Abstract:
A compressor assembly includes a housing and a compressor mechanism is disposed therein which is partially supported by a manifold. The manifold extends across the interior of the housing, has an aperture therethrough, and subdivides the interior of the housing into a first discharge chamber and a second discharge chamber. An electric motor is disposed in the second discharge chamber and includes a stator and a rotor. A shaft operatively couples the compressor mechanism with the rotor. The manifold includes an aperture into which is received a discharge gas into the first discharge chamber and a plurality of chutes to direct the discharge gas into the second discharge chamber. The chutes are in fluid communication with an exterior of the compressor mechanism defining passages therebetween. The housing includes a main section and an end section which respectively include edges. A bearing support member extends across an interior of the housing and is supported between the edges of the main and end sections of the housing. The bearing support member has portions which project radially outward. An auxiliary bearing is supported by the bearing support member and the auxiliary bearing rotatably supports the shaft. A method of assembly includes: attaching the compressor mechanism to the manifold and welding the manifold to the housing; attaching the stator to the housing and the auxiliary bearing to the bearing support member; aligning the main bearing with the stator and welding the bearing support member to the housing.

Description:
BACKGROUND OF THE INVENTION 
     The present invention relates generally to hermetic compressors for use in cooling, refrigeration or air-conditioning systems, and more particularly to hermetic scroll compressors. 
     Well known to those having skill in the art are hermetic scroll compressors such as compressor  10  of FIG. 1, having a closed hermetic housing  12  comprised of cylindrical section  14  with end cap  16  welded at the upper end thereof and base  18  at the lower end thereof. Base  18  includes a plurality of mounting feet  20 . Compressor  10  has electric motor  22 , which comprises stator  24  fixed inside cylindrical section  14  by, for example, shrink-fitting. Surrounded by stator  24  is rotor  26 , which is attached to shaft  28  by, for example, press-fit. Counterweight  27  is attached to an upper end of shaft  28  and counterweight  31  is attached to rotor  26 , as is customary, to provide substantially balanced rotation of shaft  28 . Shaft  28  is coupled to orbiting scroll  30  through eccentric  29 . Shaft  28  is supported, at opposing ends thereof, by bushing  32  and auxiliary bearing  34 . Bushing  32  is fixed within main bearing  48  by, for example, press-fit. Main bearing  48  and auxiliary bearing  34  are rigidly affixed to an internal surface  33  of cylindrical section  14  of housing  12  typically by press-fit or spot weld methods. Generally, auxiliary bearing  34  includes a plurality of outwardly extended legs  36  secured to internal surface  33  of cylindrical section  14 . 
     Those having skill in the art of compressor construction readily appreciate that spot welding, although a preferable manufacturing process to attach the bearings to the housing, may cause heat generated distortion which can lead to misalignment of stator-rotor air gap  38 . To facilitate this process, radially directed holes  40  are provided in an end portion of each leg  36  to accommodate a steel pin  42  in each hole. This process further requires each pin  42  to be aligned with each corresponding hole  44  provided in a lower part of cylindrical section  14 . Finally, each pin  42  is spot welded to cylindrical housing section  14  at hole  44 . 
     Turning now to the construction of the scroll compressor mechanism  57 , in the upper part of housing  12 , is non-orbiting scroll member  46  axially fixed to main bearing  48  by a plurality of bolts  50  in such a manner that orbiting wrap  52 , integral with orbiting scroll member  30 , and non-orbiting wrap  54 , integral with non-orbiting scroll member  46 , combine to form compression cavities or chambers  56 . Orbiting scroll member  30 , non-orbiting scroll member  46  and main bearing  48  comprise compressor mechanism  57  which is positioned in an upper part of cylindrical housing section  14 . A typical procedure associated with assembly of compressor  10  includes request for concentricity of inner radial surface  59  of stator  24  respective of inner radial surface  61  of main bearing  48 . Annular bushing  32  attached to main bearing  48 , by typical means such as press-fit, is substantially concentric with main bearing  48 . Main bearing  48  and bushing  32  must also properly align shaft  28  to provide suitable clearance between orbiting and non-orbiting wraps  52  and  54 , respectively, so proper compression in compression chambers  56  may be attained. After alignment is achieved, main bearing  48  and/or non-orbiting scroll member  46  is welded to housing  12 . 
     Discharge gas compressed by compressor mechanism  57  flows through discharge port  64  provided with check valve  62 , and into first discharge chamber  66 . First discharge chamber  66  is defined in part by a volume formed between planar surface  68  of non-orbiting scroll  46  and end cap  16 . Thereafter, the discharge gas flows from first discharge chamber  66  to second discharge chamber  70  and exits through discharge tube  72 . Discharge chamber  70  is defined by axial surface  78  of compressor mechanism  57 , internal surface  33  of a portion of housing  14 , generally below compressor mechanism  57 , and external surface  55  of the compressor motor  22 . Discharge chambers  66  and  70  are in fluid communication through narrow (e.g., 0.035″-0.040″wide) passage  74  formed by internal surface  33  of cylindrical section  14  and peripheral surface  69  of compressor mechanism  57 . Discharge tube  72  extends through the wall of cylindrical section  14  of housing  12  and into chamber  70  to transfer refrigerant gas away from compressor assembly  10 . 
     A problem associated with scroll compressors heretofore, is one of excessive noise caused by refrigerant gas turbulently flowing over the compressor mechanism prior to being discharged from the compressor housing. Compressed refrigerant gas exiting discharge port  64  enters first discharge chamber  66 , and is thereafter forced over peripheral surface  69  of compressor mechanism  57  and into second discharge chamber  70 . Narrow passage  74 , disposed between first discharge chamber  66  and second discharge chamber  70 , is substantially flow-restrictive and consists of a thin ring or annular shaped passage between cylindrical section  14  of housing  12  and compressor mechanism  57 . An outer profile of compressor mechanism  57 , exposed to the refrigerant gas flowing thereover, is generally cylindrical, and includes a pair of axially opposed and generally planar surfaces  76 ,  78 , respectively, which are connected by cylindrical surface  80 . The transition of discharge gas flow from axial planar surfaces  76 ,  78 , respectively to cylindrical surface  80  generally includes moderately sharp edges which generate turbulence when refrigerant gas flows over compressor mechanism  57 . An increase in noise is attributable to an increase in energy of the gas as gas molecules transition from a substantially ordered state to a substantially unorganized and chaotic state. The noise is transmitted through housing  12  of compressor assembly  10  and into the surrounding area. 
     Another problem associated with compressor assembly  10  arises during operation wherein localized heating occurs between the rotating rotor  26  and the stationary stator  24 . Region  25 , positioned extending radially through outer peripheral margins of rotor  26  and inner peripheral margins of stator  24 , becomes heated which detrimentally affects motor efficiency. 
     Yet another problem associated with scroll compressors heretofore, is the costly and laborious procedure of aligning the main bearing, auxiliary bearing and stator within the housing to preserve proper scroll wrap and shaft bearing clearances; typically the clearances required are a few ten thousandths of an inch. This procedure is often referred to as “mounting” the compressor. 
     Mounting of scroll compressors typically requires the diameter of the cylindrical part of the housing to be machined to provide a reference location to concentrically align the main bearing with the auxiliary bearing and to eliminate uneven stator-rotor gap during assembly. Aligning each bearing relative to the housing requires the bearing support structures to include an outer diameter smaller than that of the inner diameter of the cylindrical section of the housing so that a gap is formed between the structure and the inner surface of the housing. The gap must be uniform and somewhat small to facilitate favorable conditions for alignment and spot welding. Further, as mentioned above, typical scroll compressor design mandates precise radial placement of each bearing, thus, a typical scroll compressor exhibits a supporting bearing structure larger than necessary and/or a plurality of special arms attached to the bearing support to allow for radial adjustability. Unfortunately, these design requirements add to the weight of the compressor, complicate assembly and further add to machining time, which in turn, increases the per unit cost to the manufacturer. 
     Once the bearings and scroll are suitably aligned, the problem of weldability between metals of dissimilar thicknesses and materials must be addressed. For example, welding the relatively thin compressor housing material to the thick bearing support structures often leads to improper joining and/or distortion. Further, often the bearing structures are steel castings, as is the compressor mechanism, while the housing may be formed from cold rolled steel. Those having skill in the art of welding will appreciate that joining by welding depends upon many correlating factors, such as the shape and size of the weld area, material preheat conditions and the speed at which the joined components heat and cool. Distortion of components leads to a complete loss of all materials and labor to that point, often referred to as “scrap”, and may be caused by excessive stresses in joined components due to unequal cooling or heating during the welding process. Such undesirable distortion not only resides at the weld location, it also migrates throughout the compressor affecting, for example, precision tolerances such as the bearing gaps, wrap clearances, and the stator-rotor gap. 
     Therefore, a compressor design which preserves the dimensional tolerances necessary for proper operation of the scroll compressor, which are extremely close, generally on the order of a few ten thousandths of an inch, is highly desirable. Additionally, a design which addresses the difficulties associated with unwanted distortion and stressing of the main bearing, bearing structure, compression mechanism and auxiliary bearing caused by press-fit, shrink-fit and welding is most desirable. 
     Further, an invention which addresses operational noise, due to discharge gas turbulence internal to the housing, by decreasing the noise without adding significant complexity and cost to the compressor assembly, is highly desirable. 
     SUMMARY OF THE INVENTION 
     The present invention overcomes the disadvantages associated with prior compressor assemblies in that it provides a compressor assembly including a housing and a manifold which extends across an interior of the housing subdividing the housing into first and second discharge chambers. The first and second discharge chambers are in fluid communication through the manifold. A compressor mechanism is disposed in the housing and into which a fluid is received substantially at suction pressure and from which the fluid is discharged into the first discharge chamber substantially at discharge pressure. The compressor mechanism is attached to the manifold, whereby the compression mechanism is at least partially supported within the housing. An electric motor including a stator and a rotor is disposed in the second discharge chamber and a shaft operatively couples the rotor with the compressor mechanism. 
     The present invention further provides a compressor assembly including a housing and a compressor mechanism drivingly coupled to an electric motor by means of a shaft. The compressor mechanism and motor are disposed within the housing and the compressor mechanism receives a fluid substantially at suction pressure. A manifold is attached to the housing and subdivides an interior of the housing into first and second discharge chambers. The manifold has an aperture into which is received a discharge gas discharged from the compressor mechanism and the manifold includes a plurality of chutes which receive the discharge gas from the first discharge chamber and thereafter direct the discharge gas into the second discharge chamber. 
     The present invention further provides a compressor assembly including a housing having a main section and an end section. The main and end sections of the housing include edges. A bearing support member extends across an interior of the housing, is supported between the edges of the main and end sections of the housing and includes portions projecting radially outward to support the compressor assembly. A compressor mechanism is disposed in the housing and includes means for compressing the fluid from substantially suction pressure to substantially discharge pressure. An electric motor including a stator and a rotor are disposed in the housing. A shaft extends through the rotor and operatively couples the rotor and the compressor mechanism. An auxiliary bearing is disposed about the shaft and supported by the bearing support member. The shaft is rotatably supported by the auxiliary bearing. 
     The present invention further provides a method of assembling a scroll compressor including the steps of: assembling a main bearing, an orbiting scroll and a non-orbiting scroll to form a compressor mechanism; providing a manifold having a planar surface disposed thereon; fastening the compressor mechanism to the planar surface of the manifold to provide perpendicularity of the planar surface respective of a longitudinal axis through a centerline of the main bearing; providing a main section of the housing having first and second planar edges respectively disposed on axial ends thereof such that corresponding surfaces of first and second planar edges are substantially perpendicular to the longitudinal reference axis passing through the centerline of the housing; attaching a stator to the main section of the housing and aligning the stator therewith such that a centerline of an inner radial surface thereof is substantially aligned with the longitudinal centerline of the main section of the housing; inserting the compressor mechanism into the main section such that the planar surface of the manifold faces the stator and abuts the first planar edge of the main section of the housing; aligning the main bearing with the stator such that a centerline of an inner radial surface of the main bearing is aligned with the centerline of the inner radial surface of the stator; joining the planar surface of the manifold to the first planar edge of the main section; providing a bearing support member having a planar surface disposed thereon; fastening the auxiliary bearing to the bearing support member such that a centerline of an inner radial surface of the auxiliary bearing is substantially perpendicular respective of the planar surface of the bearing support member; providing a rotor coupled to a shaft and disposed within the main section of housing such that the longitudinal axis of the shaft and rotor are substantially coaxially positioned respective of the stator; connecting the auxiliary bearing on an end of the shaft; aligning the rotor within the stator such that the rotor and stator are separated by a substantially uniform and annular gap; joining the planar surface of the bearing support member to the second planar edge of the main section of the housing; and joining a pair of end sections to the housing such that one of the pair of end sections is joined to the housing proximate the first planar edge and the other end section is joined to the second planar edge of the main section of the housing. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The above-mentioned and other features and advantages of this invention, and the manner of attaining them, will become more apparent and the invention itself will be better understood by reference to the following description of an embodiment of the invention taken in conjunction wit the accompanying drawings, wherein: 
     FIG. 1 is a longitudinal sectional view of a prior art compressor assembly; 
     FIG. 2 is a longitudinal sectional view of the compressor assembly according to the present invention; 
     FIG. 3 is a longitudinal sectional view of the compressor assembly of FIG. 2 sectioned through a centerline of the manifold chutes; 
     FIG. 4A is a top view of the manifold; 
     FIG. 4B is a sectional view along line  4 B— 4 B of FIG. 4A; 
     FIG. 4C is a sectional view along line  4 C— 4 C of FIG. 4A; 
     FIG. 5 is a perspective view of the manifold; 
     FIG. 6A is a top view of a fixed scroll; 
     FIG. 6B is a sectional view along line  6 B— 6 B of FIG. 6A; 
     FIG. 7 is an enlarged fragmentary view of the compressor assembly shown in FIG. 3, showing the scroll compressor mechanism and the manifold; 
     FIG. 8 is a fragmentary perspective view of the compressor assembly shown in FIG. 7 with a portion thereof broken away; 
     FIG. 9A is a transverse view of the bearing support member; 
     FIG. 9B is a sectional view along line  9 B— 9 B of FIG. 9A; and 
     FIG. 9C is a sectional view along line  9 C— 9 C of FIG.  9 A. 
     Corresponding reference characters indicate corresponding parts throughout the several views. Although the drawings represent an embodiment of the present invention, the drawings are not necessarily to scale and certain features may be exaggerated in order to better illustrate and explain the present invention. The exemplification set out herein illustrates an embodiment of the invention in one form thereof, and such exemplification is not to be construed as limiting the scope of the invention in any manner. 
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     The present invention overcomes the disadvantages of the above described prior art scroll compressors by providing an improved compressor mounting arrangement requiring fewer components, resulting in less manufacturing time and less assembly required which corresponds to a substantial cost savings. The present invention also provides both a quieter and cooler operating compressor. 
     Referring to FIGS. 2 and 3, compressor assembly  82  of the present invention is shown, and in contrast to the prior art compressor shown in FIG. 1, discloses a noise attenuating manifold and a bearing support structure which are illustrated respectively by manifold  84  and bearing support member  86 . Compressor assembly  82  includes closed hermetic housing  88  comprised of main section  90  welded to manifold  84  and having first end section  92  enclosing an upper portion of compressor housing  88  by being welded thereto. In a lower portion of housing  88  is bearing support member  86 , which is generally disc-shaped and welded to a lower portion of main section  90  of housing  88  to support auxiliary bearing  94  fastened thereto. Second end section  96  of housing  88 , equal in size to the first end section  92 , is welded to bearing support member  86  to hermetically enclose housing  88  and provide an oil sump  97 . Lower portion  95  of auxiliary bearing  94  extends through bearing support member  86  and into sump  97 . Oil pump  103 , disposed within lower portion  95  of auxiliary bearing  94 , forces oil, pooled within sump  97 , through shaft  106  to lubricate compressor mechanism  120  in a well known manner. Formed as a unitary piece is bearing support member  86  including a projecting outer periphery portion comprising a plurality of mounting feet  98  to support compressor assembly  82  (FIGS. 2,  3  and  9 B). Hermetic housing  88  is subdivided into two distinct portions by bearing support member  86 . First housing portion  99  is disposed above bearing support member  86  and includes motor  100  and compressor mechanism  120  provided therein. Second housing portion  101  is disposed below bearing support member  86  and includes feet  98  of bearing support member  86 . Second end section  96  of housing  88  is joined to bearing support member  86  by, for example, welding to form sump  97  which is located generally above second housing portion  101  and below bearing support member  86 . 
     Within main section  90  of housing  88  is electric motor  100  which comprises stator  102  connected to main section  90  by, for example, shrink-fit. Rotor  104  is attached to shaft  106  by press-fit or other like connecting method. At an upper end of compressor assembly  82 , shaft  106  drives orbiting scroll  108  through eccentric  109  as is customary. Shaft  106  is supported by main bearing  112 , through bushing  110 . Counterweight  105  is attached to an upper end of shaft  106  and counterweight  107  is attached to rotor  104 , as is customary, to provide substantially balanced rotation of shaft  106 . Rotation of shaft  106  is transformed into non-rotating translation of orbiting scroll  108  through known means such as an Oldham coupling. At a lower end of compressor assembly  82 , below motor  100 , shaft  106  is supported by outboard or auxiliary bearing  94 . Annular bushing  110  is connected by press fit with inner radial surface  111  of main bearing  112  to support shaft  106 . Non-orbiting scroll  118  is secured between main bearing  112  and manifold  84  by screws  114  (FIG.  2 ). Auxiliary bearing  94  is fastened to bearing support member  86  by screws  116 . Non-orbiting scroll  118 , orbiting scroll  108  and main bearing  112  form compressor mechanism  120 . 
     Referring to FIGS. 2,  3  and  7 , in operation, electric motor  100  drives compressor mechanism  120  to compress refrigerant gas, introduced into inlet port  122  (FIG. 8) at suction pressure, within compression chamber  124 . Compression chamber  124  is defined by a plurality of compression cavities  126  positioned between non-orbiting involute wrap element  128  and orbiting involute wrap element  130 . Thus, orbiting involute wrap element  130 , driven by motor  100 , orbits about non-orbiting involute wrap element  128  to compress refrigerant gas therebetween. 
     Compressed refrigerant gas, at its final compressed state (substantially at discharge pressure), exits compressor cavities  126  through discharge port  132  (FIGS. 2,  3 ,  6 A,  6 B,  7  and  8 ) then flows into first discharge chamber  134  through check valve  136 . Check valve  136  prevents compressed refrigerant from reversing or flowing back into port  132  from first discharge chamber  134  to help prevent reverse orbiting of the orbiting scroll. Refrigerant gas flows from first discharge chamber  134  to second discharge chamber  138  through four radial projecting semi-circular chutes  146  disposed within manifold  84 . Four jets of discharge gas, in fluid communication with chutes  146 , are directed through passages  158  (FIGS.  7  and  8 ). Notably, and as best seen in FIGS. 7 and 8, annular gap  140 , a thin ring defined by an interior wall of housing  88  and the exterior peripheral surface of compressor mechanism  120 , is otherwise flow restrictive when refrigerant gas is discharged from first discharge chamber  134  to second discharge chamber  138 , however, compressor mechanism  120  includes channels  162  to accommodate increased flow. Compressor assembly  82  includes four channels  162 , formed in surface  151  of non-orbiting scroll  118  in compressor mechanism  120 , positioned adjacent annular gap  140  (FIG.  2 ). Channels  162  decrease the axial length of annular gap  140 , along the exterior of compressor mechanism  120  which increases the flow of discharge gas otherwise restricted by substantially cylindrical compressor mechanism  120 . 
     Referring to FIGS. 2 and 3, compressor assembly  82  includes discharge manifold  84  attached to compressor mechanism  120  and welded to main section  90  of housing  88 . Main bearing  112  includes bushing  110  fitted therein to receive rotating drive shaft  106  and main bearing  112  is attached by way of screws  114  (FIG. 7) to non-orbiting scroll  118 . Nonorbiting scroll  118  includes discharge port  132  (FIGS. 6A and 6B) therein to provide an exit for compressed refrigerant gas to exit compressor mechanism  120 . Refrigerant gas, contained within first discharge chamber  134 , is transferred to second discharge chamber  138  by flowing over an exterior of compressor mechanism  120 . Typical compressor mechanisms are “cylinder-shaped” (FIG. 1) and in contrast, compressor mechanism  120  includes four equidistantly arranged channels  162  forming generally round-edged axial cross-section  121  (FIG.  3 ). The channels  162  are positioned adjacent the four discharge chutes  146  disposed on manifold  84 , to promote an increased boundary layer of refrigerant gas flow between each channel  162  and respective chute  146 . The refrigerant gas then flows into second discharge chamber  138  and exits housing  88  through discharge pipe  142  (FIGS.  2  and  3 ). 
     Referring to FIGS. 4A-4C and  5 , manifold or muffler plate  84  may be integrally formed by, for example, cold forming a steel plate through a stamping process, to form an annular, one piece unit which serves as a muffler to attenuate noise created by discharge gas. Additionally, manifold  84  serves as a structure to support the compressor mechanism. Manifold  84  is generally a disc shaped member having a generally circular base portion  144 . Manifold  84  includes four semi-circular chutes  146 , extending radially and arranged symmetrically about, and equidistantly from, the center of base portion  144 . However, it is envisioned that an asymmetrical arrangement of chutes  146  would also provide suitable noise attenuation. Non-orbiting scroll  118  is secured to manifold  84  by screws  114  which extend through holes  148  in manifold  84  and thread into non-orbiting scroll  118  (FIGS. 2,  3  and  7 ). 
     Referring to FIGS. 2,  7  and  8 , which best show the manifold&#39;s attachment to housing  88 , manifold  84  includes base  144  having machined surface  150 , defining a reference surface which is substantially perpendicular to a centerline of radial inner surface  149  of bushing  110 , which is substantially concentric with a radial inner surface of main bearing  112 . Surface  150  is adapted to abuttingly contact correspondingly machined annular top edge  152  of housing  88 . Surface  150  also defines a plane which is substantially perpendicular to a centerline axis of inner radial surface  154  of stator  102  within main section  90  of housing  88  (FIGS.  2  and  3 ). Surface  150  of manifold  84  is welded to annular top edge  152  of housing  88 . Stator  102  is fixed to housing  88  by way of, for example, shrink-fitting. Holes  156  (FIGS. 4A-4C and  5 ) in manifold  84  provide oil passages between first discharge chamber  134  and sump  97  to allow oil accumulated in first discharge chamber  134  to be reclaimed by oil sump  97  (FIGS.  2  and  3 ). 
     Referring to FIGS. 6A,  6 B,  7  and  8 , further describing the operation of manifold  84  and compressor mechanism  57 , compressed refrigerant gas is discharged from discharge port  132  and into first discharge chamber  134  through check valve  136  (not shown in FIG.  8 ). The gas then flows through a first portion of four passages  158  (FIGS.  7  and  8 ), each formed by inner wall surface  160  of each chute  146  and respective surface  164  of each channel  162  within non-orbiting scroll  118  (FIGS. 6A,  6 B and  7 ). Surface  164  of each channel  162  follows a generally semi-circular exterior profile of non-orbiting scroll  118  and provides a generally smooth and unobtrusive path for the refrigerant gas to flow from first discharge chamber  134  to a second portion of passages  158 . A second portion of passages  158  abut channels  162  in non-orbiting scroll  118  and are formed in main bearing  112 . Four equidistantly arranged channels  168  having respective surfaces  166  are disposed within exterior surface portions of main bearing  112 . Each channel  168 , provided in main bearing  112 , abuts channel  162 , in non-orbiting scroll  118 , such that channel  162  continuously extends into channel  168 . Refrigerant gas is directed from first discharge chamber  134  to second discharge chamber  138  through passages  158  by remaining attached, as a gas layer having a boundary, to channels  162 ,  168 , and inner wall surfaces  160  of chutes  146 . This attachment of gas, known to those having skill in the art as a “Coanda effect”, involves attachment of high velocity fluid to a surface. As best seen in FIGS. 3 and 7, passages  158  are continuous along exterior portions of the generally oval cross-section of compressor mechanism  120  (FIG.  3 ). Further, the refrigerant gas remains attached, under a Coanda effect from surface  164  of fixed scroll  118  to surface  166  of main bearing  112  and is thereafter directed to electric motor  100 . Flow of refrigerant gas directed to motor  100  decreases heat generated in windings and increases performance of the compressor assembly  82 . 
     Referring to FIGS. 3,  7  and  8 , noise attenuation, associated with fluid flow through compressor assembly  82 , is achieved by the discharge gas being directed through multiple passages  158 . A single jet of discharge gas, exiting discharge port  132  of non-orbiting scroll  118 , has associated therewith a particular energy level, a portion of which manifests itself in the form of audible noise. This energy level, and associated noise, may be reduced by segmenting and segregating the single jet into multiple smaller jets which imparts a significant energy loss on the aggregate discharge flow. Additionally, discharge flow noise may be further decreased by directing discharge gas flow over generally curved and gradually sloped walls defining arcuate passages, e.g., the inner wall surfaces  160  of chutes  146  and surfaces  164 ,  166  of respective channels  162 ,  168  defining flow passages  158 , to prolong the boundary layer attachment of discharge gas flow to aforesaid surfaces. Increasing boundary layer attachment acts to further diminish the noise associated with flow turbulence. 
     Compressor assembly  82  includes motor  100  comprised of rotational rotor  104  and stationary stator  102  separated by rotor-stator air gap  186 . Heat generated from friction and current flow through motor windings adversely affects motor performance. The generated heat is reduced by utilizing the Coanda effect, i.e., discharge gas attached to surface  166  of compressor mechanism  120  disattaches and is directed toward motor  100  to cool the motor windings. This cooling effect increases motor efficiency and increases performance of the compressor. 
     Turning now to the mounting structure of the present invention, as best seen in FIGS. 2 and 3, compressor assembly  82  includes auxiliary bearing  94  mounted in a lower part of housing  88 . Auxiliary bearing  94  is fastened to bearing support member  86  and bearing support member  86  is attached to housing  88 . Bearing support member  86  has a plurality of mounting feet  98  integrally formed by, for example, a cold forming process such as stamping, which support compressor assembly  82  in a generally upright or vertical position. As best seen with reference to FIGS. 3 and 9A, bearing support member  86  has clearance hole  174  to accommodate a lower portion  176  of auxiliary bearing  94 . Four holes  178  in bearing support member  86  align with corresponding threaded holes  180  in bearing  94  to receive screws  116  therein to fasten auxiliary bearing  94  to bearing support member  86 . Auxiliary bearing  94  has a plurality of arcuate apertures  184  which are aligned with the rotor-stator air gap  186  of motor  100  to provide adjustability of gap  186  through clearance hole  174  in bearing support member  86  following assembly of compressor mechanism  120  with main section  90  of housing  88  (FIGS.  2  and  3 ). A portion of oil transferred with the discharge gas, otherwise accumulating on bearing support member  86 , is transferred to sump  97  through apertures  188  in bearing support member  86  (FIGS. 2,  3  and  9 A). Also, oil dispersed within refrigerant gas, which may accumulate within rotor-stator air gap  186 , is reclaimed by oil sump  97  through arcuate apertures  184  in auxiliary bearing  94 . 
     Referring to FIGS.  3  and  9 A- 9 C, bearing support member  86  includes surface  192  which has peripheral shoulder portion  194  adapted to abut edge surface  196  of main section  90  of housing  88 . Edge surface  196  is machined and abuts shoulder portion  194  of surface  192  of bearing support member  86  such that edge surface  196  is substantially perpendicular to a centerline axis of inner radial surface  154  of stator  102  (FIGS.  2  and  3 ). 
     Referring to FIG. 3, a method of assembly of compressor assembly  82  which minimizes distortion of the main bearing, auxiliary bearing and scroll wraps, during heating and cooling processes associated with welding will be discussed. The process of assembly of compressor assembly  82  includes the steps of: assembling main bearing  112  (after press fit of bushing  110  therein), orbiting scroll  108  and non-orbiting scroll  118  to form compressor mechanism  120 ; machining planar surface  150  of manifold  84  to establish perpendicularity of a reference plane disposed on surface  150  to an axial centerline of main bearing  112  whereby planar surface  150  is used as the reference for locating rotor  104  vertically; fastening manifold  84  to top portion  151  of compressor mechanism  120 ; machining end surfaces  152 ,  196  respectively of main section  90  of housing  88  to provide substantially parallel surfaces with respect to each other and substantially perpendicular to an axis passing through the centerline of inner radial surface of stator  154 ; shrink-fitting stator  102  into main section  90  of housing  88  whereby a first planar edge  152  of main section  90  provides a reference for locating stator  102  vertically; inserting compressor mechanism  120  into housing such that surface  150  of manifold  84 , facing stator  102 , abuts the corresponding first planar edge  152  of main section  90 ; inserting a mandrel, or dummy rotor, into a cavity of stator  102  to concentrically align main bearing  112  with stator  102 ; spot welding manifold  84  to main housing section  90 ; machining peripheral surface  192  of bearing support member  86  to provide substantial perpendicularity between peripheral surface  192  and a centerline axis with respect to an inner radial surface  198  of auxiliary bearing  94 ; fastening auxiliary bearing  94  to bearing support member  86 ; inserting a shaft  106  coupled to a rotor  104  into the stator  102  and fitting the auxiliary bearing  94  onto an end of the shaft until planar surface of bearing support member  86  abuts second planar edge of main section of housing; inserting gages into apertures  184  within auxiliary bearing  94  to set gap  186  between stator  102  and rotor  104 ; providing a continuous weld to join bearing support member  86  with main section  90  of housing  88 ; and welding end sections  92 ,  96  to each respective end  152 ,  86  of housing  88  to sealably enclose housing  88 . 
     While this invention has been described as having an exemplary embodiment, the present invention may be further modified within the spirit and scope of this disclosure. This application is therefore intended to cover any variations, uses, or adaptations of the invention using its general principles. For example, aspects of the present invention may be applied to rotary compressors. Further, this application is intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this invention pertains.