Abstract:
In order to improve a compressor for refrigerant, comprising an outer housing, a scroll compressor arranged in the outer housing and having a first compressor member arranged stationarily in the outer housing and a second compressor member which is movable relative to the first compressor member, the compressor members each having a base and first and second scroll ribs, respectively, which rise above the respective base and engage in one another such that the second compressor member is movable relative to the first compressor member on an orbital path about a central axis for the purpose of compressing the refrigerant, a drive unit for the second compressor member having an eccentric drive, a drive shaft, a drive motor arranged in a motor housing and having drawn-in refrigerant flowing around it as well as a bearing unit for the drive shaft which comprises a first bearing member connected to the outer housing, in such a manner that the refrigerant drawn in by the scroll compressor is free from lubricating oil to as great an extent as possible it is suggested that the refrigerant flow through an oil separator, which is arranged in the outer housing between this and the drive unit, after flowing around the drive motor and prior to entering the scroll compressor.

Description:
[0001]    The present disclosure relates to the subject matter disclosed in German application No. 102 48 926.2 of Oct. 15, 2002, which is incorporated herein by reference in its entirety and for all purposes.  
         BACKGROUND OF THE INVENTION  
         [0002]    The invention relates to a compressor for refrigerant, comprising an outer housing, a scroll compressor arranged in the outer housing and having a first compressor member arranged stationarily in the outer housing and a second compressor member movable relative to the first compressor member, these compressor members each having a base and first and second scroll ribs, respectively, which rise above the respective base and engage in one another such that the second compressor member is movable relative to the first compressor member on an orbital path about a central axis for the purpose of compressing the refrigerant, a drive unit for the second compressor member with an eccentric drive, a drive shaft, a drive motor arranged in a motor housing and having drawn-in refrigerant flowing around it as well as a bearing unit for the drive shaft which comprises a first bearing member connected to the outer housing.  
           [0003]    A compressor of this type is known, for example, from U.S. Pat. No. 4,564,339. The problem with compressors of this type is that oil carried along by the refrigerant which is drawn in still enters the scroll compressor and leads to problems in it.  
           [0004]    The object underlying the invention is, therefore, to improve a compressor of the generic type in such a manner that the refrigerant drawn in by the scroll compressor is free from lubricating oil to as great an extent as possible.  
         SUMMARY OF THE INVENTION  
         [0005]    This object is accomplished in accordance with the invention, in a compressor of the type described at the outset, in that the refrigerant flows through an oil separator, which is arranged in the outer housing between this and the drive unit, after flowing around the drive motor and prior to entering the scroll compressor.  
           [0006]    The advantage of this solution is to be seen in the fact that a possibility has been created, as a result of this additional oil separator, of separating the oil already carried along with the refrigerant drawn in and also the oil entrained by the refrigerant whilst flowing through the drive motor to a sufficiently large extent prior to it entering the scroll compressor in order to avoid the problems in the scroll compressor caused by oil.  
           [0007]    With respect to as compact a construction of the inventive compressor as possible, it has proven to be advantageous when the oil separator is arranged in a space located between the outer housing and the drive unit in a direction transverse to the central axis since the constructional length, in particular, of the compressor is not altered as a result.  
           [0008]    Furthermore, it has proven to be particularly advantageous when the space between the outer housing and the drive unit extends essentially over the entire extension of the drive unit in a direction parallel to the central axis.  
           [0009]    As a result, the space could still be arranged on one side of the drive unit. With respect to available space which is as large as possible, it is particularly expedient when the space surrounds the drive unit and, therefore, extends around the drive unit on all sides in order to obtain an optimum utilization of free space in the outer housing.  
           [0010]    The space is, in this respect, used not only for the arrangement of the oil separator but rather, preferably, in many ways. An expedient solution provides for oil separated by the oil separator in the space to move in the direction of the oil sump and for refrigerant to flow in the direction of an intake chamber of the scroll compressor. Such an arrangement utilizing the space in various ways allows a particularly compact construction of the inventive compressor.  
           [0011]    With respect to the guidance of the refrigerant, it has proven to be particularly expedient when the refrigerant enters the space after cooling the drive motor.  
           [0012]    With respect to as favorable an arrangement of the oil separator as possible, it is provided for the oil separator to be arranged, at least in sections, on an outer side of the first bearing member since, in this area, suitable space is available.  
           [0013]    The oil separator may be arranged in a particularly favorable manner when it surrounds the first bearing member at least in sections.  
           [0014]    A further, favorable arrangement in addition or alternatively to the arrangement of the oil separator on the outer side of the bearing member provides for the oil separator to be arranged, at least in sections, on an outer side of the motor housing since, in this area, a lot of space can be made available without considerably increasing the constructional size of the compressor. In this respect, it is particularly advantageous when the oil separator surrounds the motor housing at least in sections.  
           [0015]    With respect to the actual design of the oil separator, one preferred embodiment provides for the oil separator to use part of the space located between the outer housing and the drive unit.  
           [0016]    It has proven to be particularly favorable when the space between the outer housing and the drive unit used by the oil separator is an annular space.  
           [0017]    With respect to the arrangement of the oil separator in the space, no further details have so far been given. It is preferably provided, for example, for the oil separator to be located on a side facing an oil sump of supporting arms which connect the first bearing member to the outer housing in order to arrange the oil separator in a favorable manner at an adequately large distance from the intake chamber of the scroll compressor.  
           [0018]    Furthermore, it is particularly favorable when the oil separator is arranged in front of an exit opening for the refrigerant provided in the motor housing in order to achieve a good utilization of space.  
           [0019]    With respect to the guidance of the refrigerant in the oil separator, no further details have been given in conjunction with the preceding explanations concerning the individual embodiments. One particularly favorable solution provides for the refrigerant to experience a deflection in an azimuthal direction in relation to the central axis when entering the oil separator since, as a result, a particularly effective separation of oil is brought about due to the forces acting on the drops of oil and extending transversely to the direction of flow.  
           [0020]    It is particularly favorable when the refrigerant experiences the deflection in the at least one azimuthal direction as a result of a deflection element. One particularly advantageous solution provides for the refrigerant to experience a deflection in opposite azimuthal directions.  
           [0021]    It is, moreover, favorable for the further, optimum separation of oil when the refrigerant is guided in the oil separator essentially on an azimuthal path around the central axis.  
           [0022]    One embodiment of an oil separator which is particularly simple from a constructional point of view provides for the refrigerant to flow in the oil separator along an inner wall surface of the outer housing and, therefore, always be deflected in an azimuthal direction in relation to the central axis, in particular, in the case of a cylindrical outer housing.  
           [0023]    A particularly simple guidance of the oil deposited in the oil separator provides for the oil settling in the oil separator to move into the oil sump on a path extending outside the motor housing in order to prevent the refrigerant cooling the drive motor from again picking up oil and transporting it to the oil separator.  
           [0024]    With respect to the arrangement of the oil sump, no further details have so far been given. The inventive compressor is advantageously designed as a compressor working with a central axis aligned essentially vertical so that the oil sump is arranged in the outer housing on a side of the drive motor located opposite the first bearing member.  
           [0025]    With respect to the arrangement of the oil separator, no further details have so far been given. One particularly favorable solution provides, for example, for the refrigerant to flow around an outer side of the first bearing member on its way from the oil separator to the intake chamber of the scroll compressor in order to cool the first bearing member. In this respect, a large distance between the intake chamber and the oil separator can also preferably be realized.  
           [0026]    A particularly favorable solution provides for the oil separator to be located on a side facing an oil sump of supporting arms which connect the first bearing member to the outer housing.  
           [0027]    A particularly favorable embodiment with respect to the guidance of the refrigerant provides for the refrigerant to pass between the supporting arms in the direction of the intake chamber of the scroll compressor after flowing through the oil separator.  
           [0028]    With respect to the guidance of the refrigerant drawn in by the compressor in the compressor itself, no further details have so far been given. It would, for example, be conceivable to have the refrigerant enter the outer housing first of all and then to guide it to the motor housing via indirect routes.  
           [0029]    It has, however, proven to be particularly advantageous when the refrigerant flows directly into the motor housing when entering the compressor and enters the oil separator after flowing through the motor housing. As a result, it is possible to introduce the refrigerant into the motor housing in a concerted manner and avoid additional indirect routes.  
           [0030]    In this respect, it is particularly favorable when the refrigerant entering the motor housing experiences a deflection in at least one azimuthal direction.  
           [0031]    It is even better when the refrigerant experiences a deflection in opposite azimuthal directions and, therefore, flows through an interior space of the motor housing as a result of azimuthal flows extending in opposite directions.  
           [0032]    With respect to an optimum cooling effect in the drive motor, it has proven to be particularly expedient when the refrigerant enters the motor housing at the level of a first winding head when seen in the direction of the central axis.  
           [0033]    The refrigerant is expediently guided in the motor housing, when seen in the direction of the central axis, such that it flows through the drive motor from the first winding head in the direction of a second winding head.  
           [0034]    In order to guide the refrigerant as favorably as possible it is provided for the refrigerant to exit from the motor housing at the level of the second winding head when seen in the direction of the central axis.  
           [0035]    With this solution it is not described in greater detail where the first winding head and the second winding head are located.  
           [0036]    With one inventive solution, the first winding head is arranged such that this is the winding head of the drive motor which is located on a side facing away from the first bearing member whereas in another embodiment the winding head is the winding head of the drive motor which is located on a side facing the first bearing member.  
           [0037]    With respect to the guidance of oil separating in the motor housing to the oil sump, no further details have so far been given. One advantageous solution provides, for example, for oil separating in the motor housing to exit from the motor housing through oil discharge openings of a second bearing member which forms a base of the motor housing in order to reach the oil sump.  
           [0038]    In order, in addition, to also drain off oil running out of the eccentric drive on account of the lubrication in a concerted manner, it is preferably provided for the first bearing member to have an oil guide means for oil used for the lubrication of the eccentric drive.  
           [0039]    This oil guide means may be designed in the most varied of ways. One advantageous solution, for example, provides for the oil guide means to open into an interior space of the motor housing so that the oil drawn off by the oil guide means enters the interior space of the housing.  
           [0040]    In this respect, considerable portions of the oil are expediently conveyed to the oil separator by the refrigerant flowing through the interior space of the motor housing in order to supply the oil to the oil sump via the oil separator in this way.  
           [0041]    An alternative solution provides for the oil guide means to open into the intermediate space and, therefore, preferably into the oil separator.  
           [0042]    With respect to the conveyance of the lubricating oil to the individual bearings of the inventive compressor to be lubricated, no further details have so far been given. It is preferably provided for the drive shaft to have a bore for lubricating oil, through which the lubricating oil can advantageously be supplied to the respective bearings.  
           [0043]    In this respect, the bore for lubricating oil is expediently designed such that a lubrication of a rotary bearing for the drive shaft in the first bearing member is brought about via this bore.  
           [0044]    Furthermore, the bore for lubricating oil is preferably designed such that a lubrication of the eccentric drive is brought about via this bore.  
           [0045]    With respect to an optimum mounting of the drive shaft in the inventive compressor, it has merely been established thus far that the drive shaft is mounted in the first bearing member, preferably close to the eccentric drive.  
           [0046]    A particularly favorable solution provides for the drive shaft to be mounted, in addition, in a second bearing arranged at a distance from the first bearing member.  
           [0047]    In this respect, the second bearing member is expediently arranged on a side of the drive motor located opposite the first bearing member.  
           [0048]    With respect to the fixing of the second bearing member in the inventive compressor, it has proven to be favorable when the second bearing member is connected to the first bearing member via the motor housing so that a precise alignment of the first bearing member and the second bearing member is possible by means of the motor housing with a simple assembly.  
           [0049]    A solution which is expedient with respect to the simplicity of the construction of the motor housing provides for the second bearing member to form a base of the motor housing.  
           [0050]    Additional features and advantages of the design of the invention are the subject matter of the following description as well as the drawings illustrating several embodiments. 
       
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
       [0051]    [0051]FIG. 1 shows a longitudinal section through a first embodiment of an inventive compressor;  
         [0052]    [0052]FIG. 2 shows a longitudinal section through the first embodiment of the inventive compressor turned through an angle of approximately 90°;  
         [0053]    [0053]FIG. 3 shows a section along line  3 - 3  in FIG. 1;  
         [0054]    [0054]FIG. 4 shows a section along line  4 - 4  in FIG. 1;  
         [0055]    [0055]FIG. 5 shows a plan view of a base of a second bearing part forming a motor housing;  
         [0056]    [0056]FIG. 6 shows a view similar to FIG. 1 of a second embodiment of an inventive compressor;  
         [0057]    [0057]FIG. 7 shows a section along line  7 - 7  in FIG. 6;  
         [0058]    [0058]FIG. 8 shows a section along line  8 - 8  in FIG. 6 and  
         [0059]    [0059]FIG. 9 shows a section similar to FIG. 2 through a third embodiment of an inventive compressor. 
     
    
     DETAILED DESCRIPTION OF THE INVENTION  
       [0060]    A first embodiment of an inventive compressor, illustrated in FIGS.  1  to  5 , comprises an outer housing which is designated as a whole as  10  and in which a scroll compressor, which is designated as a whole as  12  and can be driven by a drive unit designated as a whole as  14 , is arranged.  
         [0061]    The scroll compressor  12  comprises a first compressor member  16  and a second compressor member  18 , wherein the first compressor member  16  has a first scroll rib  22  which rises above a base  20  of the first compressor member and is designed in the form of a circular involute and the second compressor member  18  has a second scroll rib  26  which rises above a base  24  of the second compressor member and is designed in the form of a circular involute, wherein the scroll ribs  22 ,  26  engage in one another and abut sealingly on the base surface  28  and  30 , respectively, of the respectively other compressor member  18 ,  16  so that chambers  32  are formed between the scroll ribs  22 ,  26  as well as the base surfaces  28 ,  30  of the compressor members  16 ,  18 , in which a compression of a refrigerant takes place which flows in with an initial pressure via an intake area  34  surrounding the scroll ribs  22 ,  26  radially outwards and following the compression in the chambers  32  exits via an outlet  36 , provided in the base  20  of the first compressor member  16 , compressed at high pressure.  
         [0062]    In the case of the first embodiment described, the first compressor member  16  is held securely in the outer housing  10 , namely by means of a dividing member  40  which is held, for its part, on the outer housing  10  within the same, engages over the base  20  of the first compressor member  16  at a distance and is connected sealingly to an annular flange  42  of the first compressor member  16  which extends around the outlet  36  and projects above the base  20  on a side located opposite the scroll rib  26 .  
         [0063]    As a result, a cooling chamber  44  for cooling the base  20  of the first compressor member  16  is formed between the base  20  of the first compressor member  16  and the dividing member  40  and this is the subject matter, for example, of WO 02/052205 A2, to which reference is made in full with respect to the cooling of the scroll compressor  12 .  
         [0064]    In contrast to the first compressor member  16 , the second compressor member  18  is movable about a central axis  46  on an orbital path relative to the first compressor member  16 , wherein the scroll ribs  22  and  26  abut theoretically on one another along a contact line and the contact line likewise moves about the central axis  46  during the movement of the second compressor member  18  on the orbital path.  
         [0065]    The second compressor member  18  is driven on the orbital path about the central axis  46  by the drive unit  14  already mentioned which comprises an eccentric drive  50 , a drive shaft  52  driving the eccentric drive  50 , a drive motor  54  as well as a bearing unit  56  for the mounting of the drive shaft  52 .  
         [0066]    In detail, the eccentric drive  50  is formed by an entraining member  62  which is arranged eccentrically on the drive shaft  52  and, therefore, eccentrically in relation to the central axis  46  and engages in an entraining member receiving means  64  connected to the base  24  of the second compressor member  18  in order to move the second compressor member  18  on the orbital path about the central axis  46 .  
         [0067]    The bearing unit  56  comprises, for its part, a first bearing member  66  which represents a main bearing member and mounts the drive shaft  52  in an area  70  with a bearing section  68  and which bears the entraining member  62 , wherein the entraining member  62  is preferably arranged in one piece on the area  70 .  
         [0068]    Furthermore, the first bearing member  66  encloses a space  72 , in which the eccentric drive  50  is arranged and in which a counterbalance  74  securely connected to the drive shaft  52  moves.  
         [0069]    Moreover, the first bearing member  66  extends to the side of the space  72  in the direction of the base  24  of the second compressor member  18  and has bearing surfaces  78  which extend around an opening  76  of the space  72  facing the second compressor member  18  and on which the second compressor member  18  rests with a rear side  80  located opposite the second scroll rib  26  and is, therefore, supported such that the second compressor member  18  is secured against any movement away from the first compressor member  16  as a result.  
         [0070]    The first bearing member  66  is fixed in the outer housing  10  by way of supporting arms  82  which extend radially from the first bearing member  66  as far as the outer housing  10  and hold the first bearing member  66  in it in a precise manner.  
         [0071]    The first bearing member  66  has, in addition, on a side located opposite the supporting arms  82  an outer surface  84 , on which a casing  88  of a motor housing  90  is seated, which extends within and at a distance from a cylindrical section  86  of the outer housing  10 , is likewise preferably cylindrical and extends as far as a second bearing member  92  which forms a base of the motor housing  90 , is arranged at a distance from the first bearing member  66  and forms a bearing section  94 , in which the drive shaft  52  is mounted with an end area  96  coaxially to the central axis  46 .  
         [0072]    For additional stabilization, the second bearing member  92  is supported on the outer housing  10 , in addition, via support members  98 .  
         [0073]    The entire motor housing  90  therefore extends within the cylindrical section  86  of the outer housing  10  and at a distance to it.  
         [0074]    The drive motor  54 , which comprises a rotor  100  seated on the drive shaft  52  and a stator  102  surrounding the rotor  100 , is arranged in the motor housing  90  between the first bearing member  66  and the second bearing member  92 , wherein the stator  102  is held by the casing  88  of the motor housing  90  so as to be fixed in a stable manner relative to the outer housing  10  and so a customary gap  104  exists between the rotor  100  and the stator  102 .  
         [0075]    In addition, the stator  102  is provided on its side facing the casing  88  with cooling channels  106  which extend in the stator  102  over its entire contact side  108  parallel to the central axis  46  in the form of, for example, outer grooves, wherein the stator  102  is supported on the casing  88  via the contact side  108 .  
         [0076]    A free space  112  is provided between the second bearing member  92  and a base part  110  of the outer housing  10  and this offers the possibility, in the case of an outer housing  10  rising above the base part  110  with a central axis  46  extending approximately vertical, of forming an oil sump  114 , in which, on the one hand, lubricating oil collects on account of the force of gravity and, on the other hand, lubricating oil is kept ready for the lubrication of the inventive compressor.  
         [0077]    An oil conveyor pipe  116  extending from the end area  96  of the drive shaft  52  and coaxially to it dips into the oil sump  114  and this pipe has a conveyor blade  120  in its interior  118  and therefore acts as an oil pump which pumps oil out of the oil sump  114  into a channel  122  for lubricating oil which passes through the drive shaft  52  and allows lubricating oil to exit via an opening  124  on an end side  126  of the entraining member  62  in order to lubricate a rotary bearing formed between the entraining member receiving means  64  and the entraining member  62  for the movement of the second compressor member  18  on the orbital path.  
         [0078]    Furthermore, a transverse channel  128  branches off from the channel  122  for lubricating oil and this transverse channel leads to the rotary bearing formed between the bearing section  68  of the first bearing member  66  and the area  70  of the drive shaft  52  and lubricates it and, finally, a venting channel  130  branches off from the channel  122  for lubricating oil.  
         [0079]    The oil used for the lubrication of the entraining member  62  in the entraining member receiving means  64  leaves the entraining member receiving means  64  in the area of an opening  132  of the entraining member receiving means  64  which faces the area  70 , then reaches a base  134  of the space  70  which is formed by the first bearing member  66  and from there passes via discharge channels  136 , which form an oil guide means with the base  134 , into an upper interior space  140  of the motor housing  90 . Furthermore, the oil which serves to lubricate the area  70  of the drive shaft  52  in the bearing section  68  exits from the bearing section  68  at an underside  142  thereof and, therefore, also enters the upper interior space  140  of the motor housing  90 .  
         [0080]    The refrigerant to be compressed by the scroll compressor  12  is supplied to the inventive compressor via an intake line  150  which is guided to an intake connection  152  which, for its part, is held on the outer housing  10  but is guided through this as far as the motor housing  90 .  
         [0081]    The intake connection  152  preferably has a sleeve  154  which passes through the outer housing  10  of the inventive compressor and engages in a receiving means  156  connected securely to the casing  88  of the motor housing  90 , as illustrated in FIGS. 1 and 3. The receiving means  156  encloses an inlet  158  for the refrigerant provided in the casing  88  so that the refrigerant can pass directly into a lower interior space  160  of the motor housing  90  which is located between the stator  102  and the second bearing member  92 .  
         [0082]    Furthermore, the inlet opening  158  is arranged in the direction of the central axis  46  such that the refrigerant enters the lower interior space  160  at the level of a winding head  162  of the stator  102  which likewise projects into the interior space  160 .  
         [0083]    For the optimum distribution of the refrigerant in the lower interior space  160 , a deflection unit  164  is associated with the inlet  158  and this has two deflection surfaces  166  and  168  which deflect the refrigerant flowing through the sleeve  154  approximately in a radial direction  170  in relation to the central axis  46  such that main directions of flow of the gaseous refrigerant supplied extend around the winding head  162  in two opposite azimuthal directions  172  and  174  in relation to the central axis  46 , namely within the casing  88 , the inner wall  176  of which guides the refrigerant propagating in the azimuthal directions  172  and  74  further and contributes to the fact that oil carried along with the refrigerant supplied is separated at the inner wall  176  and runs downwards along this wall in the direction of the second bearing member  92  illustrated in detail in FIG. 5, wherein the bearing member  92  also forms the base  178  which essentially closes the casing  88  and is, however, provided with oil discharge openings  180 , from which the separated oil can flow into the oil sump  114 .  
         [0084]    As a result of the closed base  178 , the refrigerant entering the lower interior space  160  of the motor housing  90  essentially does not have the possibility of passing into the free space  112  between the second bearing member  92  and the base part  110  but rather remains essentially in the interior space  160  for the purpose of cooling the winding head  162  and then, proceeding from the interior space  160 , passes through the cooling channels  106  and the gap  104  between the rotor  100  and the stator  102  into the upper interior space  140  which is located between the first bearing member  66  and the stator  102  in order to cool the winding heads  182  projecting into the upper interior space  140 .  
         [0085]    At least one exit opening  184  is provided in the casing  88 , as illustrated in FIGS. 1 and 4, at the level of the winding head  82  and the refrigerant exits from the upper interior space  140  of the motor housing  90  through this opening, namely into a space  188  which exists between the cylindrical section  88  and the first bearing member  66 —apart from the supporting arms  82 —and the motor housing  90  and which is part of an oil separator  190 . The space  188  is, in particular, located essentially between an inner wall surface  192  of the cylindrical section  86  of the outer housing  10  and an outer wall surface  194  of the cylindrical casing  88 , wherein the space  188  preferably extends as a closed annular space around the casing  88 .  
         [0086]    In order to generate a flow of the gaseous refrigerant in opposite azimuthal directions  196 ,  198  in the space  188 , a deflection unit  200  is arranged so as to be located opposite the exit opening  184  and this deflection unit has deflection surfaces  202  and  204  which deflect the gaseous refrigerant exiting from the exit opening  184  into the azimuthal directions  196  and  198 .  
         [0087]    It is, however, also conceivable to provide several exit openings  184  opening into the space  188  and deflections units  200  associated with them in angular spaced relationship around the central axis  46 .  
         [0088]    As a result of the gaseous refrigerant being guided in the azimuthal directions  196  and  198 , in particular, between the inner wall surface  192  and the outer wall surface  194 , an oil separation effect occurs on account of the constantly active, radial acceleration of drops of oil in the gaseous refrigerant and this oil separation effect is displayed, in particular, by a depositing of oil, which is carried along by the refrigerant, on the inner wall surface  192  and the outer wall surface  194 , wherein the oil, in the case of a compressor assembled with an essentially vertical central axis  46 , can run down between the outer housing  10  and the motor housing  90  preferably along the inner wall surface  192  and the outer wall surface  194  in the direction of the oil sump  114  since a free space  206 , which merges into the free space  112  proceeding from the space  188  and via which the oil can, in the end, be supplied to the oil sump  114 , exists between the outer housing  10  and the motor housing  90  over the entire extension of the motor housing  90  in the direction of the central axis  46 .  
         [0089]    The separation of all the oil carried along by the refrigerant on its way through the interior space  160 , through the gap  104  and the cooling channels  106  as well as the interior space  140  and also, in particular, at least partially, oil which exits at the underside  142  of the bearing section  68  and oil which has been supplied to the interior space  140  via the discharge channels  136  is brought about in the oil separator  190 .  
         [0090]    The refrigerant which is, therefore, essentially freed of oil in the oil separator  190  flows, proceeding from the space  188  of the oil separator  190 , between the supporting arms  82  and, therefore, past the first bearing member  66  on the outside in the direction of the intake area  34  of the scroll compressor  12  and is taken in by this and compressed, wherein the compressed refrigerant, via the outlet  36 , enters a pressure chamber  210 , which is located between a cover  212  of the outer housing  10  and the dividing member  40 , and is discharged from this through a pressure connection  214 .  
         [0091]    In a second embodiment of the inventive compressor, illustrated in FIGS.  6  to  8 , those parts which are identical to those of the first embodiment are given the same reference numerals and so, in this respect, reference is made in full to the comments concerning the first embodiment.  
         [0092]    In contrast to the first embodiment, the intake connection  152 ′ of the second embodiment is arranged such that the inlet  158 ′ is located at the level of the winding head  182  of the stator  102  and, therefore, the refrigerant supplied enters the upper interior space  140  within the motor housing  90  first of all, then enters the lower interior space  160  likewise through the gap  104  between the rotor  100  and the stator  102  and cooling channels  106  likewise provided in order to cool the winding head  162  in this interior space.  
         [0093]    In this embodiment, the exit opening  184 ′ is, therefore, located at the level of the winding head  162 , and thus the space  188 ′ between the inner wall surface  192  of the outer housing  10  and the outer wall surface  194  of the casing  88  at the level of the exit opening  184 ′ in relation to the central axis  46 , but the space  188 ′ and, therefore, the oil separator  190 ′ extend, when seen in the direction of the central axis  46 , over the entire length of the casing  88  as far as the supporting arms  82  of the first bearing member  66  and so, when seen in the direction of the central axis  46 , a longer space is available between the outer housing  10  and the casing  88  for the separation of oil.  
         [0094]    In addition, a deflection unit  200 ′, the deflection surfaces  202 ′ and  204 ′ of which likewise effect a deflection of the exiting refrigerant in the azimuthal directions  196  and  198  in the space  188 ′, is likewise associated with the exit opening  184 ′ and located opposite it.  
         [0095]    Since the space  188 ′ is essentially connected directly to the free space  112 , the oil separating in the oil separator  190 ′ has the possibility of entering the free space  112  without any problem and, from there, passing into the oil sump  114 .  
         [0096]    In a third embodiment of an inventive compressor, illustrated in FIG. 9, those parts which are identical to those of the first embodiment are given the same reference numerals and so reference can be made in full to the comments concerning the first embodiment.  
         [0097]    In contrast to the first and second embodiments, the discharge channels  136 ′ of the third embodiment do not extend such that the oil enters the space  140  but rather through the first bearing member  66  and through the casing  88  in a radial direction in relation to the central axis  46  outwards to such an extent that the oil enters the space  188  and, in it, can flow, preferably through the free space  206 , to the oil sump  114  in the free space  112  together with the oil separated in the space  188 .