EP2828527B1 - Refrigerant compressor - Google Patents

Description

The invention relates to a refrigerant compressor, comprising an overall housing, a screw compressor provided in the overall housing with a compressor housing formed as part of the overall housing in which at least one screw rotor bore is arranged, and with at least one screw rotor rotatably arranged in the screw rotor bore about an axis, one in the overall housing arranged drive motor with a motor housing designed as a further part of the overall housing, in the motor compartment of which a stator and a drive shaft rotatable about a motor axis with a rotor are arranged, and a suction gas connection via which refrigerant drawn in enters the motor compartment before it is compressed by the screw compressor and this flows through, wherein in an area of the engine compartment facing away from the screw compressor housing, a bearing receptacle is arranged in which a rotary bearing for the rotatable mounting of an end facing away from the compressor housing portion of the drive shaft that the suction gas connection is arranged on an end wall of the motor housing opposite the compressor housing and wherein refrigerant sucked in through the suction gas connection enters the motor compartment through this end wall and flows through the motor compartment in the direction of the motor axis.

Such a refrigerant compressor is from DD 210 565 A3 known.

The invention is based on the object of creating a screw compressor that is optimal in terms of cooling and mounting the drive motor. In a screw compressor of the type described at the outset, this object is achieved by the features of claim 1.

The advantage of the solution according to the invention is to be seen in the fact that on the one hand it creates the possibility of mounting the drive shaft in an area of the engine compartment opposite the compressor housing and on the other hand of still flowing through the engine compartment in the direction of the engine axis with the refrigerant sucked in, so that an optimal cooling of the drive motor can be realized with simple means.

With regard to a course of flow paths of the refrigerant in the engine compartment, no further details have been given in connection with the previous explanation of the individual exemplary embodiments.

In principle, the bearing seat could be arranged such that a flow path of the refrigerant runs past the side of the seat.

It is particularly favorable, however, if a flow path of the refrigerant entering through the suction gas connection flows against the bearing receptacle, so that the refrigerant entering through the suction gas connection has at least partially flowed around the bearing receptacle.

However, it is particularly favorable if the bearing receptacle is arranged in the flow path of the refrigerant entering through the suction gas connection in such a way that the refrigerant flows around it.

Such a flow around provides that the refrigerant flows around on an outside of the bearing receptacle.

In order to improve the cooling of the bearing receptacle even further, one embodiment preferably provides that the bearing receptacle is penetrated by a flow path of the refrigerant, so that a flow path of the refrigerant runs through the bearing receptacle, and consequently the bearing receptacle is designed so that the refrigerant can flow through it.

This solution not only has the advantage that it can further improve the cooling of the pivot bearing, but also the advantage that in this solution the refrigerant can be used to lubricate the pivot bearing in the bearing receptacle, since the refrigerant is lubricant anyway , in particular oil, and thus when flowing through the rotary bearing, the lubricant can be deposited in the rotary bearing and can thus contribute to its lubrication.

An advantageous solution provides that a flow path of the refrigerant sucked in is directed towards the end windings of the stator and thus cools the end windings of the stator.

It is also preferably provided that a flow path of the refrigerant drawn in passes through a gap between the rotor and stator and is thus able to cool both the rotor and the stator in the region of the gap.

A further advantageous solution provides that a flow path flows through recesses of the stator running radially on the outside.

Furthermore, it is preferably provided that the end wall of the motor housing has flow guide surfaces which define the course of at least one of the flow paths.

A solution is particularly favorable in which the bearing receptacle is arranged at a distance from the suction gas connection in the engine compartment, in order to disturb the flow of the sucked-in refrigerant as little as possible.

Furthermore, it is favorable for the inflow of the refrigerant if an inflow space for the refrigerant drawn in is located between the bearing receptacle and the suction gas connection.

The bearing receptacle can be fixed in the most varied of ways relative to the motor housing.

For example, it would be conceivable to fix the bearing receptacle on the motor housing by means of struts extending radially to the motor axis.

Another advantageous solution provides that the bearing receptacle is held on an end wall of the motor housing with struts, between which refrigerant drawn in can flow through.

A particularly expedient design of the motor housing according to the invention provides that its end wall is formed by a front-side detachable cover.

In this case, in particular, the bearing receptacle is also held on the front cover of the motor housing with the struts.

In order to discharge the refrigerant from the engine compartment, it is preferably provided that the engine compartment has an interior space on a side facing the compressor housing, from which the refrigerant passes through at least one opening into the helical rotor housing.

With regard to the supply of the sucked-in refrigerant to the engine compartment, no further details have been given so far.

An advantageous solution provides that the suction gas connection supplies the sucked-in refrigerant to the engine compartment with a direction of flow that is oblique to or parallel to the motor axis, so that a flow direction is already predetermined by the inflowing refrigerant.

The suction gas connection could in principle be arranged radially offset with respect to the motor axis.

In order to achieve the most favorable possible flow through the engine compartment, it is advantageously provided that the suction gas connection is arranged on the end wall of the engine housing in such a way that the geometric engine axis passes through it.

It is particularly favorable if the suction gas connection is arranged concentrically to the geometric motor axis.

Even if the motor housing is designed in such a way that its end wall is formed by an end cover, it is preferably provided that the suction gas connection is arranged on an end cover of the motor housing.

Furthermore, the suction gas connection could be connected directly to a refrigerant line leading to the refrigerant compressor according to the invention.

It is particularly useful, however, if the suction gas connection is connected to a supply unit for refrigerant.

Such a supply unit can be designed, for example, as a shut-off valve on the suction side.

It is particularly advantageous if the feed unit is designed such that it feeds the refrigerant to the suction gas connection with the flow direction running in the direction of the motor axis.

In order to facilitate the installation of the refrigerant compressor according to the invention, it is preferably provided that the feed unit can be mounted on the sag gas connection in different rotational positions with respect to an axis, so that the feed unit can be aligned according to a course of lines leading to it.

Further features and advantages are the subject of the following description and the graphic representation of some exemplary embodiments.

Fig. 1

eine perspektivische Ansicht eines erfindungsgemäßen Kältemittelverdichters;

Fig. 2

eine Seitenansicht in Richtung des Pfeils A in Fig. 1;

Fig. 3

eine Ansicht in Richtung des Pfeils B in Fig. 1;

Fig. 4

eine Ansicht in Richtung des Pfeils C in Fig. 1

Fig. 5

einen Schnitt längs Linie 5-5 in Fig. 4

Fig. 6

eine perspektivische Darstellung eines stirnseitigen Deckels mit einer Lageraufnahme mit Blick auf den Deckel von Seiten des Motorraums;

Fig. 7

eine perspektivische Darstellung des Deckels gemäß Fig. 6 mit Blick von einem Sauggasanschluss auf den Deckel;

Fig. 8

einen vergrößerten Schnitt durch den stirnseitigen Deckel mit dem Sauggasanschluss und der Lageraufnahme;

Fig. 9

einen Schnitt längs Linie 9-9 in Fig. 5;

Fig. 10

einen Schnitt längs Linie 10-10 in Fig. 5;

Fig. 11

einen Schnitt längs Linie 11-11 in Fig. 4;

Fig. 12

einen vergrößerten Schnitt ähnlich Fig. 11 im Bereich eines Druckgehäuses und

Fig. 13

einen Schnitt ähnlich Fig. 8 durch ein zweites Ausführungsbeispiel eines erfindungsgemäßen Kältemittelverdichters.

In the drawing show:

Fig. 1

a perspective view of a refrigerant compressor according to the invention;

Fig. 2

a side view in the direction of arrow A in FIG Fig. 1 ;

Fig. 3

a view in the direction of arrow B in FIG Fig. 1 ;

Fig. 4

a view in the direction of arrow C in FIG Fig. 1

Fig. 5

cut along line 5-5 in Fig. 4

Fig. 6

a perspective view of an end cover with a bearing receptacle with a view of the cover from the side of the engine compartment;

Fig. 7

a perspective view of the cover according to Fig. 6 with a view of the cover from a suction gas connection;

Fig. 8

an enlarged section through the front cover with the suction gas connection and the bearing receptacle;

Fig. 9

a section along line 9-9 in Fig. 5 ;

Fig. 10

cut along line 10-10 in Fig. 5 ;

Fig. 11

a section along line 11-11 in Fig. 4 ;

Fig. 12

similar to an enlarged section Fig. 11 in the area of a pressure housing and

Fig. 13

a cut similar Fig. 8 by a second embodiment of a refrigerant compressor according to the invention.

An in Figs. 1 to 3 The illustrated embodiment of a refrigerant compressor according to the invention has an overall housing 10 which comprises a compressor housing 12, a motor housing 14 arranged on one side of the compressor housing 12 and a pressure housing 16 arranged on a side of the compressor housing 12 opposite the motor housing 14. The compressor housing 12, the motor housing 14 and the pressure housing 16 can be separate parts of the overall housing 10 and put together to form the same, or the compressor housing 12 and the motor housing 14 and / or the compressor housing 12 and the pressure housing 16 can be designed as coherent parts.

Furthermore, in the area of a partial circumference, the motor housing 14 carries a control housing 18 in which a control for the refrigerant compressor is arranged.

As in Fig. 2 , 3 and 5 shown, the motor housing 14 encloses an engine compartment 20 and is at its end facing away from the compressor housing 12 by an end wall of the motor housing 14 forming front-side cover 22 closed, which in turn is provided with a suction gas connection 24 via which refrigerant to be sucked in can be fed to the refrigerant compressor.

As in Fig. 2 and 3 shown, the suction gas connection 24 is preferably provided with a shut-off valve 26 which is connected to a suction gas line leading to the refrigerant compressor, not shown in the drawings.

The shut-off valve 26, as in FIG Fig. 3 shown, can be mounted around an axis 28 in various rotational positions, for example in four rotational positions rotated by 90 ° in relation to one another, in order to enable optimal adaptation to a suction gas line (not shown in the drawing) leading to the refrigerant compressor.

The possibility of assembling the shut-off valve 26 in different rotational positions can be achieved in that retaining screws 32a, 32b, 32c and 32d are arranged at the same angular intervals around the axis 28, with which the shut-off valve 26 is in the four rotational positions rotated by 90 ° relative to the cover 22 is mountable.

The pressure housing 16 is detachably connected to the compressor housing 12 via a pressure housing flange 34, which can be connected to a mounting flange 36 of the compressor housing 12, with the pressure housing 16 being in the form of a cylindrical end wall 48, starting from the pressure housing flange 34 Capsule 38 extends.

Furthermore, the pressure housing 16 carries a pressure gas connection 42 on which a pressure gas-side shut-off valve 44 can be mounted.

Preferably, the capsule 38 is also closed in the area of its end wall 48 opposite the compressor housing 12 in an accessible manner with an access cover 46 ( Fig. 1 and 4th ).

As in Fig. 5 shown, in the motor housing 14 sits an electric motor designated as a whole with 50, a stator 52 fixedly arranged in the motor housing 14 and a rotor 56 which is rotatably mounted relative to the stator 52 about a motor axis 54, the rotor 56 being seated on a drive shaft 58.

The drive shaft 58 on the one hand passes through the rotor 56 in the direction of the motor axis 54 and on the other hand extends into the compressor housing 12 of a screw compressor designated as a whole with 60.

In its area extending in the compressor housing 12, the drive shaft 58 carries a screw rotor 62, which is arranged in the compressor housing 12 in a screw rotor bore 64 and can be rotated in this about an axis of rotation 63 coinciding with the motor axis 54.

In addition, the drive shaft 58 extends beyond the helical rotor 62 on its side opposite the electric motor 50 and forms an end section 66 which is rotatably mounted in a bearing housing 68 arranged within the pressure housing 16, with a bearing set 72 on the pressure side in the bearing housing 68 is provided.

Furthermore, the drive shaft 58 is supported between the screw rotor 62 and the rotor 56 in a suction-side bearing set 74 which is arranged adjacent to a suction side of the screw rotor 62.

For example, the suction-side bearing set 74 is held on a suction-side wall 76 of the compressor housing 12, while the pressure-side bearing set 72 is held on a pressure-side wall 78, the bearing housing 68 being carried by the pressure-side wall 78 for this purpose.

For precise guidance of the rotor 56 coaxially to the motor axis 54, the drive shaft 58 also has an end section 82 which extends beyond the rotor 56 and which in turn is mounted in a guide bearing 84 which is seated in a bearing receptacle 86 which is arranged coaxially to the motor axis 54 and which is fixed is arranged on the motor housing 14, specifically near the cover 22.

The bearing receptacle 86 could be supported directly on the motor housing 14 independently of the cover 22.

Preferably, the bearing receptacle 86 is as in FIG Fig. 5 , Fig. 6 and Fig. 7 shown, held on the cover 22, the bearing receptacle 86 being held at a distance from a cover base 92 by several webs, for example webs 88a, 88b or 88c arranged at equal angular distances from one another.

In particular, the bearing receptacle 86 comprises a receiving base 85 which is carried by the webs 88a, 88b and 88c, and an annular body 87 which surrounds the guide bearing 84 radially on the outside.

In addition, a suction opening 94 is provided in the cover base 92, to which the suction gas connection 24 adjoins and is in alignment therewith.

The webs 88a, 88b, 88c hold the bearing receptacle 86 at such a distance from the cover base 92 that an inflow space extending in the direction of the motor axis 54 and around the motor axis 54 is formed between the cover base 92 and the bearing receptacle 86, which is located between the in Circumferential direction successive webs 88 extending inflow openings 96a, 96b and 96c is surrounded, through which the suction gas with a relative to the motor axis 54 axial and radial component, as in Fig. 8 represented by dashed lines, can enter a frontal interior 100 of the engine compartment 20.

A suction gas filter 98, through which the suction gas must flow, is preferably arranged around the bearing receptacle 86 in the interior 100.

The suction gas flows as in Fig. 5 and 8th Shown in dashed lines, from the shut-off valve 26 in the direction parallel to the motor axis 54 through the suction gas connection 24 and the suction opening 94 into the inflow space 90, which is arranged between the suction opening 94 and the bearing receptacle 86.

The suction gas then flows from the inflow space 90 with a component that runs obliquely to the motor axis 54 through the inflow openings 96 into the interior 100, forming a plurality of flow paths S.

For example, a first flow path S1 flows against the bearing receptacle 86 in the area of the outer ring body 87, which surrounds the guide bearing 84 radially on the outside, and preferably flows around the ring body 87, so that the bearing seat is cooled.

This flow path S1 also flows against the rotor 56 at its end face 104 facing away from the compressor housing.

Furthermore, a flow path S2, for example, flows against the stator 52 in the area of its winding heads 102 facing away from the compressor housing 12 in order to cool the latter.

Another flow path S3 opens up the possibility, for example, of flowing through a gap 108 between the rotor 56 and the stator 52 in the direction of the compressor housing 12, so that both cooling of the stator 52 and cooling of the rotor 56 also take place.

In addition, a flow path S4 is formed, for example, and as in FIG Fig. 9 shown, the stator 52 flows around the radially outer recesses 106 of the same in the direction of the compressor housing 12 and thereby cooled radially on the outside.

The suction opening 94 is preferably arranged in the cover 22 in such a way that the motor axis 54 penetrates it, in particular the suction opening 94 is arranged coaxially to the motor axis 54 so that approximately rotationally symmetrical flow conditions arise in the area of the interior 100 and the bearing receptacle 86 to the motor axis 54.

The suction gas is guided to form the flow paths S on the one hand through the receptacle base 85 and the annular body 87 of the bearing receptacle 86, which form flow guide surfaces 89 facing the suction gas flow, as well as flow guide surfaces 99 which are formed in the cover base 90 following the suction opening 94 and, starting from the intake opening 94, widen increasingly with increasing extension in the direction of the compressor housing 12.

After flowing through the recesses 106 and the gap 108, the suction gas collects in the area of the compressor housing 12 facing winding heads 112 of the stator 52 in a compressor housing-side interior 116 of the motor housing 14 and is able to cool these winding heads 112 before the sucked in gas - or refrigerants, as in Fig. 10 shown, passes through openings 114a, 114b and 114c provided in the suction-side wall 76 of the compressor housing 12, and thereby enters a suction chamber 118 of the compressor housing 12.

As in Fig. 10 and Fig. 11 In addition to the first screw rotor 62, there is also a second screw rotor 122 that works together with it and is arranged in a screw rotor bore 120, the second screw rotor 122 also about an axis of rotation 123 parallel to the motor axis 54 and to the axis of rotation 63 by means of an end over the screw rotor 122 protruding bearing shaft 124 is mounted in a pressure-side bearing set 126 and a suction-side bearing set 128 is mounted.

The two screw rotors 62 and 122 now work together in such a way that refrigerant or gas is sucked in from the suction chamber 118, compressed by the interlocking screw rotors 62 and 122 and as a compressed gas or refrigerant in the area of an outlet window 132 on the pressure side, defined by the circumferential areas and end face areas exposed on the pressure side the screw rotor 62, 122 exits into the compressor housing 12 and passes out of the compressor housing 12 through a housing window 133 into the pressure housing 16.

To adjust the volume ratio, a slide 134 is also provided for this purpose, the design and function of which is described, for example, in the German patent application 10 2011 051 730.8 is described.

In order to dampen the pressure pulsations of the compressed gas or refrigerant exiting through the outlet window 132, a first silencer unit 140 is provided in the immediate connection to the housing window 133 in the pressure housing 16, which has a receiving chamber 138 directly adjoining the housing window 132, one on one of the housing window 132 opposite side of the receiving chamber 138 has inlet opening 142 and an outlet opening 144, which can be flowed through in a direction of flow 146 directed in particular transversely to the pressure-side wall 78 and away from it, in particular parallel to the motor axis 54, wherein between the inlet opening 142 and the outlet opening 144, for example, a plurality of chambers 148a and 148b and 150a, 150b and 150c that expand transversely to the flow direction 146 are provided and each of the chambers 148 and 150 is as in FIG Fig. 12 shown, separated by a partition 152 from the next chamber 148, 150, each partition 152 having a flow-constricting passage opening 154 through which the compressed gas or compressed refrigerant can pass from one of the chambers 148, 150 to the other.

In particular, for reasons of ease of manufacture, the through-openings 154 are each designed such that their extension in the flow direction 146 corresponds to the thickness of the partition 152, so that the through-openings merge into wall surfaces of the partition 152 without protruding.

In the same way, the inlet opening 142 and the outlet opening 144 also merge without protrusion into the wall surface of the respectively adjoining chamber 148 or 150.

The chambers 148, 150 preferably have different chamber volumes.

Such different chamber volumes can be achieved, for example, in that the chambers 148, 150 have the same dimensions transversely to the flow direction 146 or radially to this, but different dimensions in the direction of the flow direction 146.

In the embodiment according to Fig. 11 and 12 the inlet opening 142, the through openings 154 and the outlet opening 144 are arranged coaxially to a central axis 156 and in the same way the chambers 148 and 150 are also coaxial to the central axis 156, so that the first silencer unit 140 is rotationally symmetrical to the central axis 156.

In particular, the central axis 156 extends parallel to the axes of rotation 63 and 123 of the screw rotors 62 and 122 and thus parallel to the motor axis 54.

For example, the chambers 148 and 150 have an inner diameter D _ik that is more than 1.3 times, even better than 1.4 times, an inner diameter D _{id of} the through openings 154 and of the inlet opening 142 and the outlet opening 144.

In addition, an expansion A _{K148 of} the individual chambers 148 is more than approximately 0.2 times, even better more than approximately 0.23 times the inside diameter D _{ik of} the chambers 148, 150.

The maximum extent of the chambers 148, 150 in the direction of the central axis 156 corresponds to the inner diameter D _{ik of} the chambers 148, 150; a maximum value of D _ik of half the inner diameter D _{ik of} the chambers 148 is even better.

In contrast, the extension A _{k150 of} the chambers 150 is more than approximately 0.1 times the inner diameter D _{ik of} the chambers 150.

Following the first silencer unit 140, there follows, for example, a second silencer unit 160, which has a cross-flow chamber 162 directly adjoining the outlet opening 144, through which the compressed gas or refrigerant exiting from the first silencer unit 140 in a flow direction 164 running transversely to the flow direction 146 can flow in the direction of an outlet 166 of the second silencer unit 160, from which the compressed gas or refrigerant is then guided in a channel 168, for example formed by a tube 172, to the end wall 48 of the capsule 38 and there radially through openings 174 in the tube 172 exits and enters a pressure chamber 176 of the pressure housing 16 surrounding the pipe 172.

Around the channel 168, in particular around the pipe 172, a lubricant separation unit 180 is arranged in the pressure chamber 176 of the pressure housing 16, which has, for example, two sets of porous gas-permeable structures 182 and 184, for example made of metal, which are used for separating lubricant mist the pressurized gas or refrigerant.

After flowing through the lubricant separation unit 180, the pressurized gas or refrigerant then has the option of exiting the pressure housing 16 via the pressurized gas connection 42.

The lubricant collecting in the lubricant separating unit 180 forms an area of the pressure housing 16 and the compressor housing 12 which is located at the bottom in the direction of gravity, a lubricant bath 190, from which lubricant is taken, filtered through a filter 192 and used for lubrication.

In connection with the previous description of the first silencer unit 140 and the second silencer unit 160, nothing has been said about their arrangement.

Both the first muffler unit 140 and the second muffler unit 160 are preferably arranged in a muffler housing 200 which, for example, is integrated into the bearing housing 68 or molded onto it, so that the bearing housing 68 and the muffler housing 200 as a whole form a combined housing 210 which is inside of the pressure housing 16 and is in turn carried by the pressure-side wall 78 of the compressor housing 12.

The combined housing 210 can be constructed in the most varied of ways, on the one hand to form the bearing housing 68 and, on the other hand, to form the silencer housing 200.

The combined housing 210 is preferably constructed in two parts and comprises a base housing 212 which is connected to the pressure-side wall 78 of the compressor housing 12 and which receives the pressure-side bearing sets 70 and 126 and also part of the chambers 148 and 150, for example the chambers 148 and one Part of chambers 150.

A cover housing 214 is then firmly connected to the base housing 212 and accommodates the cross-flow chamber 162 and part of the chambers 150 and forms a cover for the pressure-side bearing sets 72 and 126.

Starting from the cover housing 214, the tube 172 then extends in the direction of the end wall 48.

In particular, the base housing 212 and the cover housing 214 can be separated by a geometric separating plane 216 which runs transversely, preferably perpendicularly, to the axes of rotation 63, 123 of the screw rotors 62, 122.

The combined housing 210 can advantageously be produced as a cast part, into which the muffler units 140, 160 and the bearing housing 68 can be molded close to the final contour using the casting mold.

The guide bearing 84 and possibly the bearing sets 72 and 74 as well as 126 and 128 are lubricated via central lubricant channels 222 and 224 of the drive shaft 58 and the bearing shaft 124, which the guide bearing 84 and possibly the bearing sets 72 and 74, 126 and 128 with for lubrication Supply oil.

In a second exemplary embodiment of a refrigerant compressor according to the invention, shown in FIG Fig. 13 , the bearing receptacle 86 'is designed so that the receptacle base 85' has one or more openings, for example a central opening 232, which is preferably arranged coaxially to the motor axis 54, so that the suction gas that passes through the suction opening 94 in the cover base 92 , has the possibility of flowing directly to the guide bearing 84 in the bearing receptacle 86 ′ along a flow path S5 through the opening 232 and, in particular, of flowing through it in the direction of the motor axis 54.

It is thus possible to cool the guide bearing 84 directly and, for example, also to lubricate it, namely by means of the lubricant that is always carried along in the suction gas, in particular in the form of oil.

In particular, this is possible when the suction opening 94 is arranged coaxially to the motor axis 54, since the bearing receptacle 86 ′ must be arranged coaxially to the motor axis 54 anyway.

Incidentally, with regard to the description of the second exemplary embodiment, reference is made in full to the statements relating to the first exemplary embodiment.

Claims (15)

1. Refrigerant compressor, comprising
   an overall housing (10),
   a screw compressor (60) provided in the overall housing (10) and having a compressor housing (12) designed as part of the overall housing (10), at least one screw rotor bore (64, 120) being arranged in said compressor housing, and having at least one screw rotor (62, 122) arranged in the screw rotor bore (64, 120) for rotation about an axis (63, 123),
   a drive motor (50) arranged in the overall housing (10) and having a motor housing (14) designed as an additional part of the overall housing (10), a stator (52) and a drive shaft (58) rotatable about a motor axis (54) with a rotor (56) being arranged in the motor chamber (20) of said motor housing,
   a suction gas connection (24), refrigerant sucked in via said connection entering the motor chamber (20) and flowing through it prior to its compression by the screw compressor (60), wherein the suction gas connection (24) is arranged at an end wall (22) of the motor housing (20) located opposite the compressor housing (12), and refrigerant sucked in through the suction gas connection (24) enters the motor chamber (20) through this end wall (22) and flows through the motor chamber (20) in the direction of the motor axis (54), wherein a bearing receptacle (86) is arranged in an area of the motor chamber (20) facing away from the compressor housing (12), a rotary bearing (84) being accommodated in said receptacle for the rotatable mounting of an end section (82) of the drive shaft (58) facing away from the compressor housing (12), and wherein the bearing receptacle (86) is arranged in the motor chamber (20) at a distance from the suction gas connection (24),
   characterized in that the drive shaft (58), on the one hand, passes through the rotor (56) in the direction of the motor axis (54) and, on the other hand, extends into the compressor housing (12) of the screw compressor (10) and bears the screw rotor (62) with its area extending in the compressor housing (12), said screw rotor being rotatable in the screw rotor bore (64) about an axis of rotation (53) coinciding with the motor axis (54), and that the drive shaft (58) extends beyond the screw rotor (62) on its side located opposite the electric motor (50) and forms an end section (66) rotatably mounted in a bearing housing (68) arranged within a pressure housing (16) by way of a set of bearings (72) on the pressure side and that the drive shaft (58) is mounted between the screw rotor (62) and the rotor (56) in a set of bearings (72) on the suction side arranged adjacent to the suction side of the screw rotor (62).
2. Refrigerant compressor as defined in claim 1, characterized in that a flow path (S1) of the refrigerant entering through the suction gas connection (24) flows against the bearing receptacle (86).
3. Refrigerant compressor as defined in claim 1 or 2, characterized in that a flow path (S5) of the refrigerant passes through the bearing receptacle (86).
4. Refrigerant compressor as defined in any one of the preceding claims, characterized in that at least one flow path (S2) of the refrigerant sucked in flows against winding heads (102) of the stator (52).
5. Refrigerant compressor as defined in any one of the preceding claims, characterized in that a flow path (S3) of the refrigerant sucked in passes through a gap (108) between stator (52) and rotor (56).
6. Refrigerant compressor as defined in any one of the preceding claims, characterized in that a flow path (S4) flows through recesses (106) of the stator (52) extending radially externally.
7. Refrigerant compressor as defined in any one of the preceding claims, characterized in that the end wall (22) of the motor housing (14) has flow guiding surfaces (89, 99) predetermining the course of at least one of the flow paths (S).
8. Refrigerant compressor as defined in any one of the preceding claims, characterized in that an inflow chamber (90) for the refrigerant sucked in is located between the bearing receptacle (86) and the suction gas connection (24).
9. Refrigerant compressor as defined in any one of the preceding claims, characterized in that the bearing receptacle (86) is held on an end wall (22) of the motor housing (14) with struts (88).
10. Refrigerant compressor as defined in any one of the preceding claims, characterized in that the suction gas connection (24) conveys the refrigerant sucked in to the motor chamber (20) with a direction of flow running at an angle or parallel to the motor axis (54).
11. Refrigerant compressor as defined in any one of the preceding claims, characterized in that the suction gas connection (24) is arranged on the end wall (22) of the motor housing (14) in such a manner that the geometric motor axis (54) passes through it and that, in particular, the suction gas connection (24) is arranged concentrically to the geometric motor axis (54).
12. Refrigerant compressor as defined in any one of the preceding claims, characterized in that the suction gas connection (24) is arranged on an end-side cover (22) of the motor housing (14).
13. Refrigerant compressor as defined in any one of the preceding claims, characterized in that the suction gas connection (24) is connected to a supply unit (26) for refrigerant.
14. Refrigerant compressor as defined in claim 13, characterized in that the supply unit (26) conveys the refrigerant to the suction gas connection (24) with a direction of flow running in the direction of the motor axis (54).
15. Refrigerant compressor as defined in either one of claims 13 or 14, characterized in that the supply unit (26) is mountable on the suction gas connection (24) in different rotary positions in relation to an axis (28).

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