Abstract:
A scroll compressor is provided and may include an orbiting scroll member having an orbiting end plate and an orbiting spiral wrap extending from the orbiting end plate. The scroll compressor may also include a non-orbiting scroll member having a non-orbiting end plate and a non-orbiting spiral wrap extending from the non-orbiting end plate and intermeshed with the orbiting spiral wrap. The scroll compressor may further include a drive member for causing the orbiting scroll member to orbit relative to the non-orbiting scroll member and a discharge slot formed by one of the orbiting scroll member and the non-orbiting scroll member. A discharge valve may be rotatable with the drive member and may operate between a closed state preventing fluid communication between the pockets and the discharge slot and an open state permitting fluid communication between the pockets and the discharge slot.

Description:
CROSS REFERENCE TO RELATED APPLICATION 
     This application is a continuation of U.S. patent application Ser. No. 12/103,265 filed on Apr. 15, 2008, which is a continuation of U.S. patent application Ser. No. 11/522,250 filed on Sep. 15, 2006 (now U.S. Pat. No. 7,371,059). The disclosures of the above applications are incorporated herein by reference in its entirety. 
    
    
     FIELD 
     The present disclosure relates to scroll type machines. More particularly, the present disclosure relates to scroll compressors which incorporate features that reduce the number of components, the size and the complexity of the scroll compressor. 
     BACKGROUND 
     The statements in this section merely provide background information related to the present disclosure and may not constitute prior art. 
     Refrigeration and air conditioning systems generally include a compressor, a condenser, an expansion valve or its equivalent, and an evaporator. These components are coupled in sequence to define a continuous flow path. A working fluid typically called a refrigerant flows through the system and alternates between a liquid phase and a vapor or gaseous phase. 
     A variety of compressor types have been used in refrigeration systems, including, but not limited to, reciprocating compressors, screw compressors and rotary compressors. Rotary compressors can include both the vane type compressors, the scroll machines as well as other rotary styled compressors. 
     Scroll machines are becoming more and more popular for the compressor of choice in both refrigeration as well as air conditioning applications due primarily to their capability for extremely efficient operation. Scroll compressors are typically constructed using two scroll members with each scroll member having an end plate and a spiral wrap extending from the end plate. The spiral wraps are arranged in an opposing manner with the two spiral wraps being interfitted. The scroll members are mounted so that they may engage in relative orbiting motion with respect to each other. During this orbiting movement, the spiral wraps define a successive series of enclosed spaces, each of which progressively decreases in size as it moves inwardly from a radially outer position at a relatively low suction pressure to a central position at a relatively high discharge pressure. The compressed gas exits from the enclosed space at the central position through a discharge passage formed through the end plates of one of the scroll members. 
     An electric motor or another power source is provided which operates to drive one of the scroll members 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 the various components of the compressor. 
     Relative rotation between the two scroll members is typically controlled by an anti-rotation mechanism. One of the more popular anti-rotation mechanisms is an Oldham coupling, which is keyed to either the two scroll members or to one of the scroll members and a stationary component such as a bearing housing. While Oldham couplings are a popular choice, other anti-rotation mechanisms may also be utilized. 
     Due to the increasing popularity of scroll compressors, the continued development of these compressors has been directed towards designs that reduce size, reduce complexity and reduce cost without adversely affecting the performance of the scroll compressor. 
     SUMMARY 
     A scroll compressor is provided and may include an orbiting scroll member having an orbiting end plate and an orbiting spiral wrap extending from the orbiting end plate. The scroll compressor may also include a non-orbiting scroll member having a non-orbiting end plate and a non-orbiting spiral wrap extending from the non-orbiting end plate and intermeshed with the orbiting spiral wrap. The scroll compressor may further include a drive member for causing the orbiting scroll member to orbit relative to the non-orbiting scroll member and a discharge slot formed by one of the orbiting scroll member and the non-orbiting scroll member. A discharge valve may be rotatable with the drive member and may operate between a closed state preventing fluid communication between the pockets and the discharge slot and an open state permitting fluid communication between the pockets and the discharge slot. 
     In another configuration, a scroll compressor is provided and may include an orbiting scroll member having an orbiting end plate and an orbiting spiral wrap extending from the orbiting end plate and a non-orbiting scroll member having a non-orbiting end plate, a non-orbiting spiral wrap extending from the non-orbiting end plate, and a discharge slot. The non-orbiting spiral wrap may be intermeshed with the orbiting spiral wrap to create pockets of progressively changing volume between a suction pressure zone and a discharge pressure zone. The scroll compressor may also include a bearing housing extending from the non-orbiting end plate and a drive member that causes the orbiting scroll member to orbit relative to the non-orbiting scroll member to compress a fluid within the pockets. The drive member may extend through the bearing housing, the non-orbiting scroll member, and the orbiting scroll member. A discharge valve may be rotatable with the drive member and may operate between a closed state preventing fluid communication between the pockets and the discharge slot and an open state permitting fluid communication between the pockets and the discharge slot. 
     Further areas of applicability will become apparent from the description provided herein. It should be understood that the description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the present disclosure. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The drawings described herein are for illustration purposes only and are not intended to limit the scope of the present disclosure in any way. 
         FIG. 1  is a vertical cross-section of a scroll compressor incorporating the unique design features of the present invention; 
         FIG. 2  is a perspective view illustrating the two scroll members, the counterweight, the Oldham coupling, and the drive shaft of the compressor shown in  FIG. 1 ; 
         FIG. 3  is a perspective view illustrating the scroll wrap profile of the orbiting scroll member shown in  FIG. 1 ; 
         FIG. 4  is a perspective view illustrating the scroll wrap profile of the non-orbiting scroll member shown in  FIG. 1 ; 
         FIG. 5  is a vertical cross-section of a compressor where the Oldham coupling has been replaced with a swing link; 
         FIG. 6  is a perspective view similar to  FIG. 2 , but illustrating the swing link in place of the Oldham coupling as illustrated in  FIG. 5 ; 
         FIG. 7  is a vertical cross-section of a scroll compressor incorporating the unique design features in accordance with another embodiment of the present invention; 
         FIG. 8  is a perspective view similar to  FIG. 2 , with the addition of an upper bearing retainer for supporting the drive shaft as shown in  FIG. 7 ; 
         FIG. 9  is a vertical cross-section of a scroll compressor incorporating the unique design features in accordance with another embodiment of the present invention; 
         FIG. 10  is a perspective view of the orbiting scroll member illustrated in  FIG. 9 ; 
         FIG. 11  is an enlarged perspective view of the discharge port of the non-orbiting scroll member illustrated in  FIG. 9 ; 
         FIG. 12  is a vertical cross-section of a scroll compressor incorporating the unique design features in accordance with another embodiment of the present invention; 
         FIG. 13  is a top view of the rotary valve illustrated in  FIG. 12 ; 
         FIG. 14  is a bottom perspective view of the rotary valve illustrated in  FIG. 12 ; 
         FIG. 15  is a vertical cross-section of a scroll compressor incorporating the unique design features in accordance with another embodiment of the present invention; 
         FIG. 16  is a vertical cross-section of a scroll compressor incorporating the unique design features in accordance with another embodiment of the present invention; and 
         FIG. 17  is a perspective view of the non-orbiting scroll machine illustrated in  FIG. 16 . 
     
    
    
     DETAILED DESCRIPTION 
     The following description is merely exemplary in nature and is not intended to limit the present disclosure, application, or uses. 
     Referring now to the drawings in which like reference numerals designate like or corresponding parts throughout the several views, there is shown in  FIG. 1  a scroll compressor that incorporates the unique design features of the present invention and which is designated generally by the reference numeral  10 . 
     Scroll compressor  10  comprises a general cylindrical hermetic shell  12  having welded at the upper end thereof a caps  14  and at the lower end thereof a base  16  having a plurality of mounting feet (not shown) integrally formed therewith. Cap  14  is provided with a refrigerant discharge fitting  18 , which may have the usual discharge valve therein (not shown). Other major elements affixed to shell  12  include an inlet fitting  22 , a main bearing housing  24  that is suitably secured to shell  12 , and a motor stator  28 . Motor stator  28  is generally square in cross-section, but with the corners rounded off to allow for the press fitting of motor stator  28  within shell  12 . The flats between the rounded corners on motor stator  28  provide passageways between motor stator  28  and shell  12 , which facilitate the return flow of the lubricant from the top of shell  12  to its bottom. 
     A drive shaft or crankshaft  30  having an eccentric crank pin  32  at the upper end thereof is rotatably journaled in a bearing  34  in main bearing housing  24 . Crankshaft  30  has at the lower end thereof a tubular extension  36  that communicates with a radially inclined and outwardly located bore  38  extending upwardly therefrom to the top of crank pin  32 . The lower portion of the interior of shell  12  forms an oil sump  40  that is filled with lubricating oil. Tubular extension  36  extends into oil sump  40  and tubular extension  36 , in conjunction with bore  38 , acts as a pump to pump the lubricating oil up crankshaft  30  and ultimately to all of the various portions of compressor  10  that require lubricating. 
     Crankshaft  30  is driven by an electric motor that includes motor stator  28  having windings  42  passing therethrough and a motor rotor  44  press fitted onto crankshaft  30 . A lower counterweight  46  is attached to motor rotor  44  and an upper counterweight  48  is attached to the upper-end of crankshaft  30 . A motor protector  50  of the usual type is provided in close proximity to motor windings  42  so that if motor windings  42  exceed their normal operating temperature, motor protector  50  will de-energize the motor. 
     Crankshaft  30  extends through the central portion of an orbiting scroll member  56 . Orbiting scroll member  56  comprises an end plate  58  having a spiral vane or wrap  60  that is designed with a rapid compression profile as described below. Projecting downwardly from end plate  58  is a cylindrical hub  62  having a journal bearing  64  therein and in which is drivingly disposed crank pin  32 . 
     Orbiting scroll wrap  60  meshes with a non-orbiting scroll wrap  66  forming part of a non-orbiting scroll member  68 , which is integral with main bearing housing  24 . During orbiting movement of orbiting scroll member  56  with respect to non-orbiting scroll member  68 , moving pockets of fluid are formed and the fluid is compressed in the fluid pockets as the volume of the fluid pockets reduce as they travel from a radially outer position to a central position of scroll members  56  and  68 . 
     Orbiting scroll member  56  has a radially inwardly disposed discharge port  70 , which is in fluid communication with a discharge chamber  72  defined by cap  14  and shell  12 . Fluid compressed by the moving pockets between scroll wraps  60  and  66  discharges into discharge chamber  72  through discharge port  70 . 
     Upper counterweight  48  rotates at a position immediately adjacent end plate  58  of orbiting scroll member  56 . During the rotation of upper counterweight  48 , discharge port  70  is cyclically covered and uncovered by upper counterweight  48 , which allows upper counterweight  48  to act as a rotary discharge valve for compressor  10 . 
     Relative rotation of scroll member  56  and  68  is prevented by an Oldham coupling  80  having a first pair of keys slidably disposed in diametrically opposing slots in non-orbiting scroll member  68  and a second pair of keys slidably disposed in diametrically opposing slots in orbiting scroll member  56 . 
     As described above, scroll wraps  60  and  66  define a rapid compression scroll profile. The rapid compression scroll profile provides the advantages of a shorter wrap, lower tool aspect ratios, lower vane aspect ratios, there is no need to machine the back side of end plate  58  other than the race for upper counterweight  48 , and it allows orbiting scroll member  56  to be manufactured using a powder medal process. The preferred profile for scroll wraps  60  and  66  is given in the following table where Ri is the initial swing radius bias and R G  is the generating radius bias: 
     
       
         
               
               
               
               
               
               
             
               
               
               
               
               
               
             
               
             
               
               
               
               
               
               
             
               
             
               
               
               
               
               
               
             
           
               
                   
               
               
                 PROFILED 
                   
                   
                   
                   
                   
               
               
                 PARAMETERS 
                   
                 WRAP 
                   
                 VANE 
               
             
          
           
               
                 Ri 
                 RG 
                 Wrap 
                 Length 
                 Thick 
                 Height 
               
               
                 mm 
                 mm 
                 deg 
                 mm 
                 mm 
                 mm 
               
               
                   
               
             
          
           
               
                 Inner Profile 
               
             
          
           
               
                 9 
                 0 
                 158.67 
                 25 
                 — 
                 — 
               
               
                 25.653 
                 2.864789 
                 250 
                 140 
                 5 
                 21.41 
               
             
          
           
               
                 Outer Profile 
               
             
          
           
               
                 15 
                 0 
                 158.67 
                 42 
                 — 
                 — 
               
               
                 21.653 
                 2.864789 
                 430 
                 244 
                 5 
                 21.41 
               
               
                   
               
             
          
         
       
     
     As illustrated in the Figures, main bearing housing  24  and non-orbiting scroll member  68  are an integral component. Preferably, this component is machined from an iron casting and the advantages of having an integral non-orbiting scroll member  68  and main bearing housing  24  include that the bearing bore can be used as a fixture for the machining of non-orbiting scroll wrap  66 . By using the bearing bore as a fixture for machining the scroll wrap, the stack-up of tolerances are minimized, the radial compliance is minimized or reduced, and the bearing/gas/flank/axial forces are linked within a single component. 
     Compressor  10  is preferably a “high side” type, in which the volume defined by shell  12 , cap  14  and base  16  is at discharge pressure. In this way, discharge fitting  18  can be conveniently located on shell  12  or cap  14 . Inlet fitting  22  sealingly engages and extends through shell  12  and is sealingly received within non-orbiting scroll member  68  to provide gas at suction pressure to compressor  10 . 
     Referring now to  FIG. 5 , a scroll compressor in accordance with another embodiment of the present invention is illustrated and is designed generally by the reference numeral  110 . 
     Scroll compressor  110  comprises a general cylindrical hermetic shell  112  having welded at the upper end thereof a cap  114  and at the lower end thereof a base  116  having a plurality of mounting feet (not shown) integrally formed therewith. Cap  114  is provided with a refrigerant discharge fitting  118 , which may have the usual discharge valve therein (not shown). Other major elements affixed to shell  112  include an inlet fitting  122 , a main bearing housing  124  that is suitably secured to shell  112 , and a motor stator  128 . Motor stator  128  is generally square in cross-section, but with the corners rounded off to allow for the press fitting of motor stator  128  within shell  112 . The flats between the rounded corners on motor stator  128  provide passageways between motor stator  128  and shell  112 , which facilitate the return flow of the lubricant from the top of shell  112  to its bottom. 
     A drive shaft or crankshaft  130  having an eccentric crank pin  132  at the upper end thereof is rotatably journaled in a bearing  134  in main bearing housing  124 . Crankshaft  130  has at the lower end thereof a tubular extension  136  that communicates with a radially inclined and outwardly located bore  138  extending upwardly therefrom to the top of crank pin  132 . The lower portion of the interior of shell  112  forms an oil sump  140  that is filled with lubricating oil. Tubular extension  136  extends into oil sump  140  and tubular extension  136 , in conjunction with bore  138 , acts as a pump to pump the lubricating oil up crankshaft  130  and ultimately to all of the various portions of compressor  110  that require lubricating. 
     Crankshaft  130  is driven by an electric motor that includes motor stator  128  having windings  142  passing therethrough and a motor rotor  144  press fitted onto crankshaft  130 . A lower counterweight  146  is attached to motor rotor  144  and an upper counterweight  148  is attached to the upper-end of crankshaft  130 . A motor protector  150  of the usual type is provided in close proximity to motor windings  142  so that if motor windings  142  exceed their normal operating temperature, motor protector  150  will de-energize the motor. 
     Crankshaft  130  extends through the central portion of an orbiting scroll member  156 . Orbiting scroll member  156  comprises an end plate  158  having a spiral vane or wrap  160  that is designed with a rapid compression profile as described below. Projecting downwardly from end plate  158  is a cylindrical hub  162  having a journal bearing  164  therein and in which is drivingly disposed crank pin  132 . 
     Orbiting scroll wrap  160  meshes with a non-orbiting scroll wrap  166  forming part of a non-orbiting scroll member  168 , which is integral with main bearing housing  124 . During orbiting movement of orbiting scroll member  156  with respect to non-orbiting scroll member  168 , moving pockets of fluid are formed and the fluid is compressed in the fluid pockets as the volume of the fluid pockets reduce as they travel from a radially outer position to a central position of scroll members  156  and  168 . 
     Orbiting scroll member  156  has a radially inwardly disposed discharge port  170 , which is in fluid communication with a discharge chamber  172  defined by cap  114  and shell  112 . Fluid compressed by the moving pockets between scroll wraps  160  and  166  discharges into discharge chamber  172  through discharge port  170 . 
     Upper counterweight  148  rotates at a position immediately adjacent end plate  158  of orbiting scroll member  156 . During the rotation of upper counterweight  148 , discharge port  170  is cyclically covered and uncovered by upper counterweight  148 , which allows upper counterweight  148  to act as a rotary discharge valve for compressor  110 . 
     Relative rotation of scroll members  156  and  168  is prevented by a swing link  178 . Swing link  178  comprises a generally U-shaped extension  180 , which is attached to or is integral with end plate  158  of orbiting scroll member  156 . U-shaped extension  180  engages a generally rectangular bearing  182 , which is pivotably disposed on a post  184  extending from non-orbiting scroll member  168 . The engagement between U-shaped extension  180  and bearing  182 , in conjunction with the engagement between bearing  182  and post  184 , prohibits the rotational movement of orbiting scroll member  156  with respect to non-orbiting scroll member  168 , but allows the necessary orbiting movement of orbiting scroll member  156  with respect to non-orbiting scroll member  168  such that the moving pockets are formed and made to move radially inward during the rotation of crankshaft  130 . 
     As described above, scroll wraps  160  and  166  also define a rapid compression scroll profile. The rapid compression scroll profile provides the advantages of a shorter wrap, lower tool aspect ratios, lower vane aspect ratios, there is no need to machine the back side of end plate  158  other than the race for upper counterweight  148 , and it allows orbiting scroll member  156  to be manufactured using a powder medal process. The preferred profile for scroll wraps  160  and  166  is given in the following table where Ri is the initial swing radius bias and R G  is the generating radius bias: 
     
       
         
               
               
               
               
               
               
             
               
               
               
               
               
               
             
               
             
               
               
               
               
               
               
             
               
             
               
               
               
               
               
               
             
           
               
                   
               
               
                 PROFILED 
                   
                   
                   
                   
                   
               
               
                 PARAMETERS 
                   
                 WRAP 
                   
                 VANE 
               
             
          
           
               
                 Ri 
                 RG 
                 Wrap 
                 Length 
                 Thick 
                 Height 
               
               
                 mm 
                 Mm 
                 deg 
                 mm 
                 mm 
                 mm 
               
               
                   
               
             
          
           
               
                 Inner Profile 
               
             
          
           
               
                 9 
                 0 
                 158.67 
                 25 
                 — 
                 — 
               
               
                 25.653 
                 2.864789 
                 250 
                 140 
                 5 
                 21.41 
               
             
          
           
               
                 Outer Profile 
               
             
          
           
               
                 15 
                 0 
                 158.67 
                 42 
                 — 
                 — 
               
               
                 21.653 
                 2.864789 
                 430 
                 244 
                 5 
                 21.41 
               
               
                   
               
             
          
         
       
     
     As illustrated in the Figures, main bearing housing  124  and non-orbiting scroll member  168  are an integral component. Preferably, this component is machined from an iron casting and the advantages of having an integral non-orbiting scroll member  168  and main bearing housing  124  include that the bearing bore can be used as a fixture for the machining of non-orbiting scroll wrap  166 . By using the bearing bore as a fixture for machining the scroll wrap, the stack-up of tolerances are minimized, the radial compliance is minimized or reduced, and the bearing/gas/flank/axial forces are linked within a single component. 
     Compressor  110  is preferably a “high side” type, in which the volume defined by shell  112 , cap  114  and base  116  is at discharge pressure. In this way, discharge fitting  118  can be conveniently located on shell  112  or cap  114 . Inlet fitting  122  sealingly engages and extends through shell  112  and is sealingly received within non-orbiting scroll member  168  to provide gas at suction pressure to compressor  110 . 
     Referring now to  FIGS. 7 and 8 , a compressor  10 ′ in accordance with another embodiment of the present invention is illustrated. Compressor  10 ′ is the same as compressor  10 , except that the integral component of main bearing housing  24  and non-orbiting scroll member  68  is replaced with the integral component of main bearing housing  24 ′ and non-orbiting scroll member  68 ′. Main bearing housing  24 ′ and non-orbiting scroll member  68 ′ are the same as main bearing housing  24  and non-orbiting scroll member  68 ′, except that main bearing housing  24 ′ and non-orbiting scroll member  68 ′ include an upper bearing housing  90 . Upper bearing housing  90  includes a plurality of supporting posts  92  and a bearing support  94 . Supporting posts  92  are integral with main bearing housing  24 ′ and non-orbiting scroll member  68 ′, or they can be a separate component attached by methods known well in the art. Bearing support  94  is attached to the plurality of supporting posts  92  using a plurality of bolts or by other means known well in the art. The plurality of supporting posts  92  are spaced along the outer periphery of main bearing housing  24 ′ and non-orbiting scroll member  68 ′ such that they do not interfere with upper counterweight  48 . Bearing support  94  positions an upper bearing  96  within which crankshaft  30  is rotatably disposed. Thus, crankshaft  30  is supported by bearing  34  located within main bearing housing  24 ′ and by upper bearing  96  located within bearing support  94 . The design, function, operation, and advantages associated with compressor  10  are also associated with compressor  10 ′, including, but not limited to, the ability to use Oldham coupling  88  illustrated in  FIG. 6  as well as the incorporation of the rapid compression scroll wrap profiles. 
     Referring now to  FIGS. 9-11 , a scroll compressor that incorporates the unique design features in accordance with another embodiment of the present invention is illustrated and it is designated generally by reference numeral  210 . 
     Scroll compressor  210  comprises a general cylindrical hermetic shell  212  having welded at the upper end thereof a cap  214  and at the lower end thereof a base  216  having a plurality of mounting feet (not shown) integrally formed therewith. Cap  214  is provided with a refrigerant discharge fitting  218 , which may have the usual discharge valve therein (not shown). Other major elements affixed to shell  212  or cap  214  include an upper bearing housing  220 , an inlet fitting  222 , a main bearing housing  224  that is suitably secured to shell  212 , and a motor stator  226 . Motor stator  226  is generally square in cross-section, but with the corners rounded off to allow for the press fitting of motor stator  226  within shell  212 . The flats between the rounded corners on motor stator  226  provide passageways between motor stator  226  and shell  212 , which facilitate the return flow of the lubricant from the top of shell  212  to its bottom. 
     A drive shaft or crankshaft  230  having an eccentric crank pin  232  at the upper end thereof is rotatably journaled in a bearing  234  in main bearing housing  224  and in a bearing  235  in upper bearing housing  220 . Crankshaft  230  has at the lower end thereof a tubular extension  236  that communicates with a radially included and outwardly located bore  238  extending upwardly therefrom to the top of crank pin  232 . The lower portion of the interior of shell  212  forms an oil sump  240  that is filled with lubricating oil. Tubular extension  236  extends into oil sump  240  and tubular extension  236 , in conjunction with bore  238 , acts as a pump to pump the lubricating oil up crankshaft  230  and ultimately to all of the various portions of compressor  210  that require lubricating. 
     Crankshaft  230  is driven by an electric motor that includes motor stator  226  having windings  242  passing therethrough and a motor rotor  244  press fitted onto crankshaft  230 . A lower counterweight  246  is attached to motor rotor  244  and an upper counterweight  248  is attached to the upper-end of motor rotor  244 . A motor protector  250  of the usual type is provided in close proximity to motor windings  242  so that if motor windings  242  exceed their normal operating temperature, motor protector  250  will de-energize the motor. 
     Crankshaft  230  extends through the central portion of an orbiting scroll member  256 . Orbiting scroll member  256  comprises an end plate  258  having a spiral vane or wrap  260  that is designed with a rapid compression profile as described above. Projecting downwardly from end plate  258  is a cylindrical hub  262  having a journal bearing  264  therein and in which is drivingly disposed crank pin  232 . 
     Orbiting scroll wrap  260  meshes with a non-orbiting scroll wrap  266  forming part of a non-orbiting scroll member  268 , which is integral with main bearing housing  224 . During orbiting movement of orbiting scroll member  256  with respect to non-orbiting scroll member  268 , moving pockets of fluid are formed and the fluid is compressed in the fluid pockets as the volume of the fluid pockets reduce as they travel from a radially outer position to a central position of scroll members  256  and  268 . 
     Orbiting scroll member  256  has a radially inwardly disposed discharge slot  270 , which is in fluid communication with a discharge port  272  that extends through non-orbiting scroll member  268 , which is in communication with a discharge chamber  274  defined by cap  214  and shell  212 . Fluid compressed by the moving pockets between scroll wraps  260  and  266  discharges into discharge chamber  274  through discharge slot  270  and discharge port  272 . 
     Relative rotation of scroll members  256  and  268  is prevented by the usual Oldham coupling  288  having a first pair of keys slidably disposed in diametrically opposing slots in non-orbiting scroll member  268  and a second pair of keys slidably disposed in diametrically opposing slots in orbiting scroll member  256 , as illustrated in  FIG. 9 . While  FIG. 9  illustrates Oldham coupling  288  as the mechanism for preventing relative rotation of scroll members  256  and  268 , it is within the scope of the present invention to replace Oldham coupling  288  with swing link  78  described above if desired. 
     As described above, scroll wraps  260  and  266  define a rapid compression scroll profile. The rapid compression scroll profile provides the advantages of a shorter wrap, lower tool aspect ratios, lower vane aspect ratios, and it allows orbiting scroll member  256  to be manufactured using a powder medal process. The preferred profile for scroll wraps  260  and  266  is given in the previous table that describes wraps  60  and  66 . 
     As illustrated in the Figures, main bearing housing  224  and non-orbiting scroll member  268  are an integral component. Preferably, this component is machined from an iron casting and the advantages of having an integral non-orbiting scroll member  268  and main bearing housing  224  include that the bearing bore can be used as a fixture for the machining of non-orbiting scroll wrap  266 . By using the bearing bore as a fixture for machining the scroll wrap, the stack-up of tolerances are minimized, the radial compliance is minimized or reduced, and the bearing/gas/flank/axial forces are linked within a single component. 
     Compressor  210  is preferably a “high side” type, in which the volume defined by shell  212 , cap  214  and base  216  is at discharge pressure. In this way, discharge fitting  218  can be conveniently located on shell  212  or cap  214 . Inlet fitting  222  sealingly engages and extends through shell  212  and is sealingly received within non-orbiting scroll member  268  to provide gas at suction pressure to compressor  210 . 
     Referring now to  FIG. 10 , discharge slot  270  of orbiting scroll member  256  is illustrated. Discharge slot  270  extends through cylindrical hub  262  and journal bearing  264 , which is press fit into cylindrical hub  262 . 
     Referring now to  FIG. 11 , discharge port  272  of non-orbiting scroll member  268  is illustrated. Discharge port  272  includes a formed recess  278 , which is in communication with an angular bore  280 , which is in communication with discharge chamber  274 . During the orbiting movement of orbiting scroll member  256 , orbiting scroll wrap  260  opens and closes discharge slot  270  and discharge port  272  to allow the compressed gas to move from the inner most moving pocket to discharge chamber  274 . 
     Referring now to  FIG. 12 , a scroll compressor that incorporates the unique design features in accordance with another embodiment of the present invention is illustrated and it is designated generally by reference numeral  310 . 
     Scroll compressor  310  comprises a general cylindrical hermetic shell  312  having welded at the upper end thereof a cap  314  and at the lower end thereof a base  316  having a plurality of mounting feet (not shown) integrally formed therewith. Cap  314  is provided with a refrigerant discharge fitting  318 , which may have the usual discharge valve therein (not shown). Other major elements affixed to shell  312  or cap  314  include an upper bearing housing  320 , an inlet fitting  322 , a main bearing housing  324  that is suitably secured to shell  312 , and a motor stator  326 . Motor stator  326  is generally square in cross-section, but with the corners rounded off to allow for the press fitting of motor stator  326  within shell  312 . The flats between the rounded corners on motor stator  326  provide passageways between motor stator  326  and shell  312 , which facilitate the return flow of the lubricant from the top of shell  312  to its bottom. 
     A drive shaft or crankshaft  330  having an eccentric crank pin  332  at the upper end thereof is rotatably journaled in a bearing  334  in main bearing housing  324  and in a bearing  335  in upper bearing housing  320 . Crankshaft  330  has at the lower end thereof a tubular extension  336  that communicates with a radially included and outwardly located bore  338  extending upwardly therefrom to the top of crank pin  332 . The lower portion of the interior of shell  312  forms an oil sump  340  that is filled with lubricating oil. Tubular extension  336  extends into oil sump  340  and tubular extension  336 , in conjunction with bore  338 , acts as a pump to pump the lubricating oil up crankshaft  330  and ultimately to all of the various portions of compressor  310  that require lubricating. 
     Crankshaft  330  is driven by an electric motor that includes motor stator  326  having windings  342  passing therethrough and a motor rotor  344  press fitted onto crankshaft  330 . A lower counterweight  346  is attached to motor rotor  344  and an upper counterweight  348  is attached to the upper-end of motor rotor  244 . A motor protector  350  of the usual type is provided in close proximity to motor windings  342  so that if motor windings  342  exceed their normal operating temperature, motor protector  350  will de-energize the motor. 
     Crankshaft  330  extends through the central portion of an orbiting scroll member  356 . Orbiting scroll member  356  comprises an end plate  358  having a spiral vane or wrap  360  that is designed with a rapid compression profile as described above. Projecting downwardly from end plate  358  is a cylindrical hub  362  having a journal bearing therein and in which is drivingly disposed crank pin  332 . 
     Orbiting scroll wrap  360  meshes with a non-orbiting scroll wrap  366  forming part of a non-orbiting scroll member  368 , which is integral with main bearing housing  324 . During orbiting movement of orbiting scroll member  356  with respect to non-orbiting scroll member  368 , moving pockets of fluid are formed and the fluid is compressed in the fluid pockets as the volume of the fluid pockets reduce as they travel from a radially outer position to a central position of scroll members  356  and  368 . 
     Non-orbiting scroll member  368  has a radially inwardly disposed discharge slot  370 , which is in fluid communication with a discharge port  372  that extends through non-orbiting scroll member  368 , which is in communication with a discharge chamber  374  defined by cap  314  and shell  312 . Fluid compressed by the moving pockets between scroll wraps  360  and  366  discharges into discharge chamber  374  through discharge slot  370  and discharge port  372 . Discharge slot  370  is a generally axially disposed slot and discharge port  372  is an inclined bore that is in communication with discharge chamber  374 . 
     Relative rotation of scroll members  356  and  368  is prevented by the usual Oldham coupling  388  having a first pair of keys slidably disposed in diametrically opposing slots in non-orbiting scroll member  368  and a second pair of keys slidably disposed in diametrically opposing slots in orbiting scroll member  356 , as illustrated in  FIG. 12 . While  FIG. 12  illustrated Oldham coupling  388  as the mechanism for preventing relative rotation of scroll members  356  and  368 , it is within the scope of the present invention to replace Oldham coupling  388  with swing link  78  described above if desired. 
     As described above, scroll wraps  360  and  366  define a rapid compression scroll profile. The rapid compression scroll profile provides the advantages of a shorter wrap, lower tool aspect ratios, lower vane aspect ratios, and it allows orbiting scroll member  356  to be manufactured using a powder medal process. The preferred profile for scroll wraps  360  and  366  is given in the previous table that describes wraps  60  and  66 . 
     As illustrated in the Figures, main bearing housing  324  and non-orbiting scroll member  368  are an integral component. Preferably, this component is machined from an iron casting and the advantages of having an integral non-orbiting scroll member  368  and main bearing housing  324  include that the bearing bore can be used as a fixture for the machining of non-orbiting scroll wrap  366 . By using the bearing bore as a fixture for machining the scroll wrap, the stack-up of tolerances are minimized, the radial compliance is minimized or reduced, and the bearing/gas/flank/axial forces are linked within a single component. 
     Compressor  310  is preferably a “high side” type, in which the volume defined by shell  312 , cap  314  and base  316  is at discharge pressure. In this way, discharge fitting  318  can be conveniently located on shell  312  or cap  314 . Inlet fitting  322  sealingly engages and extends through shell  312  and is sealingly received within non-orbiting scroll member  368  to provide gas at suction pressure to compressor  310 . 
     Referring now to  FIGS. 12-14 , a rotary discharge valve  378  is incorporated into compressor  310 . Rotary discharge valve  378  is driven by crankshaft  330  by a formed recess  380 , which engages crank pin  332  on its upper side. The lower side of rotary discharge valve  378  includes a port closing section  382 , a communication relief section  384  and a port open section  386 . As crankshaft  330  rotates, discharge slot  370  is closed when port closing section  382  is above axially disposed slot  370 , gas is allowed to flow to discharge port  372  when communication relief section  384  is above axially disposed slot  370 , and discharge port  372  is fully open when port open section  386  is above axially disposed slot  370 . 
     Referring now to  FIG. 15 , a scroll compressor that incorporates the unique design features in accordance with another embodiment of the present invention is illustrated and it is designated generally by reference numeral  410 . 
     Scroll compressor  410  comprises a general cylindrical hermetic shell  412  having welded at the upper end thereof a cap  414  and at the lower end thereof a base  416  having a plurality of mounting feet (not shown) integrally formed therewith. Cap  414  is provided with a refrigerant discharge fitting  418 , which may have the usual discharge valve therein (not shown). Other major elements affixed to shell  412  or cap  414  include an upper bearing housing  420 , an inlet fitting  422 , a main bearing housing  424  that is suitably secured to shell  412  and cap  414 , and a motor stator  426 . Motor stator  426  is generally square in cross-section, but with the corners rounded off to allow for the press fitting of motor stator  426  within shell  412 . The flats between the rounded corners on motor stator  426  provide passageways between motor stator  426  and shell  412 , which facilitate the return flow of the lubricant from the top of shell  412  to its bottom. 
     A drive shaft or crankshaft  430  having an eccentric crank pin  432  at the upper end thereof is rotatably journaled in a bearing  434  in main bearing housing  424  and in a bearing  435  in upper bearing housing  420 . Crankshaft  430  has at the lower end thereof a tubular extension  436  that communicates with a radially included and outwardly located bore  438  extending upwardly therefrom to the top of crank pin  432 . The lower portion of the interior of shell  412  forms an oil sump  440  that is filled with lubricating oil. Tubular extension  436  extends into oil sump  440  and tubular extension  436 , in conjunction with bore  438 , acts as a pump to pump the lubricating oil up crankshaft  430  and ultimately to all of the various portions of compressor  410  that require lubricating. 
     Crankshaft  430  is driven by an electric motor that includes motor stator  426  having windings  442  passing therethrough and a motor rotor  444  press fitted onto crankshaft  430 . A lower counterweight  446  is attached to motor rotor  444  and an upper counterweight  448  is attached to the upper-end of crankshaft  430 . A motor protector  450  of the usual type is provided in close proximity to motor windings  442  so that if motor windings  442  exceed their normal operating temperature, motor protector  450  will de-energize the motor. 
     Crankshaft  430  extends through the central portion of an orbiting scroll member  456 . Orbiting scroll member  456  comprises an end plate  458  having a spiral vane or wrap  460  that is designed with a rapid compression profile as described above. Projecting downwardly from end plate  458  is a cylindrical hub  462  having a journal bearing  464  therein and in which is drivingly disposed crank pin  432 . 
     Orbiting scroll wrap  460  meshes with a non-orbiting scroll wrap  466  forming part of a non-orbiting scroll member  468 , which is integral with main bearing housing  424 . During orbiting movement of orbiting scroll member  456  with respect to non-orbiting scroll member  468 , moving pockets of fluid are formed and the fluid is compressed in the fluid pockets as the volume of the fluid pockets reduce as they travel from a radially outer position to a central position of scroll members  456  and  468 . 
     Orbiting scroll member  456  has a radially inwardly disposed discharge port  470 , which is in fluid communication with a discharge chamber  472  defined by cap  414  and shell  412  through a discharge passage  474  formed in upper bearing housing  420 . Fluid compressed by the moving pockets between scroll wraps  460  and  466  discharges into discharge chamber  472  through discharge port  470  and discharge passage  474 . 
     Relative rotation of scroll members  456  and  468  is prevented by the usual Oldham coupling  488  having a first pair of keys slidably disposed in diametrically opposing slots in non-orbiting scroll member  468  and a second pair of keys slidably disposed in diametrically opposing slots in orbiting scroll member  456 , as illustrated in  FIG. 15 . While  FIG. 15  illustrates Oldham coupling  488  for preventing relative rotation of scroll members  456  and  468 , it is within the scope of the present invention to replace Oldham coupling  488  with swing link  78  described above if desired. 
     As described above, scroll wraps  460  and  466  define a rapid compression scroll profile. The rapid compression scroll profile provides the advantages of a shorter wrap, lower tool aspect ratios, lower vane aspect ratios, and it allows orbiting scroll member  456  to be manufactured using a powder medal process. The preferred profile for scroll wraps  460  and  466  is given in the previous table which described wraps  60  and  66 . 
     As illustrated in the Figures, main bearing housing  424  and non-orbiting scroll member  468  are an integral component. Preferably, this component is machined from an iron casting and the advantages of having an integral non-orbiting scroll member  468  and main bearing housing  424  include that the bearing bore can be used as a fixture for the machining of non-orbiting scroll wrap  466 . By using the bearing bore as a fixture for machining the scroll wrap, the stack-up of tolerances are minimized, the radial compliance is minimized or reduced, and the bearing/gas/flank/axial forces are linked within a single component. 
     Compressor  410  is preferably a “high side” type, in which the volume defined by shell  412 , cap  414  and base  416  is at discharge pressure. In this way, discharge fitting  418  can be conveniently located on shell  412  or cap  414 . Inlet fitting  422  sealingly engages and extends through cap  414  and is sealingly received within non-orbiting scroll member  468  to provide gas at suction pressure to compressor  410 . 
     Referring now to  FIGS. 16 and 17 , a scroll compressor that incorporates the unique features in accordance with another embodiment of the present invention is illustrated and it is designated generally by reference numeral  510 . 
     Scroll compressor  510  comprises a general cylindrical hermetic shell  512  having welded at the upper end thereof a cap  514  and at the lower end thereof a base  516  having a plurality of mounting feet (not shown) integrally formed therewith. Cap  514  is provided with a refrigerant discharge fitting  518 , which may have the usual discharge valve therein (not shown). Other major elements affixed to shell  512  include an inlet fitting  522 , a main bearing housing  524  that is suitably secured to shell  512 , and a motor stator  528 . Motor stator  528  is generally square in cross-section, but with the corners rounded off to allow for the press fitting of motor stator  528  within shell  512 . The flats between the rounded corners on motor stator  528  provide passageways between motor stator  528  and shell  512 , which facilitate the return flow of the lubricant from the top of shell  512  to its bottom. 
     A drive shaft or crankshaft  530  having an eccentric crank pin  532  is rotatably journaled in a bearing  534  in main bearing housing  524  and a bearing  536  in an outboard bearing structure  538 . Outboard bearing structure  538  is attached to a periphery of main bearing housing  524  and to cap  514 . Crankshaft  530  has at the lower end thereof a tubular extension  540  that communicates with a radially inclined and outwardly located bore  542  extending upwardly therefrom to lubricate bearing  536 . The lower portion of the interior of shell  512  forms an oil sump that is filled with lubricating oil. Tubular extension  540  extends into the oil sump and tubular extension  540 , in conjunction with bore  542 , acts as a pump to pump the lubricating oil up crankshaft  530  and ultimately to all of the various portions of compressor  510  that require lubricating. 
     Crankshaft  530  is driven by an electric motor that includes motor stator  528  having windings passing therethrough and a motor rotor  544  press fitted onto crankshaft  530 . A lower counterweight  546  is attached to motor rotor  544  and an upper counterweight  548  is attached to the upper-end of crankshaft  530 . A motor protector  550  of the usual type is provided in close proximity to the motor windings so that if the motor windings exceed their normal operating temperature, motor protector  550  will de-energize the motor. 
     Crankshaft  530  extends through the central portion of an orbiting scroll member  556 . Orbiting scroll member  556  comprises an end plate  558  having a spiral vane or wrap  560  that is designed with a rapid compression profile as described below. Projecting downwardly from end plate  558  is a cylindrical hub  562  having a journal bearing  564  therein and in which is drivingly disposed crank pin  532 . “Threaded” zone of crankshaft  530  between bearing  536  and crank pin  532  is designed in such a way that, during assembly, orbiting scroll member  556  can be assembled over bearing  536 . 
     Orbiting scroll wrap  560  meshes with a non-orbiting scroll wrap  566  forming part of a non-orbiting scroll member  568 , which is integral with main bearing housing  524 . During orbiting movement of orbiting scroll member  556  with respect to non-orbiting scroll member  568 , moving pockets of fluid are formed and the fluid is compressed in the fluid pockets as the volume of the fluid pockets reduce as they travel from a radially outer position to a central position of scroll members  556  and  568 . 
     Orbiting scroll member  556  has a radially inwardly disposed discharge port  570 , which is in fluid communication with a discharge chamber  572  defined by cap  514  and shell  512 . Fluid compressed by the moving pockets between scroll wraps  560  and  566  discharges into discharge chamber  572  through discharge port  570 . 
     Discharge port  570  (illustrated in greater detail on  FIG. 17 ) is machined into the baseplate of non-orbiting scroll member  566  and enables the discharge gas to escape the compression cavity into discharge chamber  572 . The shape of this port determines the relative position, of non-orbiting scroll wrap  566  and orbiting scroll wrap  560 , at which a pocket under compression starts to communicate with discharge port  570  and can be determined, by those skilled in the art, to minimize compression loses at a specified operational condition. Through passages  574 , the discharge gas moves to the upper portion of cap  514  and leaves compressor  510  through discharge fitting  518 . 
     Relative rotation of scroll member  556  and  568  is prevented by an Oldham coupling  580  having a first pair of keys slidably disposed in diametrically opposing slots in non-orbiting scroll member  568  and a second pair of keys slidably disposed in diametrically opposing slots in orbiting scroll member  556 . 
     As described above, scroll wraps  560  and  566  define a rapid compression scroll profile. The rapid compression scroll profile provides the advantages of a shorter wrap, lower tool aspect ratios, lower vane aspect ratios, there is no need to machine the back side of end plate  558  other than the race for upper counterweight  548 , and it allows orbiting scroll member  556  to be manufactured using a powder medal process. The preferred profile for scroll wraps  560  and  566  is given in the following table where Ri is the initial swing radius bias and R G  is the generating radius bias: 
     
       
         
               
               
               
               
               
               
             
               
               
               
               
               
               
             
               
             
               
               
               
               
               
               
             
               
             
               
               
               
               
               
               
             
           
               
                   
               
               
                 PROFILED 
                   
                   
                   
                   
                   
               
               
                 PARAMETERS 
                   
                 WRAP 
                   
                 VANE 
               
             
          
           
               
                 Ri 
                 RG 
                 Wrap 
                 Length 
                 Thick 
                 Height 
               
               
                 mm 
                 mm 
                 deg 
                 mm 
                 mm 
                 mm 
               
               
                   
               
             
          
           
               
                 Inner Profile 
               
             
          
           
               
                 9 
                 0 
                 158.67 
                 25 
                 — 
                 — 
               
               
                 25.653 
                 2.864789 
                 250 
                 140 
                 5 
                 21.41 
               
             
          
           
               
                 Outer Profile 
               
             
          
           
               
                 15 
                 0 
                 158.67 
                 42 
                 — 
                 — 
               
               
                 21.653 
                 2.864789 
                 430 
                 244 
                 5 
                 21.41 
               
               
                   
               
             
          
         
       
     
     As illustrated in the Figures, main bearing housing  524  and non-orbiting scroll member  568  are an integral component. Preferably, this component is machined from an iron casting and the advantages of having an integral non-orbiting scroll member  568  and main bearing housing  524  include that the bearing bore can be used as a fixture for the machining of non-orbiting scroll wrap  566 . By using the bearing bore as a fixture for machining the scroll wrap, the stack-up of tolerances are minimized, the radial compliance is minimized or reduced, and the bearing/gas/flank/axial forces are linked within a single component. 
     Compressor  510  is preferably a “high side” type, in which the volume defined by shell  512 , cap  514  and base  516  is at discharge pressure. In this way, discharge fitting  518  can be conveniently located on shell  512  or cap  514 . Inlet fitting  522  sealingly engages and extends through shell  512  and is sealingly received within non-orbiting scroll member  568  to provide gas at suction pressure to compressor  510 . 
     The description of the invention is merely exemplary in nature and, thus, variations that do not depart from the gist of the invention are intended to be within the scope of the invention. Such variations are not to be regarded as a departure from the spirit and scope of the invention.