Abstract:
A hydrodynamic bearing is incorporated within an alternator electrical generating system and or electric motors having permanent magnet (PM) machine rotors wherein a fluid film bearing is integrated between the rotor assembly outer diameter and the electrical stator assembly inner diameter. The alternator rotor outside diameter is a bearing surface and a static sleeve bearing is positioned inboard of the electrical stator inner diameter, coaxially and central, wherein the static sleeve inner diameter is a bearing surface. An additional select material is incorporated to sleeve bearing inner diameter surface to prevent relative surface damage during none fluid film operating conditions. 
     A gas pressurized system, incorporated as the fluid means yields improved bearing life, reduced machine axial rotor system length and reduced costs in high speed alternators and or motors applications such as in turbomachinery, alternators for generating electricity, Microturbines, hybrid gas turbine engines removing the need for external bearings.

Description:
[0001]    This application claims benefit of the provisional application Ser. No. 61/963,745 filed Dec. 12, 2013. 
     
    
     BACKGROUND OF THE INVENTION 
       [0002]    1. Field of the Invention 
         [0003]    The present invention relates generally to hydrodynamic bearings and more specifically it relates to an alternator rotor integrated bearing for turbomachinery, alternators and or electric motors having permanent magnet machine rotors wherein a hydrodynamic bearing system is incorporated between alternator rotor magnet retention sleeve outer surface and the stator inboard area. 
         [0004]    2. Description of the Prior Art 
         [0005]    It can be appreciated that hydrodynamic bearings have been in use for years. Typically, hydrodynamic bearings can be found in microturbines with high speed alternators (electrical generators) having permanent magnets, turbo alternators, turbo charges with integrated alternators and electric motors as used in machinery and or turbomachinery. 
         [0006]    A problem with conventional hydrodynamic bearings used in current turbo machinery, machinery using electric motors and or alternators having rotor permanent magnets, are external bearings (located outboard of the alternator rotor/stator) such as foil compliant air bearings, magnetic bearings, journal bearings, ball bearings or roller bearings add complexity, increase alternator or motor system size with elevated cost. Another problem with conventional hydrostatic bearings such as ball bearings and or roller bearings they have limited life and therefore related turbomachinery require maintenance intervals for replacement. Foil compliant air bearings (hydrodynamic type bearing) require increased compressor rotor and turbine rotor shroud tip clearances for operation resulting in reduced rotor compressor and turbine rotor component efficiencies. Magnetic bearings require electrical power to operate, yield large turbomachinery rotor radial clearances and are costly; the loss of electrical power could damage related turbomachinery and alternator/stator components. Another problem with conventional hydrodynamic bearings, all external bearings used in alternator rotor applications, if a bearing failure occurs both the alternator rotor and stator become damaged; and furthermore external bearings used to date have rotational shaft power losses due to roller element drag forces and or shaft fluid shear drag forces. This new device, an integrated bearing within an alternator rotor/stator allow for better control of stack-up clearances in turbomachinery applications. 
         [0007]    While these devices may be suitable for the particular purpose to which they address, they are not as suitable for turbomachinery and alternators or electric motors having permanent magnet alternator rotors wherein a hydrodynamic bearing system is incorporated between alternator rotor magnet retention sleeve outer surface and the alternator stator inboard area offers longer bearing life and reduced system cost. 
         [0008]    In these respects, the alternator rotor hydrodynamic bearing according to the present invention substantially departs from the conventional concepts and designs of the prior art, and in so doing provides an apparatus primarily developed for the purpose of turbomachinery and alternators or electric motors having permanent magnet alternator rotors wherein a hydrodynamic bearing system is incorporated between alternator rotor magnet retention sleeve outer surface and the alternator stator inboard area. 
       SUMMARY OF THE INVENTION 
       [0009]    In view of the foregoing disadvantages inherent in the known types of hydrodynamic bearing now present in the prior art, the present invention provides a new alternator rotor hydrodynamic bearing construction wherein the same can be utilized for turbomachinery and alternators or electric motors having permanent magnet alternator rotors wherein a hydrodynamic bearing system is incorporated between alternator rotor magnet retention sleeve outer surface and the alternator stator inboard area. 
         [0010]    The alternator or motor systems incorporate an internal fluid film bearing with pressurized fluid flow as an improvement over the prior art current external bearings to yield longer bearing life, reduced bearing shaft power loss, and reduced rotor blade tip clearances (for an integrated turbine or compressor rotor) improving turbomachinery component efficiencies. 
         [0011]    Permanent magnet (PM) alternator electric motors and electric generators have been used in industry, ground vehicles, aircraft auxiliary electrical power generation, turbomachinery, Microturbines, turbo pumps and turbo alternators for a number of years. Typically the alternator rotor having retained permanent magnet, involves high rotational speeds wherein the magnets are retained by an alternator rotor sleeve incorporating material selection of high strength and without effect to stator stacked laminats inner diameter formed tooth geometry flux generation with the alternator rotating magnets during operation. 
         [0012]    The general purpose of the present invention, which will be described subsequently in greater detail, is to provide a new alternator rotor hydrodynamic bearing that has many of the advantages of the hydrodynamic bearing mentioned heretofore and many novel features that result in a new alternator rotor hydrodynamic bearing which is not anticipated, rendered obvious, suggested, or even implied by any of the prior art hydrodynamic, fluid film bearing, either alone or in any combination thereof. 
         [0013]    To attain this, the present invention generally comprises: a Stator Sleeve Bearing, an Alternator Rotor Assembly, an Alternator Rotor Retainer, an Alternator Stator Assembly and an Alternator Housing. The Stator Sleeve Bearing is an insertable component within a Alternator Stator Assembly having static bearing surfaces for axial and radial alternator rotor loads with material and radial space considerations. The Alternator Rotor Assembly has a core, at least one extending shaft, permanent magnets and a alternator rotor sleeve to retain the permanent magnets wherein the alternator rotor sleeve outer diameter are bearing surfaces. The Alternator Stator Assembly incorporates stacked laminats with inner diameter tooth configured forms, has wound electrical wire about and thru the laminats external wire leads and coaxially receives the alternator rotor therein. The Alternator Housing contains the alternator stator assembly, the alternator rotor assembly, with hydrodynamic bearings therein for axial and radial alternator rotor forces and stator wire power leads exit the alternator housing. The Rotor Retainer is an end cap connected to the alternator housing, has a static fluid bearing surface, interface retains the alternator rotor assembly, the alternator stator assembly and stator sleeve bearing. 
         [0014]    There has thus been outlined, rather broadly, the more important features of the invention in order that the detailed description thereof may be better understood and in order that the present contribution to the art may be better appreciated. There are additional features of the invention that will be described hereinafter. 
         [0015]    In this respect, before explaining at least one embodiment of the invention in detail, it is to be understood that the invention is not limited in its application to the details of construction and to the arrangements of the components set forth in the following description or illustrated in the drawings. The invention is capable of other embodiments and of being practiced and carried out in various ways. Also, it is to be understood that the phraseology and terminology employed herein are for the purpose of the description and should not be regarded as limiting. 
         [0016]    A primary object of the present invention is to provide a permanent magnet alternator rotor hydrostatic or hydrodynamic bearing (fluid film bearing) that will overcome the shortcomings of the prior art devices. As a hydrostatic bearing means external pressurized fluid flow is supplied for a radial central position of the alternator rotor to the stator inner diameter in preparation for rotational operation the latter of which becomes the hydrodynamic bearing application. 
         [0017]    An object of the present invention is to provide an alternator rotor hydrostatic or hydrodynamic bearing for turbomachinery and alternators or electric motors having permanent magnet alternator rotors wherein a fluid film bearing system is incorporated between alternator rotor magnet retention sleeve outer surface and the alternator stator inboard area. The alternator rotor assembly integrates with compressor rotor and or turbine rotor. 
         [0018]    Another object is to provide an alternator rotor fluid film bearing that incorporate hydrodynamic bearings for alternator rotor application offering minimum or greatly reduced horsepower losses as experienced in current conventional rotor shaft bearings. 
         [0019]    Another object is to provide an alternator rotor fluid film bearing that is located central to the alternator stator wherein the journal sleeve material selection has no magnet flux interferences between the alternator rotor and stator without compromise to the electrical power generation and considers optimized radial gap between the stator inside diameter and the rotor magnet/sleeve outside diameter. 
         [0020]    Another object is to provide an alternator rotor fluid film bearing that is incorporated within the alternator stator that offers increased bearing life and removes the need for any alternator rotor external bearings. 
         [0021]    Another object is to provide an alternator rotor fluid film bearing that Incorporates a rub tolerant sleeve bearing material that resists wear during emergencies shut downs and possible start-ups periods without fluid flow to the rotor shaft bearing system alternator rotor magnet retention sleeve outside diameter and alternator stator sleeve bearing inside diameter. 
         [0022]    Another object is to provide an alternator rotor fluid film bearing that incorporates rub tolerant stator sleeve bearing material of a hydrodynamic bearing within the alternator stator inside diameter to prevent the alternator rotor sleeve outside diameter from contacting the stator inside diameter during external bearing failure such as power loss to a magnetic bearing system. 
         [0023]    Another object is to provide an alternator rotor fluid film bearing that incorporates a compliant foil bearing within the alternator stator between the stator and permanent magnet alternator rotor as an axially compact bearing means and if required external thrust bearings. 
         [0024]    Another object is to provide an alternator rotor fluid film bearing with a central pressurized fluid supply, channeled to the bearing wherein the discharging fluids prevent related caustic operating atmosphere fluids from contaminating the alternator rotor and or stator assemblies. 
         [0025]    Another object is to provide a hydrodynamic bearing co-axial to the alternator stator that allows improved component assembly stack up tolerance improved compressor and turbine rotor to shroud reduced clearance higher performance efficiencies. 
         [0026]    Other objects and advantages of the present invention will become obvious to the reader and it is intended that these objects and advantages are within the scope of the present invention. 
         [0027]    To the accomplishment of the above and related objects, this invention may be embodied in the form illustrated in the accompanying drawings, attention being called to the fact, however, that the drawings are illustrative only, and that changes may be made in the specific construction illustrated. 
     
    
     
       BRIEF DESCRIPTIONS OF THE DRAWINGS 
         [0028]    Various other object, features and attendant advantages of the present invention will become full appreciated as the same becomes better understood when considered in conjunction with the accompanying drawings, in which like references and characters designate the same or similar parts throughout the several view, wherein: 
           [0029]      FIG. 1 , is a ¼ cross sectional view an alternator generator/motor system having one alternator stator assembly with integral fluid film sleeve and thrust bearings. 
           [0030]      FIG. 2 , is a ¼ cross sectional view of an alternator generator/motor system having two stator assemblies with integral fluid film sleeve and thrust bearings. 
           [0031]      FIG. 3 , is a ¼ cross sectional view of the alternator generator/motor system having one stator assembly with integral fluid film sleeve bearing. 
           [0032]      FIG. 4 , is a ¼ cross sectional view of the alternator generator/motor system having two stator assemblies with integral fluid sleeve bearing. 
       
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENT 
       [0033]    Turning now descriptively to the drawings, in which similar reference characters denote similar elements throughout the several view, the attached figures illustrate a alternator rotor with a hydrodynamic bearing, which comprises a Sleeve Bearing, a Alternator Rotor Assembly, an Alternator Rotor Retainer, an Alternator Stator Assembly and an Alternator Housing.  FIG. 1  is the preferred embodiment. 
         [0034]    The alternator rotor assembly having permanent magnets incorporates a retention sleeve wherein the outer diameter is a bearing surfaces and if required axial thrust bearing are included for a journal type bearing fluid film bearing. This new bearing invention alternator/motor system incorporates an internal fluid film bearing (pressurized gas) as an improvement over the prior art current external bearings, yielding longer bearing life, simplicity, reduced rotor blade tip clearances for an integrated turbine or compressor rotor, reduced bearing power losses, improved turbomachinery component efficiencies thru reduced blade tip to shroud clearances and improved stack-up assembly clearance calculations. 
         [0035]    The invention relates to an alternator for generating electricity or an electric rotor to drive turbomachinery or machinery having permanent magnet retained within the alternator rotor assembly and a fluid film bearing is integrated therein. Considering the preferred embodiment as  FIG. 1  the alternator bearing assembly has a static stator sleeve  72  and a rotational bearing (alternator magnet retention means) component the alternator rotor sleeve bearing  71  of alternator rotor assembly  20 , is coaxially positioned within the alternator stator assembly  30 . The stator sleeve bearing  71  having a material of nonmagnetic quality (example Inconel) and of a longitudinal length thru the stator assembly  30  inner diameter is retained to the alternator housing  10  thru a flange  47  sandwiched between the end cap  23  and the alternator housing  10  outer surface receiving area  48  end of the alternator housing  10  front area proximal end with a retention ring  49  or bolt arrangement; and the distal stator sleeve end is insertable into the aft alternator housing area  41  of alternator housing  10 . The inner diameter of the stator sleeve bearing is a bearing surface, has an insertable carbon material  74  or composite material etc. capable of accepting rotor rotational surface forces without damage to alternator rotor sleeve bearing  71  outer surface. The radial thickness of the alternator sleeve bearing sleeve adds to the radial distance between the magnet and the laminat inner diameter tooth form but needs to be minimized in view of magnet  53  strength and subsequent electrical power generation thru the electrical wire  16  from the relative rotation of the alternator rotor assembly  20  magnet  28  past the laminat  31  inner surface tooth forms. Centrally located are radial fluid transfer holes  21  that allow fluid flow  11  from cavities  12 ,  37  and  17  to transition into the sleeve bearing annular cavity  24  and then downstream thru annular flow bearing surfaces forward flow  51 A and aft flow  51 B cavities formed between the alternator rotor sleeve bearing outer diameter and the inner diameter of the stator sleeve bearing  72  protective surface  74 ,  57 . The inner diameter of the sleeve bearing  72  or outer diameter of  71  could have integrated surface geometries for bearing tribology considerations—fluid film design requirements. A forward cavity  85  accepts the thrust bearing radial component  55  of the alternator rotor sleeve bearing  71  along with bearing fluid supply from  51 A to the thrust bearing  32 ,  67  and  33 , 72  fluid flow design requirements with inward discharge fluid flow  27 . The alternator rotor assembly  20  has a rotational centerline  25 , a core  56  of iron material or equivalent, permanent magnets  83 , a rotor magnet retention means alternator sleeve bearing  71  and a minimum of one rotor shaft  44  extending. The shaft end is used as an output motor drive means or as an alternator to generate electricity from an external input rotational load. The alternator rotor assembly  20 , load could be thru an integrated turbomachinery compressor rotor or turbine rotor. The alternator magnet retention sleeve bearing  71  outer diameter area as a fluid film bearing is a PM alternator rotor bearing surface with a central bearing fluid supply annular cavity  24  that receives fluid from the outboard stator sleeve fluid supply channels  21 . A forward located radial component  55  of the stator sleeve bearing  72  accept rotor thrust loads thru surfaces  33 ,  68  and  32 ,  67  aft and forward loads respectively. Forward and aft axial bearing fluid flow channels  51 A and  51 B are formed between the stator sleeve bearing  72  inner diameter and alternator sleeve bearing  71  outer diameter with exiting fluid flow  43 A and  43 B the latter discharging the thrust bearing area after passing thru cavity  85  and thrust rotor bearing channeled fluid flow surfaces  67  and  68 . Bearing fluid supply can also be thru channels  26  retention cap  23 . 
         [0036]    The Stator Sleeve Bearing is part of the hydrodynamic fluid bearing system a static bearing member located inboard of the alternator stator assembly having fluid film interface with the alternator rotor sleeve bearing surface outside diameter of the alternator rotor assembly  20 . The stator sleeve bearing  72  is of high strength material with nonmagnetic quality (example Inconel) with a longitudinal length thru the stator assembly  30  inner diameter and is retained to the alternator housing  10  thru a flange  47  sandwiched between the end cap  23  and the alternator housing  10  outer receiving area  48  end proximal end with a retention ring  49  or bolt arrangement; and the distal stator sleeve bearing end is insertable into the aft alternator housing area  41  of alternator housing  10 . The inner diameter of the stator sleeve bearing is a bearing surface, with an insertable carbon material  74  or composite material etc. capable of accepting rotor rotational surface forces without damage to alternator rotor sleeve bearing  71  surface. The radial thickness of the alternator sleeve bearing sleeve adds to the radial distance between the magnet and the laminat inner diameter tooth form but is minimized via the small bearing design clearances, not to compromise the magnetic flux and subsequent electrical power generation. As an option the radial component  47  of the stator sleeve bearing  72  could be resilient mounted along with the aft sleeve insertion  41 / 42  into the housing  10  for alternator rotor damper considerations. 
         [0037]    The Alternator Stator Assembly, retained in the alternator housing  10 , incorporates stacked laminats with inner diameter tooth configured forms, has wound electrical wire about and thru the laminats, external wire leads and coaxially receives the alternator rotor assembly. The outer diameter of the laminat stack is close fitted to the alternator housing such as to remove electrical power generated heat from the laminat stack. An alternator sleeve bearing is positioned to the stator assembly inner diameter that in operation receives an alternator rotor assembly in close proximity and coaxial to the stator inner diameter, wherein relative rotation—alternator magnets to alternator stator inner diameter tooth forms, generate a magnetic flux yielding electricity within the wires in a alternator generation mode. Stator lead wires are thru the stator housing via insulted power lugs then to outboard power electronics to change the high voltage high frequency power to useful electricity. An external bearing fluid supply passes fluid thru the alternator stator inwardly with additional cooling stator means, then to the alternator rotor sleeve bearing surfaces. The main cooling means for the stator is thru the outer diameter close fit to the alternator housing which as a stator assembly is installed into the alternator housing. Additional cooling is thru fluid supply passing inwardly thru the stator assembly in transit to the alternator rotor journal bearing supply. 
         [0038]    The Alternator Stator Assembly  30  is insertable to the Alternator Housing and consists of a laminat stack of iron stamped sheet forms  31  having inner diameter tooth forms, wound electrical wire  16  thru the stator laminats, end turns  17  and  39 , output leads  16  and output lead terminal  84  with insulated power terminal lugs  46  and retention nuts  84 A. The distal end of the stator generally has no output lead just wound wire ends  39  whereas the proximal end has output lead  16  lead wires. The alternator housing  10 , supplies fluid flow to the stator assembly, has an axially central bearing fluid flow supply  11  typically gaseous supplied thru the alternator housing  10  outer surface supply tube  29  with fluid passage into an annular manifold  12  then radially inward to a annular channel  36  wherein radial channels  37  within the stator assembly  30  transfer the pressurized gas (fluid) flow  11  to an inner stator annular cavity  18  then again thru the stator sleeve radial channels  21  to the alternator magnet retention/alternator rotor sleeve bearing  71  alternator rotor annular supply  24  for the bearing operation. A stator sleeve bearing  72  in close proximity of the stator assembly has a retention flange  47  retain at the alternator housing  10  proximal end  48  and an aft retention means  41 ,  42  wherein the end cap  23  the end cap  23  captures the radial bearing sleeve component  55  with forward  67  and aft  68  thrust face bearing interacts with the static bearing surfaces  32 ,  33 . The alternator rotor sleeve bearing  71  thrust bearing radial component  55  with surfaces  67  and  68  could be incorporated to the alternator core  83  forward or aft of the stator or combination thereof. 
         [0039]    Depending on the thrust load requirement of the alternator rotor the thrust bearing radial form  55  of the alternator sleeve could be removed leaving a straight alternator rotor sleeve bearing  71  with no thrust bearing surfaces  67  and  68  and or the forward and aft cavities of the alternator could contain a pressure to act on the faces  14 ,  13  and possible lab seal to the alternator rotor assembly  20  could be incorporated. The rotor retainer or end cap  23  has a bearing fluid drain  27  and a radial surface that is the static bearing surface of the rotation thrust bearing surface  67 / 68  axially holds the position of the alternator rotor assembly  20 . 
         [0040]    In  FIG. 1 , axially centrally located are radial fluid transfer holes  21  that allow fluid flow  11  from cavities  12 ,  37  and  17  to transition into the sleeve bearing annular cavity  24  and then downstream thru annular flow bearing surfaces forward flow  51 A and aft flow  51 B cavities formed between the alternator rotor sleeve bearing outer diameter and the inner diameter of the stator sleeve bearing  72  protective surface  74 ,  57 . The inner diameter of the sleeve bearing  72  or outer diameter of alternator rotor sleeve bearing  71  could have integrated surface configurations for bearing tribology—fluid film design requirements. A forward cavity  85  receives the thrust bearing radial component  55  of the alternator rotor sleeve bearing  71  along with bearing fluid supply from  51 A for the thrust bearing  32 ,  67  and  33 , 72  fluid flow design requirements with discharge fluid flow  27 . Supplemental supply fluid flow could be thru channel  26 . Also, the radial thrust bearing surfaces  67 ,  68  radial component  55  could be integrated to the alternator rotor core  83  for ease of alternator rotor sleeve bearing manufacture consideration, reference  FIG. 3 . 
         [0041]    The Alternator Rotor Assembly  20  has a rotational centerline  25 , a core  56  of iron material or equivalent, permanent magnets  83 , a rotor magnet retention means—alternator sleeve bearing  71  and a minimum of one rotor shaft  44  compressor or turbine rotor drive means. The shaft end is used as an output motor drive means or as an alternator to generate electricity from an external input rotational load. The alternator rotor assembly  20 , power load could be thru an integrated turbomachinery compressor rotor or turbine rotor. The alternator magnet retention sleeve bearing  71  outer diameter area as a fluid film bearing is a PM alternator rotor bearing surface with a central bearing fluid supply annular cavity  24  that receives fluid from the outboard stator sleeve fluid supply channels  21 . A forward located radial component  55  of the stator sleeve bearing  72  accept rotor thrust loads thru surfaces  33 ,  68  and  32 ,  67  aft and forward loads respectively. Forward and aft axial bearing fluid flow channels  51 A and  51 B are formed between the stator sleeve bearing  72  inner diameter and alternator sleeve bearing  71  outer diameter with exiting fluid flow  43 A and  43 B the latter discharging the thrust bearing area after passing thru cavity  85  and thrust rotor bearing channeled fluid flow thru thrust bearing surfaces  67  and  68 . 
         [0042]    The Alternator Rotor Assembly  20  has permanent magnets  28 , an alternator rotor magnet retention sleeve wherein the outer diameter of the magnet retention sleeve becomes a bearing (fluid film bearing) surface, the alternator rotor sleeve bearing  71 ,  53 . An axial thrust bearing means radial component  55  of  71  alternator rotor sleeve bearing of  FIG. 1  also could be integrated to the alternator rotor core  56 ,  83  reference FIG.  3 ,  4  to allow ease of simple alternator rotor sleeve bearing manufacture  53 A and  71 A. 
         [0043]    The Alternator Housing  10  with an end cap alternator retainer, retains the alternator stator assembly and the alternator rotor assembly with fluid film bearings therein for axial and radial alternator rotor forces. The alternator housing contains the alternator stator assembly provisions for exiting electrical output wire leads, alternator rotor assembly and stator sleeve bearing retention either ridged mounted or damper mounted to the housing structure. 
         [0044]    The alternator housing has a bearing fluid supply channels initiating from the housing outer areas. Also the bearing fluid supply could be from an inboard source interconnecting to the alternator rotor assembly shaft. A rotor fluid pump could be integrated to the alternator rotor as bearing fluid supply means. The alternator housing could receive two stator assemblies to allow use of thrust bearing means located between the stator ends. (Reference  FIG. 2, 4 ) 
         [0045]    The Alternator Rotor Retainer is an end cap, attaches to the alternator housing, axially retains/positions the alternator rotor within the stator sleeve bearing and stator assembly and has a thrust bearing surface. The end cap is a means to axially retain the alternator rotor within the alternator housing thru a thrust bearing having that has forward and aft static surfaces about the alternator rotor sleeve bearing radial component as thrust bearing radial surfaces, forward and aft captured between the stator sleeve bearing radial component and the housing end cap. There are bearing fluid supply channels about the thrust bearing for fluid supply and discharge requirements. 
         [0046]    The end cap  23  has a static thrust bearing surface  32  and axially retains/positions the alternator rotor sleeve bearing  71  radial component  55  with thrust bearing face surfaces  67 ,  68 . The thrust bearing fluid supply comes from channel  51 A into cavity  85  with discharge flow  26  and  27  the latter from channeled surfaces across the thrust bearing surface  32 ,  67 . 
       Description of Alternative Embodiments 
       [0047]    Fluid flow to the bearings, reference  FIG. 2 , could be thru a center hole  75  of  FIG. 2  radially thru and into the alternator rotor sleeve and stator sleeve assembly to annular channel  24 . As yet another configuration, reference  FIG. 2 , two coaxial alternator stator assemblies  50  could be in place of one stator assembly of  FIG. 1  with a thrust bearing location axially central to the alternator rotor sleeve bearing and positioned between the stator assembly ends. 
         [0048]      FIG. 2 , two stator assemblies  50  are incorporated wherein the magnet retention/alternator rotor sleeve  53  has a radial component  54  (could be integral to the alternator rotor core  56 ) with forward and aft thrust bearing surfaces  67  and  68  respectively. Bearing supply fluid  76  is thru the center  44  of the alternator rotor core  56  having radial channels  78  and annular fluid feed channel  24  with radial holes  69  thru the alternator rotor radial component supplying bearing fluid to an outboard cavity  64  and subsequent pressurized fluid distribution to the thrust bearing surfaces  67 ,  68  and the alternator stator sleeve to rotor sleeve annular cavities  51 A,  51 B bearing requirements with exiting fluid flow  82 A and  82 B. The alternator stator assembly  50  incorporate an outer cooling sleeve  59  with channeled fluid flow  61  between the alternator housing  63  inner diameter and cooling sleeve  59  outer diameter to remove the laminat electrical power heat generation wherein fluid supply  38  cooling flow  65  removes the stator heat; also as a supplemental fluid flow to cavity  64  for bearing surfaces fluid flow requirements consideration. Radial surfaces  59 B of the cooling sleeve  59 A interconnect with the stator sleeve bearing  58 A and  58 B as supports and thrust bearing surface means whereas the axial ends interface with the alternator housing  10  either is a hard mount or damper resilient design scheme wherein the stator sleeve bearing is spaced from the stator inner area. The outboard cooling stator sleeve axial ends of  59 B and  59 A interface with the housing either as a ridged or damper/resilient design scheme. 
         [0049]    In  FIG. 2,4  the alternator housing incorporates two stator assemblies  30  with cooling sleeve  59 A as  50  assembly yields a thrust bearing, alternator rotor position means located between the stator ends as in  FIG. 2, 4 . 
         [0050]    As another means to axially retain the alternator rotor, the rotor magnet strength interaction—close proximity to the alternator stator iron laminat in itself maintains the axial position of a low thrust load operation or non operation, thus removes the need for a retainer cap/thrust bearing component. As a further thrust bearing means  FIG. 1, 3 , the alternator surface ends  13 ,  14  with or without lab seals applied to the alternator rotor assembly core  83 , accepts fluid pressure forces therein act solely on the alternator assembly rotor ends for alternator rotor axial positioning. 
         [0051]    Also as another means of the alternator rotor thrust control a drive shaft coupling could be incorporated to drive an external compressor rotor or turbine rotor wherein the drive shaft interconnects to the alternator rotor assembly as an external thrust load control. 
         [0052]    Yet another means (reference  FIG. 2, 4 ) to retain the alternator rotor is to have a alternator housing  10  retain two axially stacked stator assemblies  50  with radial component  59 A,  59 A having surfaces  32 ,  33  interact with surfaces  67 ,  68  of the alternator rotor sleeve bearing radial component  54 . The alternator rotor assembly  20 , sleeve bearing  71  radial component  55  of  FIG. 1  could be integral to the core  83  as shown in  FIG. 3 . 
         [0053]    The Alternator Housing  10  of  FIG. 1 , retains the alternator rotor assembly  20  and stator assembly  30  of which create heat during electrical power generation or motor mode wherein a heat removing means is incorporated thru the housing. Stator power leads pass thru the alternator housing, a stator sleeve bearing coaxially within the stator inner diameter, bearing fluid supply channels thru the housing, an alternator rotor having, permanent magnets retained by a alternator sleeve bearing and positioned coaxially, axially central to the stator with a fluid film bearing within and having a minimum of one output/input power shaft extending from the alternator rotor assembly thru alternator housing. A thrust bearing is incorporated into the alternator rotor assembly  20  thru a radial surface component  55 , located at one end and is retained by a housing end cap  23 . Considering a two alternator stator scheme ( FIG. 2, 4 ) incorporated into the housing, the thrust bearing rotating radial component  54  surfaces  67 ,  68  of the alternator rotor sleeve bearing  53  are sandwiched between the stator ends having interaction with the stator assembly cooling sleeve  59 , end  59 A surfaces  32 ,  33 . The stator assemblies  50  incorporate cooling sleeves  59  outer surface heat exchangers having radial inwardly extending structure with surfaces  32 ,  33  that interact with the alternator rotor sleeve bearing  67 ,  68  as a thrust bearing means. Bearing fluid supply is from the outer surface of the housing, flow channel  64  cavity between the stator ends  52 A wherein the sleeve bearing surfaces receives annular fluid flow  51 A,  51 B via fluid flow channeled thru the thrust bearing. 
         [0054]    As another bearing fluid supply  76 , from the cap  23  end, fluid flows thru the alternator rotor center diameter  75 , core  56 , inner diameter wherein fluid passes thru the alternator rotor centrally then thru radial channels  79 , annulus  24  and channels  69  and into cavity  65  with subsequent bearing fluid flow and cooling fluid flow  61  of the cooling sleeve  59 . The stator sleeve bearing can be retained to the housing at either end or thru the stator laminat stack  30 . Also alternator rotor dampers could be incorporated via resilient stator sleeve support outside of the stator or thru the stator laminat  31  stack. 
         [0055]    As another version of this fluid film bearing application within a PM alternator generator system or motor system, the thrust bearings are removed, relying on the magnet strength interaction with the stator laminat stack for the alternator rotor axial positioning within the stator/housing assembly. 
         [0056]    Another means of retaining the stator sleeve bearing is to retain the stator sleeve bearing to the housing aft end internally stationary cantilevered from the aft end extending forward such to allow the stator to be insert over the stator sleeve bearing. 
         [0057]    As an additional alternative, the alternator stator assembly  30  consists of: a laminat stack of iron stamped sheet forms  31  with inner diameter tooth forms, wound electrical wire  16 , external output leads  84  and output lead terminals  46  with retention nuts  84 A. The distal end of the stator has no output lead just wound wire  39  whereas the proximal end has output lead  16  inner connected to output terminals  46 . The alternator housing  10  as a body has a external bearing fluid  11  typically gaseous form with flow supplied thru the outer surface port  29  and fluid passage into an annular supply manifold  12  then radially inward to a annular channel  12  and radial channels  37 , within the stator assembly  30  for fluid transfer thru the pressurized gas (working fluid) to an inner stator annular cavity  18  then again thru the stator sleeve radial channels  21  to the alternator rotor sleeve bearing  71  annular dispersion cavity  24  for the fluid film bearing operation flow cavities  51 B and  51 A. There are forward flange  47  sleeve retention to housing  10  and an aft means support  42  of the stator sleeve bearing  72  retention means  41  to the housing; the end cap  23  captures the stator sleeve bearing  72  static radial component  47  with a forward  32 ,  67  and aft  33 ,  68  thrust bearing means. Also as another scheme the alternator magnet retention sleeve thrust bearing radial component  55  could be incorporated and forward or aft of the stator or combination thereof. 
         [0058]    The thrust bearing could be integrated to the alternator core  83  as noted in  FIG. 3  allowing simplicity in the manufacturing the alternator rotor sleeve bearing  71  as a straight cylindrical sleeve form  71 A. Depending on the thrust load requirement of the alternator rotor the radial components of the alternator sleeve could be removed leaving a straight cylinder form rotor sleeve bearing with no thrust bearing and or the forward cavity and aft cavities of the alternator could contain a pressure to act on the faces surface areas  13 ,  14  and possible lab seal to the alternator rotor could be used as a fluid sealing means. The rotor retainer or end cap  23  has a radial surface  32  that is the static bearing surface of the thrust bearing surface  67  and in combination with  68 ,  33  radial surfaces axially holds the position of the alternator rotor assembly  20 . The stator assembly  30  is insertable into the housing  10  wherein the stator sleeve bearing  72  positioned within the stator assembly  30  is retained to the alternator housing  10  via radial flange  47  and retaining ring  49  or equivalent. Stator lead wire  16  with insulated lugs  46  is secured to the cap  23  and carries the output electrical power from generated electrical power or input power from an outside source to drive the alternator rotor assembly  20  as a motor. The radial component of the stator sleeve could be resilient mounted along with the aft sleeve insertion  42  into the housing for alternator rotor damper considerations. As an alternative alternator configuration in  FIG. 2  two stator assemblies  30  with cooling sleeves  59  as a further assembly  50  is incorporated wherein the alternator magnet retention sleeve becomes alternator rotor sleeve bearing  53  wherein the radial component  54  incorporates forward and aft thrust bearing surfaces  32 ,  67  and  33 ,  68  static and rotatable respectively. Bearing supply fluid  76  is thru the center  25 , hole  75  of the alternator rotor core  56  with intersecting continued fluid flow radial channels  78  and annular fluid channel  24  and radial holes  69  thru the alternator rotor assembly  20  rotor sleeve bearing  53  radial component  54  yielding bearing fluid to an outboard cavity  64  and subsequent fluid distribution to the thrust bearing surfaces  32 ,  67  and  33 ,  68  and the annular alternator rotor/stator sleeve bearing cavity thru fluid flow  51 A,  51 B requirements with exiting flow  82 A and  82 B. The stator assemblies  50  incorporate an outboard cooling sleeves  59  to remove the laminat electrical heat generation wherein fluid from cavity  38  supplies cooling channel  61  flow with exiting flow  62  to remove the generated stator heat. Supplemental fluid flow  38  of cavity  65  to cavity  64  for bearing and cooling requirements could be incorporated. Radial structures  59 A of the cooling sleeve interconnects with the stator sleeve bearing as supports and thrust bearing surface means. Outboard inner stator sleeve bearing ends  58 B and  58 A interface with the housing  10 . As yet another configuration,  FIG. 4  the thrust bearing rotor radial component  54 , surface  67 ,  68  can be integrated to the alternator rotor core  56  allowing a simple cylinder form to retain magnet  28 , retention sleeve means the alternator rotor sleeve bearing  53 A for ease of manufacture. The alternator rotor assembly  20  having permanent magnets  28  has an alternator rotor magnet retention sleeve wherein the outer diameter of retention sleeve becomes a bearing (fluid film bearing) surface, the alternator rotor sleeve bearing  71 ,  53 . An axial thrust bearing means is integrated/incorporated to this fluid film bearing or integrated to the alternator rotor core  56 ,  83  reference  FIG. 2, 4 . 
         [0059]      FIG. 1  exhibits a thrust bearing incorporated with the alternator rotor sleeve bearing  71  as a radial surface component  55 , located at one end and is retained by a housing end cap  23  with bearing surfaces therein. 
         [0060]      FIG. 2  represents a scheme having two alternator stator assemblies  50  within the alternator housing  10  wherein the thrust bearing radial component  54 , rotating radial forward and aft surfaces of the alternator rotor sleeve bearing are sandwiched between the alternator stator assembly ends. The thrust bearing radial component  54  could be integrated to the alternator rotor core  56  as noted in  FIG. 4 . The alternator stator assemblies incorporate outer surface cooling sleeves  59  with radial inboard extending structure  59 A having  32 ,  33  surface that interact with the radial component  54  surfaces  67 ,  68  as a thrust bearing means.  FIG. 2, 4  bearing fluid supply  11  with tube  29 , thru the channel  38  and  64  then past  67 ,  68  thrust bearing radial surface flow with continued flow thru the stator sleeve bearings fluid channels  51 A,  51 B an annulus between the alternator rotor sleeve bearing  53  outer diameter surfaces and the stator sleeve bearing  58 A,  58 B inner diameter fluid discharging at  82 A and  82 B. 
         [0061]    In  FIG. 2 , as another bearing fluid supply means, fluid supply  76  is delivered to and thru the alternator rotor center  75  hole, end intersecting radial flow channels  79  flowing outwardly,  69  into flow annulus  64 , for bearing fluid flow dispersion and cooling therein. The stator sleeve bearing (a static detail) can be retained to the housing at either end or thru the stator laminat stack. Also alternator rotor dampers could be incorporated via resilient stator sleeve support outside of the stator or thru the stator laminats. The radial thrust bearing component  54  could be integrated to the alternator rotor core  56  as noted in  FIG. 4 .  FIG. 2  represents a scheme having two alternator stator assemblies  50  within the alternator housing  10  wherein the thrust bearing radial component  54 , rotating radial forward and aft surfaces of the alternator rotor sleeve bearing are sandwiched between the alternator stator assembly ends. The thrust bearing radial component  54  could be integrated to the alternator rotor core  56  as noted in  FIG. 4 . The alternator stator assemblies incorporate outer surface cooling sleeves  59  with radial inboard extending structure  59 A having  32 ,  33  surface that interact with the radial component  54  surfaces  67 ,  68  as a thrust bearing means.  FIG. 2, 4  bearing fluid supply with tube  29 , thru the channel  38  and  64  then past  67 ,  68  thrust bearing radial surface flow with continued flow thru the stator sleeve bearings fluid channels  51 A,  51 B an annulus between the alternator rotor sleeve bearing  53  outer diameter surfaces and the stator sleeve bearing  58 A,  58 B inner diameter fluid discharging at  82 A and  82 B. 
         [0062]    In  FIG. 2 , as another bearing fluid supply means, fluid supply  76  is delivered to and thru the alternator rotor center  75  hole, end intersecting radial flow channels  79  flowing outwardly,  69  into flow annulus  64 , for bearing fluid flow dispersion and cooling therein. The stator sleeve bearing (a static detail) can be retained to the housing at either end or thru the stator laminat stack. Also alternator rotor dampers could be incorporated via resilient stator sleeve support outside of the stator or thru the stator laminats. As a note the radial thrust bearing component  54  could be integrated to the alternator rotor core  56  as noted in  FIG. 4 . 
         [0063]    As to further discussion of the manner of usage and operation of the present invention, the same should be apparent from the above description. Accordingly, no further discussion relating the manner of usage and operation will be provided. 
         [0064]    With respect to the above description then, it is to be realized that the optimum dimensional relationships fort the parts of the invention, to include variations is size, materials, shape, form, function and manner of operation, assembly and use, are deemed readily apparent and obvious it one skilled in the art, and all equivalent relationships to the those illustrated in the drawings and described in the specification are intended to be encompassed by the present invention. 
         [0065]    Therefore, the foregoing is considered as illustrative only of the principles of the invention. Further, since numerous modifications and changes will readily occur to those skilled o in the art, it is not desired to limit the invention to the exact construction and operation shown and described, and accordingly all suitable modifications and equivalents may be resort to, falling within the scope of the invention.