Abstract:
A scroll compressor includes a compression mechanism contained within a shell. A non-orbiting scroll is supported for axial displacement relative the shell, and includes an end plate having a wrap extending therefrom and a flange having a bore extending therethrough. A guide member is axially fixed relative the shell and extends through the bore in the flange. A first portion of the guide member is disposed within and generally abuts a first circumferential portion of the bore. A second portion of the guide member is disposed within and generally spaced apart from a second circumferential portion of the bore.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application is a continuation of U.S. patent application Ser. No. 10/800,428 filed on Mar. 15, 2004 now U.S. Pat. No. 7,070,401. The disclosure of the above application is incorporated herein by reference. 
    
    
     FIELD 
     The present invention relates to mounting arrangements for the scroll member of a scroll machine. More particularly, the present invention relates to mounting one of the scroll members for axial compliance. 
     BACKGROUND AND SUMMARY 
     A class of machines exists in the art generally known as “scroll” machines for the displacement of various types of fluids. Such machines may be configured as an expander, a displacement engine, a pump, a compressor, etc., and the features of the present teachings are applicable to any one of these machines. For purposes of illustration, however, the disclosed embodiments are in the form of a hermetic refrigerant compressor. 
     Generally speaking, a scroll machine comprises two spiral scroll wraps of similar configuration, each mounted on a separate end plate to define a scroll member. The two scroll members are interfitted together with one of the scroll wraps being rotationally displaced 180° from the other. The machine operates by orbiting one scroll member (the “orbiting scroll”) with respect to the other scroll member (the “fixed scroll” or “non-orbiting scroll”) to make moving line contacts between the flanks of the respective wraps, defining moving isolated crescent-shaped pockets of fluid. The spirals are commonly formed as involutes of a circle, and ideally there is no relative rotation between the scroll members during operation; i.e., the motion is purely curvilinear translation (i.e., no rotation of any line in the body). The fluid pockets carry the fluid to be handled from a first zone in the scroll machine where a fluid inlet is provided, to a second zone in the machine where a fluid outlet is provided. The volume of a sealed pocket changes as it moves from the first zone to the second zone. At any one instant in time there will be at least one pair of sealed pockets; and where there are several pairs of sealed pockets at one time, each pair will have different volumes. In a compressor, the second zone is at a higher pressure than the first zone and is physically located centrally in the machine, the first zone being located at the outer periphery of the machine. 
     Two types of contacts define the fluid pockets formed between the scroll members, axially extending tangential line contacts between the spiral faces or flanks of the wraps caused by radial forces (“flank sealing”), and area contacts caused by axial forces between the plane edge surfaces (the “tips”) of each wrap and the opposite end plate (“tip sealing”). For high efficiency, good sealing must be achieved for both types of contacts; however, the present teachings are primarily concerned with tip sealing. 
     The concept of a scroll-type machine has thus been known for some time and has been recognized as having distinct advantages. For example, scroll machines have high isentropic and volumetric efficiency, and, hence, are relatively small and lightweight for a given capacity. They are quieter and more vibration free than many machines because they do not use large reciprocating parts (e.g., pistons, connecting rods, etc.); and because all fluid flow is in one direction with simultaneous compression in plural opposed pockets, there are less pressure-created vibrations. Such machines also tend to have high reliability and durability because of the relatively few moving parts utilized, the relatively low velocity of movement between the scrolls. Scroll machines which have compliance to allow tip leakage have an inherent forgiveness to fluid contamination. 
     One of the difficult areas of design in a scroll-type machine concerns the technique used to achieve tip sealing under all operating conditions, and also speeds in a variable speed machine. Conventionally, this has been accomplished by (1) using extremely accurate and very expensive machining techniques, (2) providing the wrap tips with spiral tip seals, which, unfortunately, are hard to assemble and often unreliable, or (3) applying an axially restoring force by axial biasing the orbiting scroll or the non-orbiting scroll towards the opposing scroll using compressed working fluid. The latter technique has some advantages but also presents problems, namely, in addition to providing a restoring force to balance the axial separating force, it is also necessary to balance the tipping moment on the scroll member due to pressure-generated radial forces which are dependent on suction and discharge pressures, as well as the inertial loads resulting from the orbital motion which is speed dependent. Thus, the axial balancing force must be relatively high, and will be optimal at only certain pressure and speed combinations. 
     The utilization of an axial restoring force requires one of the two scroll members to be mounted for axial movement with respect to the other scroll member. This can be accomplished by securing the non-orbiting scroll member to a main bearing housing by means of a plurality of bolts and a plurality of sleeve guides as disclosed in Assignee&#39;s U.S. Pat. No. 5,407,335, the disclosure of which is hereby incorporated herein by reference. In the mounting system which utilizes bolts and sleeve guides, arms formed on the non-orbiting scroll member are made to react against the sleeve guides. The sleeve guides hold the scroll member in proper alignment. The non-orbiting scroll member experiences gas forces in the radial and tangential direction whose centroid of application is at or near the mid-height of the scroll vane or wrap. The non-orbiting scroll member also experiences tip and base friction which can be randomly more on one than the other, but can be assumed as being equal and, therefore, having a centroid at or near the mid-height of the scroll wrap or vane. The non-orbiting scroll member additionally experiences flank contact forces from the centripetal acceleration of the orbiting scroll member which acts closer to the vane tip than at the base of the vane. All of these forces combine to yield a centroid of action which is located at a point just off the mid-height of the scroll wrap or vane toward the vane tip. 
     When the arms of the non-orbiting scroll member are located at the same elevation as the centroid of action of the forces experienced, the sleeve guides reaction could be equal and coplanar. When the arms are located near the tip of the vane of the non-orbiting scroll member, the reaction is not located at the centroid of action of the forces, it is offset from the centroid in a first direction. This offset produces a moment which reacts between the arm of the non-orbiting scroll member and the sleeve guide. Similarly, when the arms are located near the end plate of the non-orbiting scroll member, the reaction is again not located at the centroid of action of the forces, it is offset from the centroid in a second direction, opposite to the first direction. This offset also produces a moment which reacts between the arm of the non-orbiting scroll member and the sleeve guide. 
     Countering this moment is a moment produced by the hold-down force on the top of the non-orbiting scroll member, the axial gas separating force and the tip force pushing up on the vanes. The tip force can move to the radially outward most tip establishing a moment arm back to the centerline axis of the scroll wrap profile. The desire for high efficiency leads to a design with minimal tip load and, thus, the countering moment is of limited magnitude with no motivation to increase it. 
     In some scroll member designs, the sleeve guide reaction is so close to the non-orbiting scroll tip or so close to the non-orbiting end plate that it is far out of the plane of the centroid of action of the forces; and this causes the overturning moment to exceed the restoring moment. This causes the non-orbiting scroll member to rock up on one side, separating the tips from the bases of the scroll members on that side. This separation causes leakage which reduces the capacity of the compressor and, to a lesser extent, increases power. 
     The load which is applied to this sleeve guide tends to lean the sleeve guide away from the load. As this occurs, the load does not distribute evenly over the axial height of the non-orbiting scroll member arm, but it concentrates in the area near or away from the tip of the non-orbiting scroll member vane, near the bottom or top of the hole in the arm. This tendency increases the moment arm of the overturning moment. 
     A stepped geometry for the sleeve guide prevents contact between the arm of the non-orbiting scroll member and the sleeve guide at specific locations by reducing the diameter of the sleeve guide at that specific location. This concept allows the centroid of the reaction forces on the sleeve guide against the arms of the non-orbiting scroll member to be relocated from its normal axial position to a more preferred axial position. 
     In a first embodiment, the centroid of reaction of the sleeve guide focuses the centroid toward the top of the hole in the arm of the non-orbiting scroll member. This reduces the moment arm of the overturning moment for these scroll designs. The sleeve guide has a reduced diameter at a specified distance below the top of the sleeve, this distance being less than the axial height of the arm of the non-orbiting scroll member. 
     In another embodiment, the reduced diameter is located only at the mid-section of the sleeve guide. The reduction in diameter does not extend to either end of the sleeve guide. This enables the sleeve guide to be symmetrical so that it can be assembled with either end up to produce the same effect. 
     In another embodiment, the hole in the arm of the non-orbiting scroll member is machined as a stepped hole with the larger portion of the stepped hole being located nearest the vane tip. 
     In another embodiment, the centroid of reaction of the sleeve guide focuses the centroid toward the bottom of the hole in the arm of the non-orbiting scroll member. This reduces the moment arm of the overturning moment for these scroll designs. The sleeve guide has a reduced diameter at a specified distance above the top of the sleeve, this distance being less than the axial height of the arm of the non-orbiting scroll member. 
     In another embodiment, the reduced diameter is located only at the opposing ends of the sleeve guide. The reduction in diameter does not extend to the middle of the sleeve guide. This enables the sleeve guide to be symmetrical so that it can be assembled with either end up to produce the same effect. 
     In another embodiment, the hole in the arm of the non-orbiting scroll member is machined as a stepped hole with the larger portion of the stepped hole being located away from the vane tip. 
     In another embodiment, a scroll compressor includes a compression mechanism contained within a shell and including a non-orbiting scroll supported for axial displacement relative the shell and including an end plate having a wrap extending therefrom and a flange having a bore extending therethrough. A guide member may be axially fixed relative the shell and extend through the bore in the flange so that a first portion of the guide member is disposed within and generally abuts a first circumferential portion of the bore and a second portion of the guide member is disposed within and generally spaced apart from a second circumferential portion of the bore. 
     In another embodiment, a scroll compressor includes a compression mechanism contained within a shell and including a non-orbiting scroll supported for axial displacement relative the shell. The non-orbiting scroll includes an end plate having a wrap extending therefrom and a flange having a bore extending therethrough. A guide member is axially fixed relative the shell and extending through the bore in the flange. A first portion of the guide member is disposed within a circumferential portion of the bore and includes a first maximum width portion having a first width generally abutting the circumferential portion of the bore. A second portion of the guide member is disposed within the circumferential portion of the bore and includes a second maximum width portion having a second width generally less than the first width. 
     In another embodiment, a scroll compressor includes a compression mechanism contained within the shell and including a non-orbiting scroll supported for axial displacement relative the shell. The non-orbiting scroll includes an end plate having a wrap extending therefrom and a flange having a bore extending therethrough. A guide member is axially fixed relative the shell and extends through the bore in the flange. A first portion of the guide member is disposed within the bore, which includes first and second circumferential portions spaced axially apart from one another. The first circumferential portion generally abuts the guide member first portion at a first minimum width portion having a first width. The second circumferential portion includes a second minimum width portion having a second width generally greater than the first width, wherein the second circumferential portion is spaced radially apart from said guide member first portion to define a recess therebetween. 
     Further areas of applicability of the present teachings will become apparent from the detailed description provided hereinafter. It should be understood that the detailed description and specific examples are intended for purposes of illustration only and are not intended to limit the scope of the claims. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The present teachings will become more fully understood from the detailed description and the accompanying drawings, wherein: 
         FIG. 1  is a vertical cross-sectional view of a scroll compressor incorporating a non-orbiting scroll mounting arrangement; 
         FIG. 2  is a section view of the compressor of  FIG. 1 , the section being taken along line  2 - 2  thereof; 
         FIG. 3  is an enlarged fragmentary section view of the mounting arrangement shown in  FIG. 1 ; 
         FIGS. 4-11  are views similar to  FIG. 3 , but showing mounting arrangements in accordance with other embodiments; 
         FIG. 12  is a vertical cross-sectional view of a scroll compressor incorporating a non-orbiting scroll mounting arrangement in accordance with another embodiment; 
         FIG. 13  is a section view of the compressor of  FIG. 12 , the section being taken along line  13 - 13  thereof; 
         FIG. 14  is an enlarged fragmentary section view of the mounting arrangement shown in  FIG. 12 ; 
         FIGS. 15-22  are views similar to  FIG. 14 , but showing mounting arrangements in accordance with other embodiments; and 
         FIG. 23  is a vertical cross-section view of a scroll compressor incorporating a non-orbiting scroll mounting arrangement in accordance with another embodiment. 
     
    
    
     DETAILED DESCRIPTION 
     The following description of the preferred embodiment(s) is merely exemplary in nature and is in no way intended to limit the teachings, its application, or uses. 
     There is illustrated in  FIG. 1  a scroll compressor which incorporates a non-orbiting scroll mounting arrangement in accordance with the present teachings and which is designated generally by reference numeral  10 . Compressor  10  comprises a generally cylindrical hermetic shell  12  having welded at the upper end thereof a cap  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 the shell include a transversely extending partition  22  which is welded about its periphery at the same point that cap  14  is welded to shell  12 , a stationary main bearing housing or body  24  which is suitably secured to shell  12 , and a lower bearing housing  26  also having a plurality of radially outwardly extending legs, each of which is also suitably secured to shell  12 . A motor stator  28 , which is generally square in cross-section but with the corners rounded off, is pressfitted into shell  12 . The flats between the rounded corners on the stator provide passageways between the stator and shell, which facilitate the flow of lubricant from the top of the shell to the 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  and a second bearing  36  in lower bearing housing  26 . Crankshaft  30  has at the lower end a relatively large diameter concentric bore  38  which communicates with a radially outwardly inclined smaller diameter bore  40  extending upwardly therefrom to the top of the crankshaft. Disposed within bore  38  is a stirrer  42 . The lower portion of the interior shell  12  is filled with lubricating oil, and bore  38  acts as a pump to pump lubricating fluid up the crankshaft  30  and into passageway  40 , and ultimately to all of the various portions of the compressor which require lubrication. 
     Crankshaft  30  is rotatively driven by an electric motor including stator  28 , windings  44  passing therethrough and a rotor  46  pressfitted on the crankshaft  30  and having upper and lower counterweights  48  and  50 , respectively. A counterweight shield  52  may be provided to reduce the work loss caused by counterweight  50  spinning in the oil in the sump. Counterweight shield  52  is more fully disclosed in Assignee&#39;s U.S. Pat. No. 5,064,356 entitled “Counterweight Shield For Scroll Compressor,” the disclosure of which is hereby incorporated herein by reference. 
     The upper surface of main bearing housing  24  is provided with a flat thrust bearing surface on which is disposed an orbiting scroll member  54  having the usual spiral vane or wrap  56  on the upper surface thereof. Projecting downwardly from the lower surface of orbiting scroll member  54  is a cylindrical hub having a journal bearing  58  therein and in which is rotatively disposed a drive bushing  60  having an inner bore  62  in which crank pin  32  is drivingly disposed. Crank pin  32  has a flat on one surface which drivingly engages a flat surface (not shown) formed in a portion of bore  62  to provide a radially compliant driving arrangement, such as shown in aforementioned Assignee&#39;s U.S. Pat. No. 4,877,382, the disclosure of which is hereby incorporated herein by reference. An Oldham coupling  64  is also provided positioned between and keyed to orbiting scroll  54  and bearing housing  24  to prevent rotational movement of orbiting scroll member  54 . Oldham coupling  64  is preferably of the type disclosed in the above-referenced U.S. Pat. No. 4,877,382; however, the coupling disclosed in Assignee&#39;s U.S. Pat. No. 5,320,506 entitled “Oldham Coupling For Scroll Compressor”, the disclosure of which is hereby incorporated herein by reference, may be used in place thereof. 
     A non-orbiting scroll member  66  is also provided having a wrap  68  positioned in meshing engagement with wrap  56  of orbiting scroll member  54 . Non-orbiting scroll member  66  has a centrally disposed discharge passage  70  communicating with an upwardly open recess  72  which is in fluid communication with a discharge muffler chamber  74  defined by cap  14  and partition  22 . An annular recess  76  is also formed in non-orbiting scroll member  66  within which is disposed a seal assembly  78 . Recesses  72  and  76  and seal assembly  78  cooperate to define axial pressure biasing chambers which receive pressurized fluid being compressed by wraps  56  and  68  so as to exert an axial biasing force on non-orbiting scroll member  66  to thereby urge the tips of respective wraps  56 ,  68  into sealing engagement with the opposed end plate surfaces. Seal assembly  78  is preferably of the type described in greater detail in Assignee&#39;s U.S. Pat. No. 5,156,539, entitled “Scroll Machine With Floating Seal,” the disclosure of which is hereby incorporated herein by reference. Non-orbiting scroll member  66  is designed to be mounted to bearing housing  24  and to this end has a plurality of radially outwardly projecting flange portions  80  circumferentially spaced around the periphery thereof as shown in  FIG. 2 . 
     As best seen with reference to  FIG. 3 , flange portion  80  of non-orbiting scroll member  66  has an opening  82  provided therein within which is fitted an elongated cylindrical bushing  84 , the lower end  86  of which is seated on bearing housing  24 . Bushing  84  may form a guide member for non-orbiting scroll member  66 , as discussed below. A bolt  88  having a head washer  90  extends through an axially extending bore  92  provided in bushing  84  and into a threaded opening provided in bearing housing  24 . As shown, bore  92  of bushing  84  is of a diameter greater than the diameter of bolt  88  so as to accommodate some relative movement therebetween to enable final precise positioning of non-orbiting scroll member  66 . Once non-orbiting scroll member  66  and, hence, bushing  84  have been precisely positioned, bolt  88  may be suitably torqued thereby securely and fixedly clamping bushing  84  between bearing housing  24  and washer  90 . Washer  90  serves to ensure uniform circumferential loading on bushing  84  as well as to provide a bearing surface for the head of bolt  88  thereby avoiding any potential shifting of bushing  84  during the final torquing of bolt  88 . It should be noted that as shown in  FIG. 3 , the axial length of bushing  84  will be sufficient to allow non-orbiting scroll member  66  to slidably move axially along bushing  84  in a direction away from orbiting scroll member  54 , thereby affording an axially compliant mounting arrangement with washer  90  and the head of bolt  88  acting as a positive stop limiting such movement. Substantially identical bushings, bolts and washers are provided for each of the other flange portions  80 . The amount of separating movement can be relatively small (e.g., on the order of 0.005″ for a scroll 3″ to 4″ in diameter and 1″ to 2″ in wrap height) and, hence, the compressor will still operate to compress fluid even though the separating force resulting therefrom may exceed the axial restoring force such as may occur on start-up. Because the final radial and circumferential positioning of the non-orbiting scroll is accommodated by the clearances provided between bolts  88  and the associated bushings  84 , the threaded openings in bearing housing  24  need not be as precisely located as would otherwise be required, thus reducing the manufacturing costs associated therewith. 
     Bushings  84  include a large diameter portion  94  which provides a first clearance between bushing  84  and flange portion  80  and a small diameter portion  96  which provides a second clearance (or annular recess) between bushing  84  and flange portion  80 . The second clearance being greater than the first clearance. Large and small diameter portions  94 ,  96  may form first and second portions of bushing (or guide member)  84 . Large diameter portion  94  may include a greater width and/or perimeter than small diameter portion  96 . The relative diameters of large diameter portion  94  and the diameter of opening  82  will be such as to allow sliding movement therebetween yet effectively resist radial and/or circumferential movement of non-orbiting scroll member  66 . Large diameter portion  94  is located at the upper side or top of bushing  84  in order to move the centroid of reaction for bushing  84  away from the tip of wrap  68  of non-orbiting scroll member  66 . More specifically, a first plane may be defined at an end plate surface of non-orbiting scroll member  66  and a second plane may be defined at a tip of wrap  68  of non-orbiting scroll member  66 . Large diameter portion  94  may be located proximate to the second plane. 
     Alternatively, as shown in  FIG. 4 , the bolts  88  and bushings  84  may be replaced by a shoulder bolt  88 ′ having a shoulder portion  84 ′. In the example of  FIG. 4 , shoulder bolt  88 ′ may form a guide member for non-orbiting scroll member  66 . Shoulder portion  84 ′ of shoulder bolt  88 ′ includes a large diameter portion  94 ′ and a small diameter portion  96 ′. Large and small diameter portions  94 ′,  96 ′ may form first and second portions of shoulder bolt (or guide member)  88 ′. Large diameter portion  94 ′ may include a greater width and/or perimeter than small diameter portion  96 ′. Large diameter portion  94 ′ is located at the upper side or top of shoulder portion  84 ′ in order to move the centroid of reaction for shoulder portion  84 ′ of shoulder bolt  88 ′ away from the tip of wrap  68  of non-orbiting scroll member  66 . Large diameter portion  94 ′ may be located proximate to the second plane at the tip of wrap  68  discussed above. Large diameter portion  94 ′ of shoulder bolt  88 ′ is slidably fit within openings  82  provided in flange portions  80  of non-orbiting scroll member  66 . In this embodiment, the axial length “A” of shoulder portion  84 ′ of shoulder bolt  88 ′ will be selected such that a slight clearance will be provided between an integral washer  90 ′ of the head portion of bolt  88 ′ and the opposed surface of flange portion  80  when non-orbiting scroll member  66  is fully seated against orbiting scroll member  54  to thereby permit a slight axial separation movement in a like manner to that described above with reference to  FIG. 3 . Also, as noted above, integral washer  90 ′ of bolt  88 ′ will act as a positive stop to limit this axial separating movement of non-orbiting scroll member  66 . The relative diameters of large diameter portion  94 ′ and bore  82  will be such as to allow sliding movement therebetween, yet effectively resist radial and/or circumferential movement of non-orbiting scroll member  66 . While this embodiment eliminates concern over potential shifting of bushing  84  relative to bolt  88  which could occur in the embodiment of  FIG. 3 , it is somewhat more costly in that the threaded holes in bearing housing  24  must be precisely located. 
       FIG. 5  illustrates another embodiment of the present invention. In  FIG. 5 , a bushing  98  is pressfitted within each of the openings  82  provided in respective flange portions  80 . A stepped shoulder bolt  88 ″ is provided extending through bushing  98  and, as described above for  FIG. 4 , includes a shoulder portion  84 ″ having an axial length “B” selected with respect to the length of bushing  98  to afford the axial movement of non-orbiting scroll member  66 . In the example of  FIG. 5 , shoulder bolt  88 ″ may form a guide member for non-orbiting scroll member  66 . Shoulder portion  84 ″ of shoulder bolt  88 ″ includes a large diameter portion  94 ″ and a small diameter portion  96 ″. Large and small diameter portions  94 ″,  96 ″ may form first and second portions of shoulder bolt (or guide member)  88 ″. Large diameter portion  94 ″ may include a greater width and/or perimeter than small diameter portion  96 ″. Large diameter portion  94 ″ is located at the upper side or top of shoulder portion  84 ″ in order to move the centroid of reaction for shoulder portion  84 ″ of shoulder bolt  88 ″ away from the tip of wrap  68  of non-orbiting scroll member  66 . Large diameter portion  94 ″ may be located proximate to the second plane at the tip of wrap  68  discussed above. In this embodiment, because bushing  98  is pressfitted within opening  82 , it will slidably move along large diameter portion  94 ″ of shoulder portion  84 ″ of bolt  88 ″ along with non-orbiting scroll member  66  to afford the desired axially compliant mounting arrangement. This embodiment allows for somewhat less precise locating of the threaded bores in bearing housing  24  as compared to the embodiment of  FIG. 4  in that bushing  98  may be bored and/or reamed to provide the final precise positioning of non-orbiting scroll member  66 . Further, because the axial movement occurs between bushing  98  and shoulder bolt  88 ″, concern as to possible wearing of openings  82  provided in non-orbiting scroll member  66  is eliminated because any wear occurs between bushing  98  and shoulder bolt  88 ″. As shown, bushing  98  has an axial length such that it is seated on bearing housing  24  when non-orbiting scroll member  66  is fully seated against orbiting scroll member  54 ; however, if desired, a shorter bushing  98  could be utilized in place thereof. Again, as in the above-described embodiments, an integral washer  90 ″ of shoulder bolt  88 ″ will cooperate either with the end of bushing  98  or flange  80  as desired to provide a positive stop limiting axial separating movement of non-orbiting scroll member  66 . 
     In the embodiment of  FIG. 6 , a counterbore  100  is provided in bearing housing  24 . Counterbore  100  serves to receive small diameter portion  96 ′ of shoulder portion  84 ′ of bolt  88 ′ illustrated in  FIG. 4 . In the example of  FIG. 6 , shoulder bolt  88 ′ may form a guide member for non-orbiting scroll member  66 . Again, the axial length “C” of shoulder portion  84 ′ will be selected so as to allow for the desired limited axial movement of non-orbiting scroll member  66  and integral washer  90 ′ of bolt  88 ′ will provide a positive stop therefor. Because counterbore  100  can be reamed to establish the precise relative location of non-orbiting scroll member  66 , the tolerance for locating the threaded bore in bearing housing  24  may be increased somewhat. Further, this embodiment eliminates the need to provide and assemble separately fabricated bushings. Also, similarly to that described above, the relative diameters of large diameter portion  94 ′ of shoulder portion  88 ′ with respect to bore  82  in non-orbiting scroll member  66  will be such to accommodate axial sliding movement yet resist radial and circumferential movement. Similar to  FIG. 4 , large diameter portion  94 ′ is located at the upper side or top of shoulder portion  88 ′ in order to move the centroid of reaction for shoulder portion  84 ′ of shoulder bolt  88 ′ away from the tip of wrap  68  of non-orbiting scroll member  66 . Thus, the embodiment of  FIG. 6  is similar to the embodiment of  FIG. 4  and the description of  FIG. 4  applies to  FIG. 6 . 
     Referring now to  FIG. 7 , another embodiment of the present invention is illustrated. The embodiment illustrated in  FIG. 7  is the same as that described above for  FIG. 3  but in  FIG. 7 , bushing  84  includes two large diameter portions  94  and small diameter portion  96 . In the example of  FIG. 7 , bushing  84  may form a guide member for non-orbiting scroll member  66 . By incorporating two large diameter portions  94  at opposite sides of bushing  84 , bushing  84  becomes symmetrical, eliminating the need to orient bushing  84  during the assembly process. The description of  FIG. 3  above applies to  FIG. 7 , also with the only difference being the incorporation of the second large diameter portion  94 . 
     Referring now to  FIG. 8 , another embodiment of the present invention is illustrated. In the embodiment shown in  FIG. 8 , flange portion  80  of non-orbiting scroll member  66  has a stepped opening  182  provided therein within which is fitted an elongated cylindrical bushing  184 , the lower end of which is seated on bearing housing  24 . A bolt  88  having a head with a washer  90  extends through an axially extending bore  192  provided in bushing  184  and into the threaded opening provided in bearing housing  24 . In the example of  FIG. 8 , bushing  184  may form a guide member for non-orbiting scroll member  66 . As shown, bore  192  of bushing  184  is of a diameter greater than the diameter of bolt  88  so as to accommodate some relative movement therebetween to enable final precise positioning of non-orbiting scroll member  66 . Once non-orbiting scroll member  66 , and hence bushing  184 , have been precisely positioned, bolt  88  may be suitably torqued, thereby securely and fixedly clamping bushing  184  between bearing housing  24  and washer  90 . Washer  90  serves to ensure uniform circumferential loading on bushing  184 , as well as to provide a bearing surface for the head of bolt  88 , thereby avoiding any potential shifting of bushing  184  during the final torquing of bolt  88 . It should be noted that, as shown in  FIG. 8 , the axial length of bushing  184  will be sufficient to allow non-orbiting scroll member  66  to slidably move axially along bushing  184  in a direction away from the orbiting scroll member  54 , thereby affording the axially compliant mounting arrangement with washer  90  and the head of bolt  88  acting as a positive stop limiting such movement. Substantially identical bushings, bolts, washers and holes are provided for each of the other flange portions  80 . The amount of separating movement can be relatively small (e.g., on the order of 0.005″ for a scroll 3″ to 4″ in diameter and 1″ to 2″ in wrap height) and, hence, compressor  10  will still operate to compress even though the separating force resulting therefrom may exceed the axial restoring force such as may occur on start-up. Because the final radial and circumferential positioning of non-orbiting scroll member  66  is provided between bolts  88  and the associated bushings  184 , the threaded openings in bearing housing  24  need not be as precisely located as would otherwise be required, thus reducing the manufacturing costs associated therewith. 
     Stepped opening  182  includes a small diameter portion  194  and a large diameter portion  196 . Small and large diameter portions  194 ,  196  may form first and second circumferential portions of stepped opening  182 . Small diameter portion  194  may include a minimum width portion having a width less than a width of a minimum width portion of lame diameter portion  196 . The width of bushing  184  may be generally equal to the width of the minimum width portion of small diameter portion  194 . The relative diameters of small diameter portion  194  and the outside diameter of bushing  184  will be such as to allow sliding movement therebetween, yet effectively resist radial and/or circumferential movement of non-orbiting scroll member  66 . Small diameter portion  194  is located at the upper side or top of flange portion  80  in order to move the centroid of reaction for bushing  184  away from the top of wrap  68  of non-orbiting scroll member  66 . A clearance between large diameter portion  196  and bushing  184  may generally form a recess therebetween. 
     Alternatively, as shown in  FIG. 9 , bolts  88  and bushings  184  may be replaced by a shoulder bolt  188  slidably fit within stepped openings  182  provided in respective flange portions  80  of non-orbiting scroll member  66 . Stepped openings  182  includes small diameter portion  194  and large diameter portion  196 . In the example of  FIG. 9 , shoulder bolt  188  may form a guide member for non-orbiting scroll  66 . Small diameter portion  194  is located at the upper side or top of opening  182  in order to move the centroid of reaction for the shoulder portion of shoulder bolt  188  away from the tip of wrap  68  of non-orbiting scroll member  66 . In this embodiment, the axial length “A” of the shoulder portion of shoulder bolt  188  will be selected such that a slight clearance will be provided between the head portion of bolt  188  and the opposed surface of flange portion  80  when non-orbiting scroll member  66  is fully axially seated against orbiting scroll member  54  to thereby permit a slight axial separating movement in like manner as described above with reference to  FIG. 3 . Also, as noted above, the head of bolt  188  will act as a positive stop to limit this axial separating movement of non-orbiting scroll member  66 . The relative diameters of small diameter portion  194  of bore  182  and the outer diameter of the shoulder portion of bolt  188  will be such as to allow sliding movement therebetween, yet resist radial and/or circumferential movement of non-orbiting scroll member  66 . While this embodiment eliminates concern over potential shifting of the bushing relative to the securing bolt, which could occur in the embodiment of  FIG. 8 , it is somewhat more costly in that the threaded holes in bearing housing  24  must be precisely located. 
       FIG. 10  illustrates another embodiment of the present invention. In  FIG. 10 , a bushing  198  is pressfitted within each opening  82  provided in respective flange portions  80 . A shoulder bolt  188 ′ is provided extending through bushing  198  and, as described above, includes a shoulder portion having an axial length “B” selected with respect to the length of bushing  198  to afford the desired axial movement of non-orbiting scroll member  66 . In the example of  FIG. 10 , shoulder bolt  188 ′ may form a guide member for non-orbiting scroll member  66 . Bushing  198  includes a small diameter portion  194 ′ and a large diameter portion  196 ′. Small diameter portion  194 ′ is located at the upper side or top of opening  82  in order to move the centroid of reaction for the shoulder portion of bolt  188 ′ away from the tip of wrap  68  of non-orbiting scroll member  66 . In this embodiment, because bushing  198  is pressfitted within opening  82 , it will slidingly move along the shoulder portion of bolt  188 ′ along with non-orbiting scroll member  66  to afford the desired axially compliant mounting arrangement. Additionally, since bushing  198  is coupled to non-orbiting scroll member  66 , small and large diameter portions  194 ′,  196 ′ may define the first and second circumferential portions discussed above. This embodiment allows for somewhat less precise locating of the threaded bores in bearing housing  24  as compared to the embodiment of  FIG. 9  in that bushing  198  may be bored and/or reamed to provide the final precise positioning of non-orbiting scroll member  66 . Further, because the axial movement occurs between bushing  198  and shoulder bolt  188 ′, concerns as to possible wearing of openings  82  provided in non-orbiting scroll member  66  is eliminated because any wear occurs between bushing  198  and shoulder bolt  188 ′. As shown, bushing  198  has an axial length such that it is seated on bearing housing  24  when non-orbiting scroll member  66  is fully seated against orbiting scroll member  54 ; however, if desired, a shorter bushing  198  could be utilized in place thereof. Again, as in the above-described embodiments, an integral washer  190 ′ of shoulder bolt  188 ′ will cooperate either with the end of bushing  198  or flange  80  as desired to provide a positive stop limiting axial separating movement of non-orbiting scroll member  66 . 
     In the embodiment of  FIG. 11 , a counterbore  200  is provided in bearing housing  24 . Counterbore  200  serves to receive the shoulder portion of bolt  188 . Again, the axial length “C” of the shoulder portion of bolt  188  will be selected so as to allow for the desired limited axial movement of non-orbiting scroll member  66  and integral washer  190  of bolt  188  will provide a positive stop therefore. Bolt  188  may form a guide member for non-orbiting scroll member  66 . Because counterbore  200  can be reamed to establish the precise relative location of non-orbiting scroll member  66 , the tolerance for locating the threaded bore of bearing housing  24  may be increased somewhat. Further, this embodiment eliminates the need to provide and assemble separately fabricated bushings. Also similarly to that described above, the relative diameters of the shoulder portion of bolt  188  with respect to small diameter portion  194  of stepped opening  182  in non-orbiting scroll member  66  will be such to accommodate axial sliding movement, yet resist radial and circumferential movement. Similar to  FIG. 9 , small diameter portion  194  is located at the upper side or top of stepped opening  182  in order to move the centroid of reaction for shoulder bolt  188  away from the tip of wrap  68  of non-orbiting scroll member  66 . Thus, the embodiment of  FIG. 11  is similar to the embodiment of  FIG. 9 , and the description of  FIG. 9  applies to  FIG. 11 . 
     Referring now to  FIGS. 12-14 , a scroll compressor which incorporates a non-orbiting scroll mounting arrangement in accordance with another embodiment of the present invention is illustrated and is designated generally by reference numeral  310 . Scroll compressor  310  is the same as scroll compressor  10  except that non-orbiting scroll member  66  is replaced by non-orbiting scroll member  366  and the mounting arrangement for non-orbiting scroll member  366 . 
     Non-orbiting scroll member  366  is also provided having wrap  68  positioned in meshing engagement with wrap  56  of orbiting scroll member  54 . Non-orbiting scroll member  366  may define a first plane at an end plate surface thereof and a second plane at a tip of wrap  68 . Non-orbiting scroll member  366  has centrally disposed discharge passage  70  communicating with upwardly open recess  72  which is in fluid communication with discharge muffler chamber  74  defined by cap  14  and partition  22 . Annular recess  76  is also formed in non-orbiting scroll member  366  within which is disposed seal assembly  78 . Recesses  72  and  76  and seal assembly  78  cooperate to define axial pressure biasing chambers which receive pressurized fluid being compressed by wraps  56  and  68  so as to exert an axial biasing force on non-orbiting scroll member  366  to thereby urge the tips of respective wraps  56 ,  68  into sealing engagement with the opposed end plate surfaces. Non-orbiting scroll member  366  is designed to be mounted to bearing housing  24  and to this end has a plurality of radially outwardly projecting flange portions  380  circumferentially spaced around the periphery thereof as shown in  FIG. 13 . 
     As best seen with reference to  FIG. 14 , flange portion  380  of non-orbiting scroll member  366  has an opening  382  provided therein within which is fitted an elongated cylindrical bushing  384 , the lower end  386  of which is seated on bearing housing  24 . Bushing  384  may form a guide member for non-orbiting scroll member  366 . A bolt  388  having a head washer  390  extends through an axially extending bore  392  provided in bushing  384  and into a threaded opening provided in bearing housing  24 . As shown, bore  392  of bushing  384  is of a diameter greater than the diameter of bolt  388  so as to accommodate some relative movement therebetween to enable final precise positioning of non-orbiting scroll member  366 . Once non-orbiting scroll member  366  and, hence, bushing  384  have been precisely positioned, bolt  388  may be suitably torqued thereby securely and fixedly clamping bushing  384  between bearing housing  24  and washer  390 . Washer  390  serves to ensure uniform circumferential loading on bushing  384  as well as to provide a bearing surface for the head of bolt  388  thereby avoiding any potential shifting of bushing  384  during the final torquing of bolt  388 . It should be noted that as shown in  FIG. 14 , the axial length of bushing  384  will be sufficient to allow non-orbiting scroll member  366  to slidably move axially along bushing  384  in a direction away from orbiting scroll member  54 , thereby affording an axially compliant mounting arrangement with washer  390  and the head of bolt  388  acting as a positive stop limiting such movement. Substantially identical bushings, bolts and washers are provided for each of the other flange portions  380 . The amount of separating movement can be relatively small (e.g., on the order of 0.005″ for a scroll 3″ to 4″ in diameter and 1″ to 2″ in wrap height) and, hence, the compressor will still operate to compress even though the separating force resulting therefrom may exceed the axial restoring force such as may occur on start-up. Because the final radial and circumferential positioning of the non-orbiting scroll is accommodated by the clearances provided between bolts  388  and the associated bushings  384 , the threaded openings in bearing housing  24  need not be as precisely located as would otherwise be required, thus reducing the manufacturing costs associated therewith. 
     Bushings  384  include a large diameter portion  394  and a small diameter portion  396 . The relative diameters of large diameter portion  394  and the diameter of opening  382  will be such as to allow sliding movement therebetween yet effectively resist radial and/or circumferential movement of non-orbiting scroll member  366 . Large diameter portion  394  is located at the lower side or bottom of bushing  384  in order to move the centroid of reaction for bushing  384  toward the tip of wrap  68  of non-orbiting scroll member  366 . Large diameter portion  394  may be located proximate to the first plane discussed above. 
     Alternatively, as shown in  FIG. 15 , the bolts  388  and bushings  384  may be replaced by a shoulder bolt  388 ′ having a shoulder portion  384 ′. Shoulder portion  384 ′ of shoulder bolt  388 ′ includes a large diameter portion  394 ′ and a small diameter portion  396 ′. In the example of  FIG. 15 , shoulder bolt  388 ′ may form a guide member for non-orbiting scroll member  366 . Large diameter portion  394 ′ is located at the lower side or bottom of shoulder portion  384 ′ in order to move the centroid of reaction for shoulder portion  384 ′ of shoulder bolt  388 ′ toward the tip of wrap  68  of non-orbiting scroll member  366 . Large diameter portion  394 ′ of shoulder bolt  388 ′ is slidably fit within openings  382  provided in flange portions  380  of non-orbiting scroll member  366 . In this embodiment, the axial length “A” of shoulder portion  384 ′ of shoulder bolt  388 ′ will be selected such that a slight clearance will be provided between an integral washer  390 ′ of the head portion of bolt  388 ′ and the opposed surface of flange portion  380  when non-orbiting scroll member  366  is fully seated against orbiting scroll member  54  to thereby permit a slight axial separation movement in a like manner to that described above with reference to  FIG. 14 . Also, as noted above, integral washer  390 ′ of bolt  388 ′ will act as a positive stop to limit this axial separating movement of non-orbiting scroll member  366 . The relative diameters of large diameter portion  394 ′ and bore  382  will be such as to allow sliding movement therebetween, yet effectively resist radial and/or circumferential movement of non-orbiting scroll member  366 . While this embodiment eliminates concern over potential shifting of bushing  384  relative to bolt  388  which could occur in the embodiment of  FIG. 14 , it is somewhat more costly in that the threaded holes in bearing housing  24  must be precisely located. 
       FIG. 16  illustrates another embodiment of the present invention. In  FIG. 16 , a bushing  398  is pressfitted within each of the openings  382  provided in respective flange portions  380 . A stepped shoulder bolt  388 ″ is provided extending through bushing  398  and, as described above for  FIG. 15 , includes a shoulder portion  384 ″ having an axial length “B” selected with respect to the length of bushing  398  to afford the axial movement of non-orbiting scroll member  366 . In the example of  FIG. 16 , shoulder bolt  388 ″ may form a guide member for non-orbiting scroll member  366 . Shoulder portion  384 ″ of shoulder bolt  388 ″ includes a large diameter portion  394 ″ and a small diameter portion  396 ″. Large diameter portion  394 ″ is located at the lower side or bottom of shoulder portion  384 ″ in order to move the centroid of reaction for shoulder portion  384 ″ of shoulder bolt  388 ″ toward the tip of wrap  68  of non-orbiting scroll member  366 . In this embodiment, because bushing  398  is pressfitted within opening  382 , it will slidably move along large diameter portion  394 ″ of shoulder portion  384 ″ of bolt  388 ″ along with non-orbiting scroll member  366  to afford the desired axially compliant mounting arrangement. Additionally, since bushing  398  is coupled to non-orbiting scroll member  366 , large and small diameter portions  394 ″,  396 ″ may define the first and second circumferential portions discussed above. This embodiment allows for somewhat less precise locating of the threaded bores in bearing housing  24  as compared to the embodiment of  FIG. 15  in that bushing  398  may be bored and/or reamed to provide the final precise positioning of non-orbiting scroll member  366 . Further, because the axial movement occurs between bushing  398  and shoulder bolt  388 ″, concern as to possible wearing of openings  382  provided in non-orbiting scroll member  366  is eliminated because any wear occurs between bushing  398  and shoulder bolt  388 ″. As shown, bushing  398  has an axial length such that it is seated on bearing housing  24  when non-orbiting scroll member  366  is fully seated against orbiting scroll member  54 ; however, if desired, a shorter bushing  398  could be utilized in place thereof. Again, as in the above-described embodiments, an integral washer  390 ″ of shoulder bolt  388 ″ will cooperate either with the end of bushing  398  or flange  380  as desired to provide a positive stop limiting axial separating movement of non-orbiting scroll member  366 . 
     In the embodiment of  FIG. 17 , a counterbore  400  is provided in bearing housing  24 . Counterbore  400  serves to receive large diameter portion  394 ′ of shoulder portion  384 ′ of bolt  388 ′ illustrated in  FIG. 15 . In the example of  FIG. 17 , bolt  388 ′ may form a guide member for non-orbiting scroll member  366 . Again, the axial length “C” of shoulder portion  384 ′ will be selected so as to allow for the desired limited axial movement of non-orbiting scroll member  366  and integral washer  390 ′ of bolt  388 ′ will provide a positive stop therefor. Because counterbore  400  can be reamed to establish the precise relative location of non-orbiting scroll member  366 , the tolerance for locating the threaded bore in bearing housing  24  may be increased somewhat. Further, this embodiment eliminates the need to provide and assemble separately fabricated bushings. Also, similarly to that described above, the relative diameters of large diameter portion  394 ′ of shoulder portion  388 ′ with respect to bore  382  in non-orbiting scroll member  366  will be such to accommodate axial sliding movement yet resist radial and circumferential movement. Similar to  FIG. 15 , large diameter portion  394 ′ is located at the lower side or bottom of shoulder portion  388 ′ in order to move the centroid of reaction for shoulder portion  384 ′ of shoulder bolt  388 ′ toward the tip of wrap  68  of non-orbiting scroll member  366 . Thus, the embodiment of  FIG. 17  is similar to the embodiment of  FIG. 15  and the description of  FIG. 15  applies to  FIG. 17 . 
     Referring now to  FIG. 18 , another embodiment of the present invention is illustrated. The embodiment illustrated in  FIG. 18  is the same as that described above for  FIG. 14  but in  FIG. 18 , bushing  384  includes two small diameter portions  396  and large diameter portion  394 . In the example of  FIG. 18 , bushing  384  may form a guide member for non-orbiting scroll member  366 . By incorporating two large diameter portions  396  at opposite sides of bushing  384 , bushing  384  becomes symmetrical, eliminating the need to orient bushing  384  during the assembly process. The description of  FIG. 14  above applies to  FIG. 18  also with the only difference being the incorporation of the second small diameter portion  396 . 
     Referring now to  FIG. 19 , another embodiment of the present invention is illustrated. In the embodiment shown in  FIG. 19 , flange portion  380  of non-orbiting scroll member  366  has a stepped opening  482  provided therein within which is fitted an elongated cylindrical bushing  484 , the lower end of which is seated on bearing housing  24 . In the example of  FIG. 19 , bushing  484  may form a guide member for non-orbiting scroll member  366 . A bolt  388  having a head with a washer  390  extends through an axially extending bore  492  provided in bushing  484  and into the threaded opening provided in bearing housing  24 . As shown, bore  492  of bushing  484  is of a diameter greater than the diameter of bolt  388  so as to accommodate some relative movement therebetween to enable final precise positioning of non-orbiting scroll member  366 . Once non-orbiting scroll member  366 , and hence bushing  484 , have been precisely positioned, bolt  388  may be suitably torqued, thereby securely and fixedly clamping bushing  484  between bearing housing  24  and washer  390 . Washer  390  serves to ensure uniform circumferential loading on bushing  484 , as well as to provide a bearing surface for the head of bolt  388 , thereby avoiding any potential shifting of bushing  484  during the final torquing of bolt  388 . It should be noted that, as shown in  FIG. 19 , the axial length of bushing  484  will be sufficient to allow non-orbiting scroll member  366  to slidably move axially along bushing  484  in a direction away from the orbiting scroll member  54 , thereby affording the axially compliant mounting arrangement with washer  390  and the head of bolt  388  acting as a positive stop limiting such movement. Substantially identical bushings, bolts, washers and holes are provided for each of the other flange portions  380 . The amount of separating movement can be relatively small (e.g., on the order of 0.005″ for a scroll 3″ to 4″ in diameter and 1″ to 2″ in wrap height) and, hence, compressor  10  will still operate to compress even though the separating force resulting therefrom may exceed the axial restoring force such as may occur on start-up. Because the final radial and circumferential positioning of non-orbiting scroll member  366  is provided between bolts  388  and the associated bushings  484 , the threaded openings in bearing housing  24  need not be as precisely located as would otherwise be required, thus reducing the manufacturing costs associated therewith. 
     Stepped opening  482  includes a small diameter portion  494  and a large diameter portion  496 , forming first and second circumferential portions thereof. The relative diameters of small diameter portion  494  and the outside diameter of bushing  484  will be such as to allow sliding movement therebetween, yet effectively resist radial and/or circumferential movement of non-orbiting scroll member  366 . Small diameter portion  494  is located at the lower side or bottom of flange portion  380  in order to move the centroid of reaction for bushing  484  toward the top of wrap  68  of non-orbiting scroll member  366 . 
     Alternatively, as shown in  FIG. 20 , bolts  380  and bushings  484  may be replaced by a shoulder bolt  488  slidably fit within stepped openings  482  provided in respective flange portions  380  of non-orbiting scroll member  366 . In the example of  FIG. 20 , shoulder bolt  488  may form a guide member for non-orbiting scroll member  366 . Stepped openings  482  includes small diameter portion  494  and large diameter portion  496 . Small diameter portion  494  is located at the lower side or bottom of opening  482  in order to move the centroid of reaction for the shoulder portion of shoulder bolt  488  toward the tip of wrap  68  of non-orbiting scroll member  366 . In this embodiment, the axial length “A” of the shoulder portion of shoulder bolt  488  will be selected such that a slight clearance will be provided between the head portion of bolt  488  and the opposed surface of flange portion  380  when non-orbiting scroll member  366  is fully axially seated against orbiting scroll member  54  to thereby permit a slight axial separating movement in like manner as described above with reference to  FIG. 14 . Also, as noted above, the head of bolt  488  will act as a positive stop to limit this axial separating movement of non-orbiting scroll member  366 . The relative diameters of small diameter portion  494  of bore  482  and the outer diameter of the shoulder portion of bolt  488  will be such as to allow sliding movement therebetween, yet resist radial and/or circumferential movement of non-orbiting scroll member  366 . While this embodiment eliminates concern over potential shifting of the bushing relative to the securing bolt, which could occur in the embodiment of  FIG. 19 , it is somewhat more costly in that the threaded holes in bearing housing  24  must be precisely located. 
       FIG. 21  illustrates another embodiment of the present invention. In  FIG. 21 , a bushing  498  is pressfitted within each opening  382  provided in respective flange portions  380 . A shoulder bolt  488 ′ is provided extending through bushing  498  and, as described above, includes a shoulder portion having an axial length “B” selected with respect to the length of bushing  498  to afford the desired axial movement of non-orbiting scroll member  366 . In the example of  FIG. 21 , shoulder bolt  488 ′ may form a guide member for non-orbiting scroll member  366 . Bushing  498  includes a small diameter portion  494 ′ and a large diameter portion  496 ′. Small diameter portion  494 ′ is located at the lower side or bottom of opening  382  in order to move the centroid of reaction for the shoulder portion of bolt  488 ′ toward the tip of wrap  68  of non-orbiting scroll member  366 . In this embodiment, because bushing  498  is pressfitted within opening  382 , it will slidingly move along the shoulder portion of bolt  488 ′ along with non-orbiting scroll member  366  to afford the desired axially compliant mounting arrangement. Additionally, since bushing  498  is coupled to non-orbiting scroll member  366 , small and large diameter portions  494 ′,  496 ′ may define first and second circumferential portions of flanged portion  380 . This embodiment allows for somewhat less precise locating of the threaded bores in bearing housing  24  as compared to the embodiment of  FIG. 20  in that bushing  498  may be bored and/or reamed to provide the final precise positioning of non-orbiting scroll member  366 . Further, because the axial movement occurs between bushing  498  and shoulder bolt  488 ′, concerns as to possible wearing of openings  382  provided in non-orbiting scroll member  366  is eliminated because any wear occurs between bushing  498  and shoulder bolt  488 ′. As shown, bushing  498  has an axial length such that it is seated on bearing housing  24  when non-orbiting scroll member  366  is fully seated against orbiting scroll member  54 , however, if desired, a shorter bushing  498  could be utilized in place thereof. Again, as in the above-described embodiments, an integral washer  490 ′ of shoulder bolt  488 ′ will cooperate either with the end of bushing  498  or flange  380  as desired to provide a positive stop limiting axial separating movement of non-orbiting scroll member  366 . 
     In the embodiment of  FIG. 22 , a counterbore  500  is provided in bearing housing  24 . Counterbore  500  serves to receive the shoulder portion of bolt  488 . In the example of  FIG. 22 , bolt  488  may form a guide member for non-orbiting scroll member  366 . Again, the axial length “C” of the shoulder portion of bolt  488  will be selected so as to allow for the desired limited axial movement of non-orbiting scroll member  366  and integral washer  490  of bolt  488  will provide a positive stop therefore. Because counterbore  500  can be reamed to establish the precise relative location of non-orbiting scroll member  366 , the tolerance for locating the threaded bore of bearing housing  24  may be increased somewhat. Further, this embodiment eliminates the need to provide and assemble separately fabricated bushings. Also similarly to that described above, the relative diameters of the shoulder portion of bolt  480  with respect to small diameter portion  494  of bore  482  in non-orbiting scroll member  366  will be such to accommodate axial sliding movement, yet resist radial and circumferential movement. Similar to  FIG. 20 , small diameter portion  494  is located at the lower side or bottom of bore  482  in order to move the centroid of reaction for shoulder bolt  488  toward the tip of wrap  68  of non-orbiting scroll member  366 . Thus, the embodiment of  FIG. 22  is similar to the embodiment of  FIG. 20 , and the description of  FIG. 20  applies to  FIG. 22 . 
     Referring now to  FIG. 23 , a scroll compressor which incorporates a non-orbiting scroll mounting arrangement in accordance with another embodiment of the present invention is illustrated and is designated generally by reference numeral  510 . Scroll compressor  510  is the same as scroll compressor  10  except that non-orbiting scroll member  66  is replaced by non-orbiting scroll member  66  is replaced by non-orbiting scroll member  566  and the mounting arrangement for non-orbiting scroll member  566 . 
     Non-orbiting scroll member  566  is also provided having wrap  68  positioned in meshing engagement with wrap  56  of orbiting scroll member  54 . Non-orbiting scroll member  566  may define a first plane at an end plate surface thereof and a second plane at a tin of wrap  68 . Non-orbiting scroll member  566  has centrally disposed discharge passage  70  communicating with upward open recess  72  which is in fluid communication with discharge muffler chamber  74  defined by cap  14  and partition  22 . Annular recess  76  is also formed in non-orbiting scroll member  566  within which is disposed seal assembly  78 . Recess  72  and  76  and seal assembly  78  cooperate to define axial pressure biasing chambers which receive pressurized fluid being compressed by wraps  56  and  68  so as to exert to axial biasing force on non-orbiting scroll member  566  to thereby urge the tips of respective wraps  56 ,  68  into sealing engagement with the opposed end plate surfaces. Non-orbiting scroll member  566  is designed to be mounted to bearing housing  24  and to this end has a plurality of radially outwardly projecting flange portions  580  circumferentially spaced around the periphery thereof in the same manner as flange portions  380  illustrated in  FIG. 13 . 
     The axial centerline for outwardly projecting flange portions  580  is positioned at the centroid of reaction for flange portions  580  and thus there is no need to provide a stepped bushing to move the centroid of reaction. Flange portions  580  may be located axially between the first and second planes discussed above. Each flange portion  580  is provided with a circular cylindrical bushing  584  disposed within a bore  585  extending through flange  580 . 
     The function, operation and advantages of compressor  510  are the same as those detailed above for compressor  10 . 
     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.