Abstract:
A vertical compressor is converted to a horizontal compressor by laying the vertical compressor on its side and locating it within the standard shell of a larger vertical compressor. The end caps and partition of the smaller compressor are removed while the end caps and the partition of the larger compressor are added. A lubricant pump pumps lubricant from the sump defined between the two shells to all areas of the compressor requiring lubrication.

Description:
FIELD OF THE INVENTION 
     The present invention relates to scroll machines. More particularly, the present invention relates to scroll compressors which are positioned horizontally and utilize an existing compressor shell to encase a second existing compressor shell within which the scroll compressor is located. 
     BACKGROUND AND SUMMARY OF THE INVENTION 
     Scroll type machines are becoming more and more popular for use as compressors in both refrigeration as well as air conditioning applications due primarily to their capability for extremely efficient operation. Generally, these machines incorporate a pair of intermeshed spiral wraps one of which is caused to orbit relative to the other so as to define one or more moving chambers which progressively decrease in size as they travel from an outer suction port toward a center discharge port. An electric motor is provided which operates to drive the orbiting scroll member via a suitable drive shaft affixed to the motor rotor. In a hermetic compressor, the bottom of the hermetic shell normally contains an oil sump for lubricating and cooling purposes. 
     Generally, the motor includes a stator which is secured to the shell of the compressor. The motor rotor rotates within the stator to impart rotation to a crankshaft which is normally press fit within the motor rotor. The crankshaft is rotationally supported by a pair of bearings which are supported by a main bearing housing and a secondary bearing housing. The crankshaft includes an eccentric crank pin which extends into a bore defined in a hub of the orbiting scroll. Disposed between the hub of the crank pin and the inner surface of the bore is a drive bushing which rides against a bearing that is press fit within the bore of the hub. 
     The design for scroll compressors position the central axis of the crankshaft in a vertical or horizontal position. One difference between the vertical and horizontal scroll compressor designs is the lubrication sump and the delivery systems which deliver the lubricant to the various components of the compressor which require lubrication. In a typical vertically positioned compressor, lubricant is stored in the lower portion of the shell with the lower end of the crankshaft being submerged within the sump. The crankshaft has a relatively large diameter centrally located bore which communicates with a radially outwardly inclined smaller diameter bore which extends to the top of the crankshaft. The larger diameter bore acts as a pump to pump the lubricating fluid up the crankshaft into the smaller diameter bore and ultimately to all of the various portions of the compressor which require lubrication. 
     When the compressor is positioned horizontally, it is not practical to immerse the end of the crankshaft within the lubricant since this would require filling over one-half of the shell with lubricant. The present invention provides the art with a horizontal compressor which includes a typical vertical compressor which has been positioned horizontally. The horizontally positioned vertical compressor is disposed within the shell of a larger vertical compressor to provide the necessary lubrication sump for the horizontal compressor. 
     Other advantages and objects of the present invention will become apparent to those skilled in the art from the subsequent detailed description, appended claims and drawings. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     In the drawings which illustrate the best mode presently contemplated for carrying out the present invention: 
     FIG. 1 is a side view of a horizontal scroll type refrigeration compressor in accordance with the present invention; 
     FIG. 2 is an end view of the horizontal scroll type refrigeration compressor shown in FIG. 1; 
     FIG. 3 is a vertical cross-sectional view through the center of the scroll type refrigeration compressor shown in FIG. 1; 
     FIG. 4 is an end view of the scroll type refrigeration compressor shown in FIG. 1 with the cap and partition removed; and 
     FIG. 5 is an end view of the scroll type refrigeration compressor at the end opposite to the one shown in FIG. 1 with the end cap and the oil pump removed. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     Referring now to the drawings in which like reference numerals designate like or corresponding parts throughout the several views, there is shown in FIGS. 1-5 a horizontal-type refrigeration scroll compressor in accordance with the present invention which is designated generally by the reference numeral  10 . Compressor  10  comprises an inner generally cylindrical shell  12  and an outer generally cylindrical hermetic shell  14 . Inner generally cylindrical shell  12  is preferably a standard compressor shell from a currently existing vertical compressor. Likewise, outer generally cylindrical hermetic shell  14  is preferably a standard compressor shell from a currently existing vertical compressor which is larger than the compressor from shell  12 . By utilizing two existing compressor shells, one large one small, the costs associated with producing horizontal compressor  10  can be reduced significantly. 
     Generally cylindrical hermetic outer shell  14  has welded at one end thereof an end cap  16  and at the opposite end an end cap  18 . A plurality of feet  20  are secured to shell  14  to facilitate this positioning of compressor  10  within a refrigeration system. Cap  16  is provided with a refrigerant discharge fitting  22  which may have the usual discharge valve therein. Other major elements affixed to shell  14  include a transversely extending partition  24  which is welded about its periphery at the same point that end cap  16  is welded to shell  14 , a suction fitting  56 , an oil drain fitting  28 , a terminal block  30 , a liquid injection fitting  32  and a sight glass  34 . Inner shell  12  is disposed within outer shell  14  and it is centrally positioned within outer shell  14  by a plurality of spacers  26 . 
     Major elements which are affixed to shell  12  include a main bearing housing  36  which is suitably secured to shell  12  by a plurality of radially outwardly extending legs and a secondary bearing housing  38  also having a plurality of radially outwardly extending legs each of which is also suitably secured to shell  12 . A motor stator  40  which is generally square or hexagonal in cross-section but with the corners rounded off is press fitted into shell  12 . The flats between the rounded corners on stator  40  provide passageways between stator  40  and shell  12 , which facilitate the flow of lubricant and refrigerant gas within shell  12 . 
     A drive shaft or crankshaft  42  having an eccentric crank pin  44  at one end thereof is rotatably journaled in a bearing  46  in main bearing housing  36  and a second bearing  48  in secondary bearing housing  38 . Crankshaft  42  has at the opposite end a relatively large diameter concentric bore  50  which communicates with a radially outwardly inclined smaller diameter bore  52  extending through crankshaft  42 . Secured to the outer side of secondary bearing housing  38  is a lubricant pumping system  60  which is powered by crankshaft  42 . Pumping system  60  includes an inlet housing assembly  62 , an inlet tube  64  and a lubricant pump  66  driven by crankshaft  42 . Lubricant pump  66  is secured to inlet housing assembly  62  which is in turn secured to secondary bearing housing  38 . Inlet tube  64  extends from inlet housing assembly  62  to a power position between shells  12  and  14 . The lower position between shells  12  and  14  define a sump  68  within which lubricant is accumulated. Pump  66  draws lubricant from sump  68  through tube  64  and housing assembly  62  and pumps this lubricant into bore  50  and into bore  52  and ultimately to all of the various portions of compressor  10  which require lubrication. 
     Crankshaft  42  is rotatively driven by an electric motor including stator  40 , windings  70  passing therethrough and a rotor  72  press fitted on crankshaft  42  and having first and second counterweights  74  and  76 , respectively. 
     The outer surface of main bearing housing  36  is provided with a flat thrust bearing surface  78  against which is disposed an orbiting scroll member  80  having the usual spiral vane or wrap  82  extending outward from an end plate  84 . Projecting outwardly from the opposite surface of end plate  84  of orbiting scroll member  80  is a cylindrical hub  86  having a journal bearing  88  therein and in which is rotatively disposed a drive bushing  90  having an inner bore  92  in which crank pin  44  is drivingly disposed. Crank pin  44  has a flat on one surface which drivingly engages a flat surface (not shown) formed in a portion of bore  92  to provide a radially compliant driving arrangement, such as shown in assignee&#39;s U.S. Pat. No. 4,877,382, the disclosure of which is hereby incorporated herein by reference. An Oldham coupling  94  is also provided positioned between orbiting scroll member  80  and bearing housing  36  and keyed to orbiting scroll member  80  and a non-orbiting scroll member  96  to prevent rotational movement of orbiting scroll member  80 . Oldham coupling  94  is preferably of the type disclosed in assignee&#39;s co-pending U.S. Pat. No. 5,320,506, the disclosure of which is hereby incorporated herein by reference. 
     Non-orbiting scroll member  96  is also provided having a wrap  98  extending outwardly from an end plate  100  which is positioned in meshing engagement with wrap  82  of orbiting scroll member  80 . Non-orbiting scroll member  96  has a centrally disposed discharge passage  102  which communicates with an upwardly open recess  104  which in turn is in fluid communication with a discharge muffler chamber  106  defined by cap  16  and partition  24 . An annular recess  108  is also formed in non-orbiting scroll member  96  within which is disposed a seal assembly  110 . Recesses  104  and  108  and seal assembly  110  cooperate to define axial pressure biasing chambers which receive pressurized fluid being compressed by wraps  82  and  98  so as to exert an axial biasing force on non-orbiting scroll member  96  to thereby urge the tips of respective wraps  82 ,  98  into sealing engagement with the opposed end plate surfaces of end plates  100  and  84 , respectively. Seal assembly  110  is preferably of the type described in greater detail in U.S. Pat. No. 5,156,539, the disclosure of which is hereby incorporated herein by reference. Non-orbiting scroll member  96  is designed to be mounted to bearing housing  36  in a suitable manner such as disclosed in the aforementioned U.S. Pat. No. 4,877,382 or U.S. Pat. No. 5,102,316, the disclosure of which is hereby incorporated herein by reference. 
     Thus, horizontal compressor  10  of the present invention provides the art with an effective cost reducing method of converting a typical vertically oriented compressor into a horizontal compressor. The utilization of two shells from existing vertical compressors enables a low cost conversion to the horizontal system. The existing smaller shell with its compressor mounted within it is located within the shell of a large compressor. The two shells form a lubricant sump from which lubricant is pumped by a pumping system powered by the rotating crankshaft. 
     While the above detailed description describes the preferred embodiment of the present invention, it should be understood that the present invention is susceptible to modification, variation and alteration without deviating from the scope and fair meaning of the subjoined claims.