing journals in the area of the outer sills.

A-further important feature of the present invention is the relative size of the outer and inner pockets as well as the location of the pockets with respect to the respective ports. It is preferable that the outer pockets have a projected area which is less than the projected area of the associated inner pockets and more specifically that the outer pocket projected area be slightly smaller than the projected area of the inner pockets as well as the sill areas on opposite ends of each of the pockets. Thisinsures that the force developed in the outer pocket will not overcome that in the inner pockets and consequently thrust the sleeve into direct contact with the bearing journal.

Furthermore, while not absolutely necessary to the practice of the present invention it is desirable to specifically locate the outer pockets relative to the path of flow of the fluid through the pump to insure that (l) the portions of bearing sleeves located above and below the path of flow through the pump will not be distorted towards each other; and (2) that the portion of the bearing sleevesadjacent the path of flow will not be distroted towards each other. If the pockets do not extend a required circumferential distance on opposite sides of the respective ports, the resultant forces from the fluid in the outer pockets willtend to move the opposed segments towards each other and ultimately result in metal-to-metal contact along the inner surface of the bearing sleeve and the outer surface of the bearing journal. Such a condition could cause a complete desctruction of the shaft and/or the bearing sleeve. Alternatively,.if thecircumferential extent of the outer pockets is too great, the forces resulting from the pressurized fluid above andbelow the path of flow through thepump will tend to distort the upper and lower portions of the bearing sleeve towards each other and again result in metal-to-metal contact. Thus, it is desirable that the respective pockets 58 terminate at a point which is spaced a predetermined circumferential distance from a plane extending vertically between the inlet and outlet ports. Such a spacing is preferably on the order of a 2025 arc between the vertical plane and the adjacent edge of the pocket.

The illustrative embodiment shows a pair of outer pockets on each side of the recessed portions 70 with each pair to be located adjacent the respective ports. This will result in a complete balance of the rotor within the working chamber. it is to be understood that the respective pairs of pockets could be replaced with single pockets covering substantially the same circumferential area without departing from the spirit of the invention. In addition the means for preventing rotation of the sleeves in the bore could be performed by the frictional engagement of the resilient sealing means 80, 82 rather than the separate screws.

What is claimed is: i 1. In combination with a housing having a circular wall defining an opening receiving a rotatable shaft, a

bearing interposed between said wall and shaft, said bearing comprising a sleeve having an outer surface and an inner surface, said sleeve having inner dimension greater than the diameter of said shaft and outer dimension less than the diameter of said opening to accommodate radial movement of said sleeve relative to said opening and shaft; means defining an outer pocket between said outer surface and said wall; sealing means between said outer surface and said wall and surrounding said outer pocket; means defining an inner pocket between said inner surface and said shaft; communication means between said outer pocket and said inner pocket; and means supplying pressurized fluid to said outer pocket, said pressurized fluid being received in said inner pocket through said communicating means to produce forces on said shaft to floatingly support said sleeve between said housing and said shaft.

2. The combination as defined in claim 1, in which said outer pocket has a projected area less than the projected area of said inner pocket.

3. The combination as defined in claim 1, in which said means defining said inner pocket includes axially spaced recesses spaced from each other and from opposite ends of said sleeve to define sill areas and in which said means defining said outer pocket includes a recess in said outer surface, said outer pocket having a projected area less than the sum of the projected areas of said inner pockets and saidsill areas.

4. The combination as defined in claim 1, the further improvement of additional bearings means supporting said rotatable shaft for rotation about a substantially fixed axis in said housing.

5. The combination as defined in claim 1, in which said communication means has orifice means therein to restrict the flow from the outer pocket to the inner pocket so that movement of the inner pocket away from said shaft will reduce the pressure of the fluid in the inner pocket while retaining the pressure of the fluid in the outer pocket.

6. The combination as defined in claim 1, and including means defining a second outer pocket between said wall and said outer surface; means defining a second inner pocket between said inner surface and said shaft, said second pockets being-substantially diametrically opposed to said first pockets, and communication means between said second outer and inner pockets.

7. In a fluid unit having a rotor supported in a working chamber of a housing by a shaft, said shaft having opposite ends received in a bore in said housing with the working chamber having-first and second ports, the improvement of first and second bearings comprising a sleeve cooperating with said shaft and said bore to define inner and outer pockets adjacent said first port, said sleeves each having an inner dimension greater than the diameter of said shaft and an outer dimension less than the diameter of said bore to accommodate radial movement relative to said shaft and said bore; sealing means between said bearings and said bore and surrounding said outer pockets; means preventing rotation of said sleeves in said bore; and means for supplying fluid from said second port to said pockets to floatingly support said sleeves between said shaft and said bore and counterbalance the reaction forces produced on said rotor by the fluid in said second port.

8. A fluid unit as defined in claim 7, in which said inner pockets are each divided into first and second axially spaced portions and said sleeves cooperate with 10 said shaft to produce flow paths from each of said portions to maintain said sleeves and shaft axially aligned with each other.

9. A fluid unit as defined in claim 7, in which said fluid is delivered to said outer pockets and said sleeves have restricted openings interconnecting each outer pocket with an inner pocket to deliver fluid thereto so that said sleeves are urged toward said shaft by said fluid in said outer pocket.

10. A fluid device as defined in claim 7, in which said sleeves cooperate with said shaft to define second inner and outer pockets adjacent said second port, the fur ther improvement of means connecting said first port to said second pockets.

11. A bearing comprising a member having an ,outer surface and an inner surface defining an opening; first means defining at least one recess on the outer surface; second means defining first and second recesses located at axially spaced locations parallel to the axis of said opening on said inner surface and in opposed relation to said outer recess; communication means between said inner recesses and said outer recess; said recesses adapted to cooperate with surfaces on a moving and a fixed element to produce chambers adapted to receive a pressurized fluid source whereby to produce reaction forces on the respective elements, said inner surface having a portion between said first and second inner recesses, said portion having circumferentially spaced segments axially spaced from each other to produce axially spaced portions at circumferentially spaced locations between the first and second recesses.

12. A bearing as defined in claim 11, in which said inner recesses are respectively spaced from opposed edges of said member to define sill areas and in which said outer recess has a projected area less than the projected area of said inner recesses and said sill areas.

13. A bearing as defined in claim 11, in which said member is a substantially circular sleeve and said first means defines four circumferentially spaced outer recesses; said second means defines four groups of first and second inner recesses respectively in opposed relation to one of said outer recesses with communication means between the respective inner recesses and the opposed adjacent outer recess, said outer recesses having a projected area less than the projected area of said inner recesses.

14. A bearing as defined in claim 13, including the through said device and including at least one member,

said at least one member having an internal surface cooperating with said shaft to define chamber means, each chamber means including wall means dividing the chamber means into axially spaced chambers, said wall means having axially and circumferentially spaced wall segments permitting fluid contact on said shaft the en tire distance between axially spaced ends of said chamber means during each revolution of rotation of said,

shaft; means defining outer pockets between said member and said housing, with said outer pockets being respectively in communication with the axially spaced portions of one of said chamber means, the projected 118532v area of each of said outer pockets being less than the UNITED STA'IES PA'IEN'I OFFICE CERTIFICATE OF CORRECTION Patent No. 3, 1 ,5 Dated June 4 1974 Inventofls) Birger F. Jansson and Albert A. Schmitz It is certified that error appears in the above-identified patent and that seid Letters Patent are hereby corrected as shown below:

IN THE'ABSTRACT:

Line 1, delete "a met-bod and".

Line 2, delete "rotating element" and substitute --rotor supporting shaft-.

Lines 4 thru 12, cancel "The method conteI nplates...' 4

forcesproduced on the rotor."

Lines 13 and 14, delete "for defining the chambers receiving the diverted fluid" Signed and sealed this 17th day of September 1974.,

(SEAL) Attest:

MCCOY; M. GIBSON JR. c; MARSHALL DANN Arresting Officer Commissioner of Patents .1 r. Fo H :0 \0 0 (\0 M) uscomwhc MI -PW I B U uwlluvlm "mum. mllrl IMI n- \u in

Claims

1. In combination with a housing having a circular wall defining an opening receiving a rotatable shaft, a bearing interposed between said wall and shaft, said bearing comprising a sleeve having an outer surface and an inner surface, said sleeve having inner dimension greater than the diameter of said shaft and outer dimension less than the diameter of said opening to accommodate radial movement of said sleeve relative to said opening and shaft; means defining an outer pocket between said outer surface and said wall; sealing means between said outer surface and said wall and surrounding said outer pocket; means defining an inner pocket between said inner surface and said shaft; communication means between said outer pocket and said inner pocket; and means supplying pressurized fluid to said outer pocket, said pressurized fluid Being received in said inner pocket through said communicating means to produce forces on said shaft to floatingly support said sleeve between said housing and said shaft.

3. The combination as defined in claim 1, in which said means defining said inner pocket includes axially spaced recesses spaced from each other and from opposite ends of said sleeve to define sill areas and in which said means defining said outer pocket includes a recess in said outer surface, said outer pocket having a projected area less than the sum of the projected areas of said inner pockets and said sill areas.

6. The combination as defined in claim 1, and including means defining a second outer pocket between said wall and said outer surface; means defining a second inner pocket between said inner surface and said shaft, said second pockets being substantially diametrically opposed to said first pockets, and communication means between said second outer and inner pockets.

7. In a fluid unit having a rotor supported in a working chamber of a housing by a shaft, said shaft having opposite ends received in a bore in said housing with the working chamber having first and second ports, the improvement of first and second bearings comprising a sleeve cooperating with said shaft and said bore to define inner and outer pockets adjacent said first port, said sleeves each having an inner dimension greater than the diameter of said shaft and an outer dimension less than the diameter of said bore to accommodate radial movement relative to said shaft and said bore; sealing means between said bearings and said bore and surrounding said outer pockets; means preventing rotation of said sleeves in said bore; and means for supplying fluid from said second port to said pockets to floatingly support said sleeves between said shaft and said bore and counterbalance the reaction forces produced on said rotor by the fluid in said second port.

8. A fluid unit as defined in claim 7, in which said inner pockets are each divided into first and second axially spaced portions and said sleeves cooperate with said shaft to produce flow paths from each of said portions to maintain said sleeves and shaft axially aligned with each other.

10. A fluid device as defined in claim 7, in which said sleeves cooperate with said shaft to define second inner and outer pockets adjacent said second port, the further improvement of means connecting said first port to said second pockets.

11. A bearing comprising a member having an outer surface and an inner surface defining an opening; first means defining at least one recess on the outer surface; second means defining first and second recesses located at axially spaced locations parallel to the axis of said opening on said inner surface and in opposed relation to said outer recess; communication means between said inner recesses and said outer recess; said recesses adapted to cooperate with surfaces on a moving and a fixed element to produce chambers adapted to receive a pressurized fluid sourcE whereby to produce reaction forces on the respective elements, said inner surface having a portion between said first and second inner recesses, said portion having circumferentially spaced segments axially spaced from each other to produce axially spaced portions at circumferentially spaced locations between the first and second recesses.

14. A bearing as defined in claim 13, including the further improvement of means defining at least one axial slot in said inner surface, said slot being disposed between adjacent groups of recesses and extending between opposite edges of said sleeve.

15. In combination with a fluid translator unit having a rotor assembly including a shaft and a housing with primary bearing means supporting said rotor assembly for rotation about a fixed axis in said housing to translate fluid between spaced ports, secondary bearing means for counterbalancing reaction forces on said rotor assembly from the pressure of fluid translated through said device and including at least one member, said at least one member having an internal surface cooperating with said shaft to define chamber means, each chamber means including wall means dividing the chamber means into axially spaced chambers, said wall means having axially and circumferentially spaced wall segments permitting fluid contact on said shaft the entire distance between axially spaced ends of said chamber means during each revolution of rotation of said shaft; means defining outer pockets between said member and said housing, with said outer pockets being respectively in communication with the axially spaced portions of one of said chamber means, the projected area of each of said outer pockets being less than the projected area of the respective chambers associated therewith; and means for supplying pressurized fluid to said pockets whereby the flow into said chambers and from said chambers between said shaft and internal surface.