EP1413758B1 - Scroll compressor with oil separator - Google Patents

Abstract

The compressor has a scroll compressor unit (12) that is arranged in outer housing (10) and comprised with compressor portions (16,18) which are relatively movable. A stroke catcher is formed with an aperture which is extended from an orifice to a high pressure side of a high pressure chamber (210) in the scroll compressor unit. A movement space is formed between valve with a valve seat and the stroke catcher. The aperture is positioned with respect to a central axis of the movement space.

Description

The invention relates to a compressor for refrigerants, comprising an outer casing, a arranged in the outer casing scroll compressor with a first, fixed in the outer housing compressor body and a second compressor body movable relative to the first compressor body, each one floor and above the respective floor have uplifting first and second spiral ribs, which interlock, that for compressing the refrigerant, the second compressor body opposite the first compressor body on an orbital track about a central axis is movable, a drive unit for the second compressor body with an eccentric drive, a drive shaft, a in a motor housing arranged and flowed around by the sucked refrigerant drive motor and a bearing unit for the drive shaft, which has a first, with the Enclosed outer housing comprises bearing body.

In the PATENT ABSTRACTS OF JAPAN vol. 1999, no. 01, 29th January 1999 (1999-01-29) & JP 10 274178 A (MITSUBISHI ELECTRIC CORP), October 13, 1998 (1998-10-13) is a compressor of the above type described, wherein the drive motor flows around the sucked refrigerant is.

The drive motor sits in an inner shell, which via a support element an outer casing is supported to the generation of noise and To suppress vibrations.

In the PATENT ABSTRACTS OF JAPAN vol. 2000, no. 15, 6 April 2001 (2001-04-06) & JP 2000 345978 A (MITSUBISHI HEAVY IND LTD), December 12, 2000 (2000-12-12) is also a compressor for refrigerants in an area between the bearing body and the engine in azimuthal Direction around the drive shaft flows.

In such compressors, the problem is that still from sucked refrigerant entrained oil enters the scroll compressor and in this leads to problems.

The invention is therefore based on the object, a compressor of generic type to improve that of the scroll compressor sucked refrigerant is as much as possible free of lubricating oil.

This object is achieved in a compressor of the type described above According to the invention solved in that the refrigerant after flowing around the Drive motor and before entering the scroll compressor an oil separator flows through which in the outer housing between this and the Drive unit is arranged.

The advantage of this solution is the fact that through this additional Oil separator was created a possibility of the sucked refrigerant already carried along and also on the refrigerant during the course of the Flowed through the drive motor oil entrained before entering the To divide the scroll compressor in a sufficiently large extent to the oil problems in the scroll compressor.

With regard to a compact construction as possible of the invention Compressor, it has proved to be advantageous if the oil separator in one in the direction transverse to the central axis between the outer housing and the Drive unit lying intermediate space is arranged, since thus in particular the length of the compressor does not change.

Furthermore, it has proved to be particularly advantageous when the Gap between the outer housing and the drive unit in essentially over the entire extension of the drive unit in the direction extends parallel to the central axis.

Thus, the gap could still be unilaterally the drive unit be arranged. It is particularly useful in terms of possible large available space when the gap the Surrounds drive unit and thus runs around the drive unit on all sides, for an optimal use of free space in the outer housing too receive.

The gap is not only for the arrangement of the oil separator but preferably used in many ways. An appropriate solution looks like this in that in the space from the oil separator separated oil in Direction of the oil sump moves and refrigerant toward a suction chamber of the scroll compressor flows. Such, the space in more diverse Way using arrangement allows a particularly compact design the compressor of the invention.

With regard to the management of the refrigerant, it has proven to be particularly useful proven when the refrigerant after cooling of the drive motor in the Interspace occurs.

With regard to a most favorable arrangement of the oil separator is provided that the oil separator at least partially on an outside of the first bearing body is arranged, since in this area suitable Space is available.

Particularly favorable, the oil separator can then arrange, if this at least partially surrounds the first bearing body.

Another favorable arrangement in addition to or as an alternative to arranging the Ölabscheiders on the outside of the bearing body provides that the oil separator at least in sections on an outer side of the motor housing is arranged, since in this area much space is made available can, without significantly increasing the size of the compressor. It is particularly advantageous if the oil separator at least partially surrounds the motor housing.

With regard to the specific design of the oil separator provides a preferred Embodiment before that the oil separator a part of between the Outer housing and the drive unit lying gap uses.

As it has proven particularly favorable when the oil separator used space between the outer housing and the drive unit an annulus is.

Regarding the arrangement of the oil separator in the gap were so far no details given. So it is preferably provided that the oil separator on a side facing the oil sump of the first Bearing body with the outer housing connecting retaining arms is to the Oil separator conveniently at a sufficiently great distance from the To arrange intake of the scroll compressor.

Furthermore, it is particularly advantageous if the oil separator in front of a motor housing provided outlet opening for the refrigerant is arranged to to achieve a good space utilization.

Regarding the guidance of the refrigerant in the oil separator were in Connection with the previous explanation of the individual embodiments no details provided. This is what a particularly favorable one looks like Solution before that the refrigerant when entering the oil separator a deflection in azimuthal direction to the central axis learns, as a result particularly effective oil separation by acting on the oil droplets and is achieved transverse to the flow direction forces.

It is particularly favorable when the refrigerant by a deflecting the Redirection experiences in the at least one azimuthal direction. A special advantageous solution provides that the refrigerant is a reversal in opposite experiences azimuthal directions.

For further optimal oil separation, it is also beneficial if the Refrigerant in the oil separator substantially in an azimuthal path the central axis is guided.

A structurally particularly simple embodiment of an oil separator sees in that the refrigerant in the oil separator along an inner wall surface of the Outer housing flows and thus in particular in a cylindrical Outer housing is always deflected in the azimuthal direction to the central axis.

A particularly simple guidance of the precipitated oil in the oil separator provides that the oil precipitating in the oil separator on an outside the motor housing extending path into the oil sump moved to prevent the refrigerant cooling the drive motor from re-oiling receives and transported to the oil separator.

With regard to the arrangement of the oil sump have so far no closer Information provided. So is advantageously the compressor of the invention as working with a substantially vertically aligned central axis Compressor designed so that the oil sump in the outer housing on a the arranged first bearing body opposite side of the drive motor is.

With regard to the arrangement of the oil separator were so far no closer Information provided. Thus, a particularly favorable solution that the Refrigerant on its way from the oil separator to the suction chamber of the scroll compressor an outer side of the first bearing body flows around the first Cool the bearing body. Preferably, this is also a long distance between the suction chamber and the oil separator feasible.

A particularly favorable solution provides that the oil separator on a side facing the oil sump of the first bearing body with the Outside housing connecting retaining arms is located.

A particularly favorable embodiment with regard to the guidance of the refrigerant provides that the refrigerant after flowing through the oil separator between the holding arms in the direction of the suction space of the scroll compressor flows through it.

Regarding the guidance of the sucked by the compressor refrigerant in the compressor itself so far no details have been made. So For example, it would be conceivable for the refrigerant to be initially introduced into the outer housing let enter and then lead by detours in the motor housing.

However, it has proved to be particularly advantageous if the refrigerant is at Entry into the compressor flows directly into the motor housing and after passing through the motor housing, it enters the oil separator. In order to it is possible to introduce the refrigerant specifically into the motor housing and to avoid additional detours.

It is particularly advantageous if the entering into the motor housing Refrigerant undergoes a deflection in at least one Azimutalrichtung.

Even better, if the refrigerant is a reversal in opposite Azimuthalrichtungen undergoes and thus an interior of the motor housing flows through oppositely directed azimuthal flows.

With regard to an optimal cooling effect in the drive motor, it has proven to be particularly useful when the refrigerant in the direction of the central axis seen at the level of a first winding head in the motor housing entry.

Conveniently, the refrigerant is in the motor housing in Direction of the central axis seen so that it drives the engine from flows through the first winding head in the direction of a second winding head.

In order to lead the refrigerant as low as possible is provided that the Refrigerant seen in the direction of the central axis at the level of the second Winding head emerges from the motor housing.

In this solution is not described in detail, where the first winding head and the second winding head lie.

In a solution according to the invention, the first winding head is arranged such that that this is the winding head of the drive motor, which on one the first bearing body side facing away, while another side Embodiment of the winding head is the winding head of the drive motor, which lies on a side facing the first bearing body.

Regarding the guidance of itself in the engine housing separating oil for Oil sump have so far been no further details. She sees one advantageous solution before that in the motor housing separating oil Oil drain openings of a second floor forming a bottom of the motor housing Bearing body exits the motor housing to get into the oil sump.

To further also out of the eccentric due to the lubrication outgoing Targeted discharge of oil is preferably provided that the first Bearing body an oil guide used for lubrication of the eccentric drive Has oil.

This oil guide can be designed in various ways. Thus, an advantageous solution that the oil passage in an interior of the motor housing opens, so that the discharged oil from the oil guide in enters the interior of the housing.

Conveniently, the oil is in significant parts of the Interior of the motor housing flowing through refrigerant to the oil separator promoted to supply the oil through the oil separator to the oil sump.

An alternative solution provides that the oil guide into the space and thus preferably opens into the oil separator.

Regarding the promotion of the lubricating oil to the individual to be lubricated Storage of the compressor according to the invention have so far no closer Information provided. So it is preferably provided that the drive shaft a Having oil drilling, through which advantageously the Lubricating oil can be supplied to the respective camps.

Conveniently, the lubricating oil hole is designed so that over this one lubrication of a pivot bearing for the drive shaft in the first Bearing body takes place.

Further, preferably, the lubricating oil hole is formed so that over this a lubrication of the eccentric drive takes place.

With regard to an optimal storage of the drive shaft in the invention Compressor has so far only been determined that the drive shaft in the first bearing body, preferably stored near the eccentric drive is.

A particularly favorable solution provides that the drive shaft in addition to a second, spaced from the first bearing body bearing is stored.

Conveniently, the second bearing body is on a first Bearing body opposite side of the drive motor arranged.

With regard to the fixation of the second bearing body in the invention Compressor, it has proved to be favorable when the second bearing body is connected via the motor housing with the first bearing body, so that by the motor housing a precise alignment of the first bearing body and the second bearing body is given with easy mounting option.

A convenient in terms of simplicity of construction of the motor housing Solution provides that the second bearing body a bottom of the motor housing forms.

Further features and advantages of the embodiment of the invention are the subject matter the following description and the graphic representation of some Embodiments.

Fig. 1

einen Längsschnitt durch ein erstes Ausführungsbeispiel eines erfindungsgemäßen Kompressors;

Fig. 2

einen um einen Winkel von ungefähr 90° gedrehten Längsschnitt durch das erste Ausführungsbeispiel des erfindungsgemäßen Kompressors;

Fig. 3

einen Schnitt längs Linie 3-3 in Fig. 1;

Fig. 4

einen Schnitt längs Linie 4-4 in Fig. 1;

Fig. 5

eine Draufsicht auf einen Boden eines Motorgehäuse bildendes zweites Lagerteil;

Fig. 6

eine Ansicht ähnlich Fig. 1 eines zweiten Ausführungsbeispiels eines erfindungsgemäßen Kompressors;

Fig. 7

einen Schnitt längs Linie 7-7 in Fig. 6;

Fig. 8

einen Schnitt längs Linie 8-8 in Fig. 6 und

Fig. 9

einen Schnitt ähnlich Fig. 2 durch ein drittes Ausführungsbeispiel eines erfindungsgemäßen Kompressors.

In the drawing show:

Fig. 1

a longitudinal section through a first embodiment of a compressor according to the invention;

Fig. 2

a longitudinal section rotated through an angle of approximately 90 ° by the first embodiment of the compressor according to the invention;

Fig. 3

a section along line 3-3 in Fig. 1;

Fig. 4

a section along line 4-4 in Fig. 1;

Fig. 5

a plan view of a bottom of a motor housing forming the second bearing part;

Fig. 6

a view similar to Figure 1 of a second embodiment of a compressor according to the invention.

Fig. 7

a section along line 7-7 in Fig. 6;

Fig. 8

a section along line 8-8 in Fig. 6 and

Fig. 9

a section similar to FIG. 2 by a third embodiment of a compressor according to the invention.

A first embodiment of a compressor according to the invention, shown in Figs. 1 to 5, comprises an outer housing designated as a whole by 10, in which a generally designated 12 spiral compressor is arranged, which by a designated as a whole with 14 drive unit is drivable.

The scroll compressor 12 comprises a first compressor body 16 and a second compressor body 18, wherein the first compressor body 16 a above a floor 20 of the same uplifting first, in the form of a Circular involute trained spiral rib 22 and the second compressor body 18 a rising above a floor 24 of the same second in shape a spiral involute trained spiral rib 26, wherein the spiral ribs 22, 26 engage each other and in each case on the bottom surfaces 28th or 30 of the other compressor body 18, 16 sealingly abut, so that between the spiral ribs 22, 26 and the bottom surfaces 28, 30 of the Compressor body 16, 18 form chambers 32, in which a compression a refrigerant takes place via one of the spiral ribs 22, 26 radially outward surrounding intake 34 flows with initial pressure and after the Compressing in the chambers 28 via an outlet 36, provided in the bottom 20th of the first compressor body 16, compressed to high pressure emerges.

In the described first embodiment, the first compressor body 16 firmly held in the outer housing 10, by means of a Separator 40, which in turn on the outer housing 10 within the same is held, the bottom 20 of the first compressor body 16 at a distance engages and tight with an around the outlet 36 extending annular flange 42 of the first compressor body 16, which over the bottom 20 on one of the spiral rib 26 opposite side protrudes, is connected.

This is between the bottom 20 of the first compressor body 16 and the Separator 40, a cooling chamber 44 for cooling the bottom 20 of the first Compressor body 16 is formed, for example, the subject of WO 02/052205 A2, in which the cooling of the scroll compressor 12 is described.

In contrast to the first compressor body 16, the second compressor body 18 about a central axis 46 on an orbital path relative to the first Compressor body 16 movable, wherein the spiral ribs 22 and 26 theoretically abut each other along a line of contact and the line of contact also during the movement of the second compressor body 18 on the orbital path revolving around the central axis 46.

The drive of the second compressor body 18 on the orbital track to the Central axis 46 is effected by the already mentioned drive unit 14, which an eccentric 50, a drive shaft 50 driving the eccentric drive 52, a drive motor 54 and a bearing unit 56 for supporting the Drive shaft 52 includes.

In particular, the eccentric 50 is formed by an eccentric on the drive shaft 52 and thus arranged eccentrically to the central axis 46 Driver 62, which in a fixed to the bottom 24 of the second compressor body 18 connected driver receptacle 64 engages to thus the second compressor body 18 on the orbital path about the central axis 46 to move.

The bearing unit 56 in turn comprises a first bearing body 66, which represents a main bearing body and with a bearing portion 68 the Drive shaft 52 supports in a region 70 and which the driver 62nd carries, wherein the driver 62 preferably in one piece to the area 70th is arranged.

Furthermore, the first bearing body 66 encloses a space 72, in which the Eccentric 50 is arranged and in which a fixed to the Drive shaft 52 connected balancing mass 74 moves.

In addition, the first bearing body 66 extends laterally of the space 72 in Direction of the bottom 24 of the second compressor body 18 and has a the second compressor body 18 facing opening 76 of the space 72nd around extending wings 78, on which the second compressor body 18 with one of the second spiral rib 26 opposite back 80 rests and thus supported so that the second compressor body 18th thereby secured against movement away from the first compressor body 16 is.

The fixation of the first bearing body 66 in the outer housing 10 takes place doing so with retaining arms 82 extending radially from the first bearing body 66 to the Outer housing 10 extend and in this the first bearing body 66 precisely hold.

The first bearing body 66 further has on a holding arms 82 opposite Side on an outer surface 84, on which a within and at a distance from a cylindrical portion 86 of the outer housing 10th extending, preferably also cylindrical housing sleeve 88 of a Motor housing 90 sits, extending to a second floor of the motor housing 90 forming bearing body 92 extends, the distance from the first Bearing body 66 is arranged and forms a bearing portion 94, in which the drive shaft 52 with an end portion 96 coaxial with the central axis 46th is stored.

For additional stabilization of the second bearing body 92 is still on support body 98 supported on the outer housing 10.

The entire motor housing 90 thus extends within the cylindrical Section 86 of the outer housing 10 and at a distance from this.

In the motor housing 90 is between the first bearing body 66 and the second bearing body 92 of the drive motor 54 is arranged, which one on the drive shaft 52 seated rotor 100 and a rotor 100 surrounding Stator 102, wherein the stator 102 of the housing sleeve 88 of the Motor housing 90 is held stably fixed relative to the outer housing 10, so That is, a conventional gap 104 between the rotor 100 and the stator 102nd consists.

In addition, the stator 102 facing the housing sleeve 88 on its Side provided with cooling channels 106 which are parallel to the central axis 46, for example in the form of outer grooves, in the stator 102 over the entire plant side 108 run, wherein the stator 102 via the plant side 108 is supported on the housing sleeve 88.

Between the second bearing body 92 and a bottom part 110 of the outer housing 10 is a free space 112 is provided, which opens up the possibility that at about the bottom portion 110 with approximately vertically extending central axis 46 elevating outer housing 10 forms an oil sump 114, in which on the one hand lubricating oil accumulates due to gravity and on the other hand Lubricating oil for lubricating the compressor according to the invention ready is held.

In the oil sump 114 emerges from the end portion 96 of the Drive shaft 52 and coaxial with this extending oil delivery pipe 116, which has in its interior 118 a conveyor wing 120 and thus acting as an oil pump, which oil from the oil sump 114 in a drive shaft 52 passing lubricating oil passage 122 which pumps via an orifice 124 lubricating oil on an end face 126 of the driver 62 emerge leaves one between the cam receiver 64 and the driver 62nd formed pivot bearing for the movement of the second compressor body 18 lubricate the orbital track.

Furthermore, from the lubricating oil channel 122 branches off a transverse channel 128, which to between the bearing portion 68 of the first bearing body 66 and the Area 70 of the drive shaft 52 formed pivot bearing leads and this lubricates and finally branches from the lubricating oil passage 122 a vent passage 130 off.

The used for lubrication of the driver 62 in the driver seat 64 Oil leaves the driver seat 64 in the area of the area 70 facing opening 132 of the cam receiver 64, then arrives a bottom 134 of the space 70 formed by the first bearing body 66 and from this via drainage channels 136 which communicate with the bottom 134 an oil guide form, in an upper interior 140 of the motor housing 90. Further occurs Oil, the lubrication of the area 70 of the drive shaft 52 in the bearing section 68 serves, on an underside 142 of the bearing portion 68 of this from and thus also in the upper interior 140 of the motor housing 90 a.

The supply of refrigerant to be compressed by the scroll compressor 12 the compressor according to the invention via a suction line 150, which is guided to a suction port 152, which in turn on the outer housing 10 is held, but through this through to the motor housing 90 is guided.

Preferably, the suction port 152 has a sleeve 154 which is the Outer housing 10 of the compressor according to the invention interspersed and in a fixed to the housing sleeve 88 of the motor housing 90 connected recording 156 engages, as shown in FIGS. 1 and 3. The receptacle 156 encloses while a provided in the housing sleeve 88 inlet 158 for the refrigerant, so that this directly into a lower interior 160 of the motor housing 90 may occur between the stator 102 and the second Bearing body 92 is located.

Further, the inlet opening 158 is arranged in the direction of the central axis 46, that the refrigerant in the amount of a winding head 162 of the stator 102 in the lower interior 160 enters, which also projects into the interior 160.

For optimal distribution of the refrigerant in the lower interior 160 is the inlet 158 associated with a deflection unit 164, which two deflection surfaces 166 and 168, the approximately in the radial direction 170 to Center axis 46 through the sleeve 154 inflowing refrigerant so that Main flow directions of the supplied gaseous refrigerant in two opposite Azimuthalrichtungen 172 and 174 to the central axis 46 to the Winding 162 run around and within the housing sleeve 88, the inner wall 176 of which is in the azimuthal directions 172 and 174 spreading refrigerant continues and helps that with the supplied Refrigerant entrained oil deposited on the inner wall 176 is and at this in the direction of in Fig. 5 individually shown second Bearing body 92 runs down. Wherein the bearing body 92 and the Housing sleeve 88 forms substantially occlusive bottom 178, the However, with oil drain holes 180 is provided, from which the separating oil can drain into the oil sump 114.

Due to the closed bottom 178 has in the lower interior 160th the motor housing 90 entering refrigerant substantially not the Possibility, in the free space 112 between the second bearing body 92nd and the bottom part 110, but remains substantially in the inner space 160 for cooling the winding head 162 and then enters starting from the inner space 160 through the cooling channels 106 and the gap 104 between the rotor 100 and the stator 102 in the upper interior 140th over which lies between the first bearing body 66 and the stator 102 to the projecting into the upper interior 140 winding heads 182 to cool.

At the level of the winding head 82 is in the housing sleeve 88, as in Fig. 1 and 4, at least one outlet opening 184 is provided, through which the refrigerant exits from the upper interior 140 of the motor housing 90, in a gap 188, which between the cylindrical portion 88 and the first bearing body 66 - apart from the holding arms 82 - and the motor housing 90 is made and which part an oil separator 190 is. In particular, the gap 188 is in substantially between an inner wall surface 192 of the cylindrical portion 86 of the outer housing 10 and an outer wall surface 194 of the cylindrical Housing sleeve 88 is located, wherein the gap 188 preferably as closed annulus extends around the housing sleeve 88 around.

For generating a flow of the gaseous refrigerant in opposite directions extending azimuthal directions 196, 198 in the space 188 the outlet opening 184 is arranged opposite a deflection unit 200, which deflection surfaces 202 and 204, that from the outlet opening 184 leaking gaseous refrigerant in the azimuthal Divert directions 196 and 198.

But it is also conceivable, several opening into the space 188 Outlet openings 184 and associated therewith deflecting units 200 in Angular distance to provide around the central axis 46 around.

By guiding the gaseous refrigerant in the azimuthal directions 196 and 198, in particular between the inner wall surface 192 and the Outer wall surface 194, occurs due to the always acting radial acceleration of oil droplets in the gaseous refrigerant, an oil separator effect especially in a precipitate of oil released by the Refrigerant is carried on the inner wall surface 192 and the outer wall surface 194, the oil being at a substantially vertical center axis 46 positioned compressor between the outer housing 10 and the Motor housing 90 preferably along the inner wall surface 192 and the Outer wall surface 194 can run in the direction of the oil sump 114, since 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 a starting from the gap 188 in the free space 112 passing There is free space 206 over which the oil ultimately the oil sump 114 can be fed.

In the oil separator 190, the deposition of all takes place from the refrigerant on its way through the interior 160, through the gap 104 and the Cooling channels 106 and the interior 140 entrained oil, in particular at least partially also oil, which at the bottom 142 of the bearing section 68 exits, and oil, which is supplied via the drain channels 136 to the interior 140 has been.

The refrigerant thus substantially freed of oil in the oil separator 190 then flows starting from the gap 188 of the oil separator 190th between the holding arms 82 and thus outside of the first bearing body 66 over in the direction of the suction portion 34 of the scroll compressor 12 and is sucked by this and compressed, the compressed refrigerant through the outlet 36 enters a pressure space 210 which is between a lid 212 the outer housing 10 and the separator body 40 is located and by this a pressure port 214 is discharged.

In a second embodiment of the compressor according to the invention, shown in Figs. 6 to 8, those parts are the same as those of the first Embodiment are identical, provided with the same reference numerals, so that in this respect the contents of the first embodiment Reference is made.

In contrast to the first embodiment, in the second embodiment the suction port 152 'is arranged so that the inlet 158' is at the level of the winding head 182 of the stator 102 and thus the supplied Refrigerant first in the upper interior 140 within the Motor housing 90 enters, then also through the gap 104 between the Rotor 100 and the stator 102 and also provided cooling channels 106 in the lower interior 160 enters to in this the winding head 162 to cool.

In this embodiment, therefore, the outlet opening 184 'in height the winding head 162, and thus the gap 188 'between the Inner wall surface 192 of the outer housing 10 and the outer wall surface 194 the housing sleeve 88 relative to the central axis 46 at the level of the outlet opening 184 ', the gap 188' and thus the oil separator 190 ' However, as seen in the direction of the central axis 46 extend over the entire length of the housing sleeve 88 to the support arms 82 of the first Bearing body 66, so that seen in the direction of the central axis 46, a longer Gap between the outer housing 10 and the housing sleeve 88 for the oil separation is available.

Moreover, the exit port 184 'is also opposite one Deflection unit 200 'associated, the deflection surfaces 202' and 204 'also a deflection of the exiting refrigerant in the azimuthal directions 196th and 198 in the gap 188 'effect.

Since the gap 188 'substantially directly to the free Room 112 adjoins, has in the oil separator 190 'separating oil easily the opportunity to enter the free space 112 and from there into to pass the oil sump 114.

In a third embodiment of a compressor according to the invention, shown in Fig. 9, those parts are the same as those of the first embodiment are identical, provided with the same reference numerals, so that in full reference to the comments on the first embodiment can be taken.

In contrast to the first and second embodiments are in the third embodiment, the drain channels 136 'not so that the oil in the Room 140 enters, but so far through the first bearing body 66 therethrough and through the housing sleeve 88 therethrough in the radial direction to the central axis 46 to the outside, that the oil enters the gap 188 and in this together with the separated in the space 188 oil, preferably by the free space 206, the oil sump 114 in the free space 112 to flow can.

Claims (35)

1. Compressor for refrigerant, comprising
   an outer housing (10),
   a scroll compressor (12) arranged in the outer housing and having a first compressor member (16) arranged stationary in the outer housing (10) and a second compressor member (18) movable relative to the first compressor member (16), said compressor members each having a base (20, 24) and first and second scroll ribs (22, 26), respectively, rising above the respective base (20, 24), said ribs engaging in one another such that the second compressor member (18) is movable relative to the first compressor member (16) on an orbital path about a central axis (46) for the purpose of compressing the refrigerant,
   a drive unit (14) for the second compressor member (18) with an eccentric drive (50), a drive shaft (52), a drive motor (54) arranged in a motor housing (90) and having drawn-in refrigerant flowing around it as well as a bearing unit (56) for the drive shaft, said bearing unit comprising a first bearing member (66) connected to the outer housing (10),
   characterized in that the refrigerant flows through an oil separator (190) after flowing around the drive motor (54) and prior to entering the scroll compressor (12), said oil separator being arranged in the outer housing (10) between this and the drive unit (14).
2. Compressor as defined in claim 1, characterized in that the oil separator (190) is arranged in a space (188) located between the outer housing (10) and the drive unit (14) in a direction transverse to the central axis (46).
3. Compressor as defined in claim 1 or 2, characterized in that the space (188, 206) between the outer housing (10) and the drive unit (14) extends essentially over the entire extension of the drive unit (14) in a direction parallel to the central axis (46).
4. Compressor as defined in claim 2 or 3, characterized in that the space (188, 206) surrounds the drive unit (14).
5. Compressor as defined in any one of claims 2 to 4, characterized in that oil separated by the oil separator (190) in the space (188, 206) moves In the direction of the oil sump (114) and refrigerant flows in the direction of an intake chamber (34) of the scroll compressor (12).
6. Compressor as defined in any one of claims 2 to 5, characterized in that refrigerant enters the space (188, 206) after cooling the drive motor (54).
7. Compressor as defined in any one of the preceding claims, characterized in that the oil separator (190) is arranged on an outer side of the first bearing member (66) at least in sections.
8. Compressor as defined in claim 7, characterized in that the oil separator (190) is arranged so as to surround the first bearing member (66) at least in sections.
9. Compressor as defined in any one of the preceding claims, characterized in that the oil separator (190) is arranged on an outer side of the motor housing (90) at least in sections.
10. Compressor as defined in claim 9, characterized in that the oil separator (190) is arranged so as to surround the motor housing (90) at least in sections.
11. Compressor as defined in any one of the preceding claims, characterized in that the oil separator (190) uses part of the space (188) located between the outer housing (10) and the drive unit (14).
12. Compressor as defined in claim 11, characterized in that the space (188) between the outer housing (10) and the drive unit (14) used by the oil separator (190) is an annular space.
13. Compressor as defined in any one of the preceding claims, characterized in that the refrigerant experiences a deflection in an azimuthal direction (196, 198) in relation to the central axis (46) when entering the oil separator (190).
14. Compressor as defined in claim 13, characterized in that the refrigerant experiences a deflection in opposite azimuthal directions (196, 198).
15. Compressor as defined in any one of the preceding claims, characterized in that the refrigerant is guided in the oil separator (190) essentially on an azimuthal path around the central axis (46).
16. Compressor as defined in any one of the preceding claims, characterized in that the refrigerant flows in the oil separator (190) along an inner wall surface (192) of the outer housing (10).
17. Compressor as defined in any one of the preceding claims, characterized in that oil settling in the oil separator (190) flows into an oil sump (114) on a path extending outside the motor housing (90).
18. Compressor as defined in any one of the preceding claims, characterized in that the oil sump (114) is arranged in the outer housing (10) on a side of the drive motor (54) located opposite the first bearing member (66).
19. Compressor as defined in any one of the preceding claims, characterized in that the refrigerant flows around an outer side of the first bearing member (66) on its way from the oil separator (190) to the intake chamber (34) of the scroll compressor (12).
20. Compressor as defined in any one of the preceding claims, characterized in that the oil separator is located on a side of the supporting arms facing the oil sump, said supporting arms connecting the first bearing member to the outer housing.
21. Compressor as defined in claim 20, characterized in that the refrigerant passes between the supporting arms (82) in the direction of an intake chamber (34) of the scroll compressor (12) after flowing through the oil separator (190).
22. Compressor as defined in any one of the preceding claims, characterized in that the refrigerant flows directly into the motor housing (90) when entering the compressor and enters the oil separator (190) after flowing through the motor housing (90).
23. Compressor as defined in any one of the preceding claims, characterized in that the refrigerant entering the motor housing (90) experiences a deflection in at least one azimuthal direction (172, 174).
24. Compressor as defined in claim 23, characterized in that the refrigerant entering the motor housing (90) experiences a deflection in opposite azimuthal directions (172, 174).
25. Compressor as defined in any one of the preceding claims, characterized in that the refrigerant enters the motor housing (90) at the level of a first winding head (162, 182) when seen in the direction of the central axis (46).
26. Compressor as defined in claim 25, characterized in that the refrigerant, when seen in the direction of the central axis (46), flows through the drive motor (54) from the first winding head (162, 182) in the direction of a second winding head (182, 162).
27. Compressor as defined in claim 25 or 26, characterized in that the refrigerant exits from the motor housing (90) at the level of the second winding head (182, 162).
28. Compressor as defined in any one of the preceding claims, characterized in that oil separated in the motor housing (90) exits from the motor housing (90) through oil discharge openings (180) in a base (92) of the motor housing (90) in order to reach the oil sump (114).
29. Compressor as defined in any one of the preceding claims, characterized in that the first bearing member (66) has an oil guide (134, 136) for oil used for the lubrication of the eccentric drive (50).
30. Compressor as defined in claim 29, characterized in that the oil guide (134, 136) opens into an interior space (140) of the motor housing (90).
31. Compressor as defined in claim 30, characterized in that considerable portions of the oil are conveyed to the oil separator (190) by the refrigerant flowing through the interior space (140) of the motor housing (90).
32. Compressor as defined in claim 29, characterized in that the oil guide (134, 136) opens into the space (188).
33. Compressor as defined in any one of the preceding claims, characterized in that the drive shaft (52) has a bore (122) for lubricating oil.
34. Compressor as defined in claim 33, characterized in that lubrication of a rotary bearing (68, 70) for the drive shaft (52) in the first bearing member (66) is brought about via the bore (122) for lubricating oil.
35. Compressor as defined in claim 33 or 34, characterized in that lubrication of the eccentric drive (50) is brought about via the bore (122) for lubricating oil.

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