EP2507566A2

EP2507566A2 - Compressor

Info

Publication number: EP2507566A2
Application number: EP10781444A
Authority: EP
Inventors: Wolfgang Etter; Arno Goerlich
Original assignee: GEA Bock GmbH
Current assignee: Bock GmbH
Priority date: 2009-12-02
Filing date: 2010-11-23
Publication date: 2012-10-10
Also published as: AU2010327140A1; CN102639872B; JP2013511657A; JP5503749B2; WO2011066914A4; WO2011066914A3; US20120234038A1; BR112012012840A2; DE102009056518A1; WO2011066914A2; US9021830B2; AU2010327140B2; CN102639872A

Abstract

The invention relates to a compressor (10, 200) for compressing refrigerant, comprising a drive mechanism arranged in a drive mechanism chamber (14) bounded at least partially by a drive mechanism housing (12), a suction gas volume (46) and a high pressure volume (48), wherein the high pressure volume (48) is in fluid communication via a second fluid connection (74) with the driving mechanism chamber (14), wherein the compressor further comprises a first fluid connection (54, 254) that can be brought into fluid communication or is in fluid communication with an oil-conducting volume (205) of a refrigeration system or of the compressor (10, 200), and wherein an oil separator (56) is arranged in the first fluid connection (54, 254).

Description

compressor

The invention relates to a compressor according to the preamble of patent claim 1.

Compressors for compressing refrigerant are now widely used. This is the case, for example, in the field of (room) air conditioning as well as in the field of cooling a wide variety of goods. In the field of (room) air conditioning, among other things, the air conditioning of residential and office buildings and the air conditioning of motor vehicles (for example, the air conditioning of passenger compartments of

Passenger cars and the air conditioning of cabs in trucks) and the air conditioning in the field of railway (air conditioning of trains, trams and the like) to call. In the field of cooling, refrigeration compressors are found, inter alia, in the area of transport refrigeration (eg cooling of semitrailers of

Lorries, cooling of railway wagons and the like), as well as in the stationary area, for example in the field of supermarket refrigeration (refrigerated counters, cooling of warehouses in supermarkets and other warehouses) use.

An example of a refrigerant compressor with an engine, which in a

Engine room is arranged, which (partially or in total) by a

Engine housing is limited, can be found in the field of air conditioning of

Passenger cars. The compressors for passenger cars are usually compressors of the swashplate design. In this design, the engine on a swash plate or a swivel ring which (r) pivotally connected to a with a Motor is arranged in operative engagement drive shaft.

Characterized in that the swash plate or the swivel ring, which (r) arranged with pistons, which are arranged in cylinder bores, pivotally to the drive shaft, the stroke volume of the piston and thus the delivery volume of the compressor can be influenced. The delivery volume or the piston stroke of the compressor can be adjusted by the pressure prevailing in the engine room. To control or control the piston stroke, these compressors have a low-pressure fluid connection, which the engine room with a suction gas volume in the form of a suction chamber in

Fluid communication brings, as well as a high-pressure fluid connection, which the

Engine room with a high-pressure volume (pressure chamber) in fluid communication brings on. As a result, the engine room can be supplied with high-pressure refrigerant via the high-pressure fluid connection, thereby increasing the engine room pressure. The pressure in the engine room can be reduced via the low-pressure fluid connection.

In the known compressors of Schwenkscheibenbauart is about

oil lubricated compressor. Due to the rotational movement of the swash plate, the movement of other moving components and the pressure changes in the engine room located oil is whirled up and forms an oil mist (oil mist lubrication). The im

Engine room resulting oil mist is via the low-pressure fluid connection

(between engine room and suction chamber) in the suction chamber and spent there together with the refrigerant in the cylinder. After compression, the oil mist is partially conveyed back into the engine room via the high pressure fluid connection, while other parts of the oil pass through a refrigerant circuit

Refrigeration system in which the compressor is arranged (in particular over in

Refrigerant circuit arranged cooling or heat exchanger in the form of a condenser and an evaporator, as well as via a circulating expansion element) back into the suction gas volume or the suction chamber. To be safe

To ensure lubrication, while the oil is pumped in a circle. Refrigerant compressors of this type have an oil charge of about 100 g of oil per 1 liter of refrigerant.

Even with compressors that are not constructed in the swash plate type (e.g.

Compressor with constant piston stroke) oil enters the refrigerant circuit and from there back into the suction chamber of the compressor, although in these compressors usually no fluid connection between the suction chamber and engine room exists.

Compressors for the air conditioning of passenger compartments of passenger cars are a mass product, which is replaced in the event of a defect. A repair is not planned. Likewise, no maintenance of the same is provided during the life of such a compressor. However, this is not the case in the range of compressors with greater cooling capacity. While compressors in passenger cars have relatively low operating lives, larger compressors, for example, in buses or for the refrigeration of goods in trucks and warehouses are almost continuously in operation. Due to the high operating times, regular maintenance of the compressors is essential. The regular maintenance also involves an oil change. If there is oil in the entire refrigerant circuit, part of the used oil remains in the compressor or in the refrigeration system during the oil change. This would shorten the maintenance intervals.

Furthermore, due to the oil present in the entire refrigerant circuit energy disadvantages, which are not significant in the field of passenger car air conditioning, but provide for larger compressors for energy losses.

Accordingly, it is an object of the present invention to provide a compressor which operates at low operating costs and which compared to the prior art

offers energetic benefits.

This object is achieved by a compressor for compressing

Refrigerant solved according to claim 1. It should be noted at this point that the invention is not limited to a compressor of the swash plate type. The invention may be used in all conceivable reciprocating compressors such as e.g. Reciprocating compressors in series, V or W design, axial piston compressors and radial piston compressors with contant piston stroke and in all conceivable rotary piston compressors such. Screw, rotary piston, scroll / scroll compressors are ralisiert.

Further features of the invention are specified in the subclaims.

The invention will now be described by way of example with reference to the accompanying drawings, given by way of preferred embodiments. In the drawings show 1 shows a first embodiment of a compressor according to the invention in a schematic representation; and

Fig. 2 shows a second embodiment of a compressor according to the invention in turn in a schematic representation.

In the first embodiment shown in Fig. 1 is a

Compressor 10 of the swash plate design. This has an engine housing 12, which limits an engine room 14 (crank chamber). In the engine room 14, a swash plate 16 is arranged. In alternative embodiments, the

Swivel disk 16 may also be designed in the form of a swivel ring. The

Pivot plate 16 is rotationally driven by a drive shaft 18 and is about sliding blocks (not shown in Fig. 1) with piston 22 in operative engagement. In the first embodiment shown here, the compressor 10 has five pistons 22.

Alternatively, however, any other number of pistons is conceivable.

The swash plate 16 which is rotatably connected to the drive shaft 18 is connected to the drive shaft 18 by means of a (not shown tilting or

Swivel mechanism ', indicated by a double arrow 20) articulated so that it is adjustable in its inclination (inclination angle 24) of the drive shaft. By changing the inclination angle 24 between the drive shaft 18 and the

Swivel disk 16, the delivery volume of the compressor can be controlled or controlled. The further the inclination angle 24 deviates from 90 °, i. the smaller the

Inclination angle is, the larger the delivery volume, since the stroke of the piston 22, which are arranged in respective piston associated cylinder bores 26, the smaller, the inclination angle 24 is.

The drive shaft 18 is arranged via a in the engine housing 12

Sealing element 28, which is designed as a ring seal and the engine compartment 14 fluid-tight seals against the environment, introduced into the engine compartment 14. The drive shaft 18 is mounted in two places in the compressor 10, namely by means of a first bearing 30, which is arranged in the engine housing 12 and by means of a second bearing 32, which is arranged in a cylinder block 34, in which also the cylinder bores 26 are arranged. Also limited by the engine housing 12, the compressor 10, an oil reservoir 36, which is in fluid communication with the engine room 14 via an opening 38. Both in the oil reservoir 36 and in parts of the engine room 14 is an oil sump 40, which serves for the lubrication of the compressor 10.

The described first embodiment of a compressor 10 according to the invention also has a cylinder head 42, which is delimited by a cylinder head housing 44. In the cylinder head 42, a suction gas volume 46 is arranged in the form of a suction chamber or a suction chamber. Furthermore, a high-pressure volume 48 in the form of a chamber-shaped pressure chamber is arranged in the cylinder head 42. As indicated by a first arrow 50, refrigerant to be compressed flows out of the suction gas volume 46 via an opening (suction valve, suction plate) (not shown) into the cylinder bores 26, which after the compression process, as indicated by a second arrow 52, enters the high-pressure volume 48 is ejected.

Between the engine room 14 (as the oil-carrying volume of the compressor 10) and the Sauggasvolumen 46, a first fluid connection 54 is arranged (which in the embodiment described here with the low-pressure fluid connection of the

Swash plate compressor 10 coincides). Arranged in the first fluid connection 54 is an oil separator 56, which in the described first embodiment is designed as a centrifugal oil separator and has an oil separator inlet 66 and an oil separator outlet 72. The first fluid connection 54 has a

Ölabscheiderzuführabschnitt 58 and a Olabscheiderabführabschnitt 60. A first end 62 of the Ölabscheiderzuführabschnitts 58 of the first fluid connection 54 is in fluid communication with the engine room 14, while a second end 64 of the Ölabscheiderzuführabschnitts 58 of the first fluid connection 54 with the

Ölabscheidereingang 66 is in fluid communication. The Olabscheiderabführabschnitt 60 of the first fluid connection 54 in turn has a first end 68 and a second end 70, wherein the first end 68 of the Ölabscheiderabführabes 60 with the

Oil separator output 72 is in fluid communication. The second end 70 of the

Ölabscheiderabführabes 60 of the first fluid connection 54 is connected to the

Suction gas volume 46 in fluid communication. It should be noted at this point that the oil separator supply section 58 of the first fluid connection 54 need not necessarily be in fluid communication with the engine compartment 14 as the oil carrying volume. In alternative embodiments, it is also conceivable for the first end 62 of the oil separator feed section 58 to be arranged in the compressor 10 with a low-pressure volume or a low-pressure side of a refrigeration system (known in principle to the person skilled in the art and described below in the description of the second embodiment) is, as oil-carrying volume, in fluid communication. Ie in alternative

Embodiments, it is conceivable that the first fluid connection not with the

Low-pressure fluid communication of the compressor 10 coincides, but represents a separate from this, its own fluid connection, which brings the low-pressure side of the refrigeration system (via the Ölfiter 56) in fluid communication with the Sauggasvolumen 46.

Furthermore, the compressor according to the invention on a second fluid connection 74, via which the engine room 14 with the high-pressure volume 48 in

Fluid communication (which in the first embodiment coincides with the high pressure fluid connection of the swash plate type compressor 10). The second

Fluid connection 74 has a drive media portion 76 which is in fluid communication with high pressure volume 48 at its first end 78. At its second end 80, the drive media section 76 is provided with a drive media inlet 82 of an injector 84 disposed in the second fluid connection 74 and one in the second

Fluid connection 74 arranged jet pump 84 in fluid communication. The second fluid connection 74 further includes an exit section 86, which in turn has a first end 88 and a second end 90. The first end 88 of the

Exit section 86 stands with a arranged on the injector 84

Injector outlet 92 in fluid communication while the second end 90 of the

Exhaust section 86 is in fluid communication with the engine compartment 14.

Since the engine room 14 via the second fluid connection 74 and via the injector 84 disposed therein with the high-pressure volume 48 of the compressor 10 in

(continuous) fluid communication is the engine room 14th

continuously charged with pressurized refrigerant. The amount of refrigerant flowing from the high-pressure volume 48 into the engine compartment 14 is determined or limited by an injector nozzle 93 arranged in the injector 84. This is necessary because it is necessary for power regulation of the compressor 10, the pressure in

Engine room 14 against the prevailing in the suction volume 46 suction pressure (depending on the load case) to maintain a higher level.

The pressure to be set in the engine compartment 14 is via a point reducible cross section in the form of a pulse valve 100, which is arranged in the Ölabscheiderabführab 60 of the first fluid connection 54 and with an electronic

Regulating device 101 is regulated. If the pressure prevailing in the engine compartment 14 exceeds the desired pressure, the pulse valve 100 is opened while it is closed when the desired pressure is undershot. In the pulse valve 100, which is used in the first embodiment, it is a solenoid operated solenoid valve, which can be closed by current flow in the associated electromagnet 103. As Stell- or

Control variable is not used in the described first embodiment

Engine room pressure, but the pressure prevailing in the suction gas volume 46 pressure. It should be mentioned at this point that instead of a pulse valve 100 also has an (adjustable) aperture, an adjustable slide or another valve in the

Ölabscheiderabführabschnitt 60 of the first fluid connection 54 would be conceivable.

Due to the pressure difference between in the engine room 14 and in the

Suction gas volume 46 prevailing pressure flows (with open pulse valve 100) refrigerant, which entrains an upset due to the flow conditions and due to the rotational movement of the swash plate 16 oil mist over the Ölabscheiderzuführabschnitt 58 of the first fluid connection 54 and the

Oil separator inlet 66 into the Zentrifugalölabscheider 56. As it flows into the Zentrifugalölabscheider 56, the gas is set in rotation, which are thrown due to the centrifugal forces in the oil mist oil droplets to an oil separator housing 94, which collect in a lower portion of Zentrifugalölabscheiders in a Olabscheidereservoirs 96. In order not to re-whirl up the oil which is present in the oil separator reservoir 96 and running downwards on the wall of the oil separator housing 94 in the form of an oil film, the centrifugal oil separator 56 has a T or mushroom-shaped baffle plate or a T-shaped or mushroom-shaped baffle plate 98 which is deflected from the offset in rotation and now freed from oil mist refrigerant in the direction of the Ölabscheiderausgangs 72 and this leaves again. In the injector 84 and the jet pump is by a fluid jet (driving medium), which enters through the Treibmedieneintritt 82 in the injector 84, a pumping action generated via a Saugmedieneintritt 102 of the injector 84 a medium to be sucked, which in this case the oil from the Centrifugal oil separator 56 (which with

Refrigerant is mixed) is, sucks, accelerated and expelled through the injector 92 again. To supply oil to the suction media inlet 102, the latter is in fluid communication via a third fluid connection 104 with an oil outlet 106 of the centrifugal oil separator 56. The entrained oil is doing at the second end 90 of the

Outlet portion 78 of the second fluid connection 74 is introduced via a there arranged engine room inlet 108 in the engine compartment 14, wherein the

Engine room inlet 108 in the area to be lubricated points of the compressor 10, in the presently described first embodiment on the swash plate 16th

is arranged so that it is constantly supplied with oil or lubricant. Additionally or alternatively, it would also be conceivable that further engine room inlets 108 are arranged in the compressor, which supply additional oil to be lubricated points (for example bearings) (see also the second described below

Embodiment of a compressor according to the invention).

The fact that the oil which passes through the injector 84 has or has mixed refrigerant means that the entrained refrigerant, after passing through an injector nozzle (expansion element), is passed through the injector.

(due to expansion) is cooled, resulting in a cooling of the oil. As a result, a heating of the engine compartment 14 and the engine housing 12th

avoided or reduced. The idea of the invention therefore also includes the arrangement of a device for oil cooling in a compressor. This idea is not limited to compressors having an oil separator. Rather, compressors are also conceivable that have no oil separator and still a device for oil cooling. So it is conceivable, for example, that the injector 84 does not have a

Oil separator (Zentrifugalölabscheider 56) but is supplied via an oil pump with an oil-refrigerant mixture, wherein the entrained oil, which serves the lubrication, is cooled when flowing through the expansion device in the form of the injector (especially by the expansion of the entrained refrigerant). The basic idea to implement an Olkühlvorrichtung in a compressor is not limited to the use of an injector or any other expansion device. Also, an oil cooling by an air, - water, or refrigerant cooled or a

otherwise cooled oil cooler, which may be located at any point of a compressor oil circuit, is conceivable.

As already mentioned above and can be seen again from FIG. 2, the compressor does not have to be a compressor of the swash plate design. The compressor 200 shown in FIG. 2 is a reciprocating compressor in a series construction according to the oscillating delivery principle with a constant piston stroke. In the embodiment shown in FIG. 2, the compressor 200 has two pistons 202. The pistons 202 are operatively connected to the piston 202 itself and the drive shaft 18 connecting rod 204 with the same. Of course, the number of pistons 202 is not limited to two. Any number of pistons 202 is conceivable.

The compressor 200 according to the second embodiment also has a suction gas volume 46, a high-pressure volume 48, and an engine room 14. A second and third fluid connection 74, 104, and an injector 84 are analogous to the first

Embodiment arranged. That the second fluid connection 74 is in turn arranged between the high-pressure volume 48 and the engine compartment 14 and permits fluid communication between the high-pressure volume 48 and the engine compartment 14 or the locations to be lubricated in it (bearings, seals, etc.). In the second fluid connection 74, an injector 84 or a jet pump is arranged analogously to the first embodiment. The third fluid connection 104 fluidly communicates the oil separator 56 with the injector 84.

All components already known from the first embodiment

Designated reference numerals correspond in their design and functionality to those of the first embodiment, so that is omitted in the description of the present second embodiment, a repeated mention or description. As a result, be the differences between the first and the second

Embodiment explained.

In contrast to the compressor 10 of the swash plate type (first described

Embodiment), the compressor 200 of the second embodiment, an in Compared to the first embodiment, modified first fluid connection 254. Although this also has a Ölabscheiderzuführabschnitt 258 and a

Oil separator Abführabschnitt 60, wherein the Ölabscheiderabführabschnitt 60 in its arrangement and functionality of the Ölabscheiderabführabschnitt 60 of the first

beschrienenen embodiment corresponds; however, the oil separator supply section 258 of the second possible embodiment differs in arrangement and functionality from the oil separator supply section 58 of the first embodiment. The oil separator supply section 258 is connected at a first end 262 via a suitable connection (e.g., connection device) to a low-pressure side 205 of a refrigeration system (the refrigeration system is not shown in the drawings, the basic structure of a refrigeration system and its refrigeration cycle is known to those skilled in the art)

Fluid communication can be brought. This will ensure that oil that is in the

Refrigerant circuit of the refrigeration system is located (oil, which after the compression process via the high pressure volume 48 in the refrigerant circuit of the refrigeration system, in which the compressor 200 is arranged), from the low pressure side of the refrigeration system, which also (like the engine room 14) an oil-carrying volume of Represents refrigeration system, passes through the oil filter 56 back into the engine room 14 of the compressor 200. For this purpose, a second end 64 of the Ölabscheiderzuführabschnitts 258 of the first

Fluid connection 254 analogous to the first embodiment with the oil separator 66 in fluid communication. The low-pressure side 205 of the refrigeration system is the portion of the refrigerant circuit which is under low pressure, i. In the described embodiment, it is contemplated to fluidly communicate the first end 262 of the first fluid connection 254 with a portion of the refrigerant circuit that communicates between the expansion device and an evaporator of the refrigeration system is arranged. Such a construction makes it possible to provide for the lubrication of the compressor 200 with the oil that has entered the refrigerant circuit.

The delivery volume of the second embodiment of a compressor according to the invention is controlled by switching on and off of the compressor 200. This makes it possible to dispense with the pulse valve 100, since by a suitable choice of the flow rates of the first, second and third fluid connection 54, 74, 104 ideal (preferably approximately constant) conditions, in particular an ideal oil supply to be lubricated Jobs can be guaranteed. The flow rates, which are defined as the amount of refrigerant / refrigerant oil mixture / oil per time flowing through the respective fluid connection 54, 74, 104, can be determined, for example, by a suitable geometry of the

Cross-section of the fluid connections 54, 74, 104 and / or a suitable choice of

Injectors 84 are ensured. Alternatively, of course, also in this embodiment, the arrangement of locations of reduced or reducible cross-section (such as diaphragms, valves) is conceivable.

In the second embodiment, the second Fiuidverbindung 74 stands with a

Engine room inlet 206 in fluid communication, which is in a tubular

Lubricant supply channel 208 opens. The lubricant supply channel 208 is in turn in Fiuidverbindung with the first bearing 30 and with the first sealing member 28, so as to ensure a lubrication of the first bearing 30 and an optimal function of the sealing element 28. It is of course conceivable that a compressor according to the invention may have a plurality of engine room inlets 208, which are in fluid communication with the second fluid connection, whereby a plurality of points to be lubricated are supplied with lubricant. This consideration also applies to the first

Embodiment. Alternatively or additionally, it is also conceivable that the

Engine room inlet 208 (in the first embodiment 108) is in fluid communication with, for example, the (then correspondingly formed or branched) lubricant supply channel 208 having a plurality of locations to be lubricated. The supply of the points to be lubricated of the compressor 200 is analogous to the first embodiment.

In both described embodiments, as well as in alternative

Embodiments, it is conceivable that at least parts of the oil filter 56 (e.g.

Oil separator housing 94 and / or the baffle plate 98 and / or other components of the oil filter 56 or the entire oil filter 56 are integrally formed with the compressor housing and thus manufactured in one operation with the housing manufacturing, e.g. can be poured. The same applies to the first, second and third Fiuidverbindung 54, 74, 104, 254, which may also be partially or wholly integrally formed with the compressor housing or may be arranged or formed in this.

The idea of the invention includes not only a compressor 10, 200, which is designed according to the invention, but also a corresponding one Specify refrigeration system with a refrigerant circuit, which has a high pressure side (high pressure volume) and a low pressure side (low pressure volume) 205, and a compressor 10, 200 according to the invention, as defined above by the figure description and by the appended claims. Other components of the refrigerator (condenser, expansion element and evaporator) are familiar to the expert and also described in more detail above.

At this point it should be noted that it is in the oil separator 56

Of course, it does not have to be a centrifugal oil separator, but any other oil separator, e.g. an oil separator with sieve bodies or filter elements is conceivable.

In summary, the following points in particular should be mentioned again:

1. The entrained oil is separated by a Zentrifugalölabscheider from the gas stream and passed through the rotation and gravity to the bottom of the separator.

2. For the removal of the collecting oil is (in the case of the first preferred embodiment) existing for power adjustment bypass, which between the high pressure volume 40 and the engine room 14 in the form of the first

Fluid connection 54 is formed used. The pressure difference between

Engine room 14 and the high pressure volume 40 makes it possible to operate the injector or the jet pump 84, which sucks the collected oil from the oil separator 56 and via corresponding fluid connection (outlet section 86 of the second

Fluid connection 74) transported to the required lubrication points.

3. The fact that the entrained refrigerant after passing through an injector nozzle (an expansion device, which is arranged in the injector), a cooling of the

Refrigerant and the oil conditionally, an undesirable heating of the

Engine room 14 and the engine housing 12 avoided or at least reduced.

Such a construction ensures that the highly loaded components of the compressor are constantly supplied with lubricant.

However, while the invention will be described in terms of embodiments having fixed feature combinations, it also encompasses the other conceivable advantageous ones

Combinations as specified in particular, but not exhaustive, by the subclaims. All disclosed in the application documents features are claimed as essential to the invention, as far as they are new individually or in combination over the prior art.

LIST OF REFERENCE NUMBERS

10 compressors

12 engine case

14 engine room

16 swashplate

18 drive shaft

20 double arrow

22 pistons

24 tilt angle

26 cylinder bore

28 sealing elements

30 first camp

32 second camp

34 cylinder block

36 oil reservoir

38 opening

40 oil sump

42 cylinder head

44 cylinder head housing

46 suction gas volume

48 high pressure volume

50 first arrow

52 second arrow

54, 254 first fluid connection Zentrifugalölabscheider / oil separator

, 258 Olabscheiderzuführabschnitt the first fluid connection

54

Olabscheiderabführabschnitt the first fluid connection

54

, 262 first end of 58 and 258, respectively

second end of 58 and 258 respectively

Ölabscheidereingang

first end of 60

second end of 60

Ölabscheiderausgang

second fluid connection

Drive Media Portion of Second Fluid Connection 74 First End of FIG. 76

second end of 76

Driving media entry

Injector / ejector

exit section

first end of 86

second end of 86

injector outlet

injector nozzle

Ölabscheidergehäuse

Ölabscheidereservoir

flapper

0 pulse valve

2 suction media inlet

4 third fluid connection

6 oil leakage

8 engine room inlet

0 compressor

2 pistons

4 connecting rods

5 low pressure side of a refrigeration system Engine room inlet Lubricant intake I

Claims

claims

A compressor (10, 200) for compressing refrigerant with one in at least one

partially by an engine housing (12) limited engine room (14)

arranged engine, a Sauggasvolumen (46) and a high pressure volume (48), wherein the high pressure volume (48) via a second fluid connection (74) with the

Engine room (14) is in fluid communication,

characterized in that

the compressor further comprises a first fluid connection (54, 254), which with an oil-carrying volume (205) of a refrigeration system or the compressor (10, 200) in

Fluid communication can be brought or is in fluid communication, wherein in the first fluid connection (54, 254) an oil separator (56) is arranged.

2. Compressor according to claim 1,

characterized in that

the oil-carrying volume (205) is the suction gas volume (46) of the compressor (10, 200) or a low-pressure volume of the refrigeration system.

3. compressor (10, 200) according to any one of the preceding claims,

characterized in that

the oil separator (56) has a centrifugal oil separator.

4. compressor (10, 200) according to any one of the preceding claims,

characterized in that

the oil separator (56) has an oil outlet (106), which via a third

Fluid connection (104) with the second fluid connection (74) between the

High pressure volume (48) and the engine room (14) is in fluid communication.

5. compressor (10, 200) according to claim 4,

characterized in that

the oil outlet (106) with one in the second fluid connection (74) between

High-pressure volume (48) and engine room (14) and is in fluid communication with the second fluid connection (74) in fluid communication injector (84) arranged there and in fluid communication with the second fluid connection (74) in fluid communication in fluid communication.

6. compressor (10, 200) according to claim 5,

characterized in that

the injector (84) or the jet pump a Treibmedieneintritt (82), a

Suction media inlet (102) and an injector outlet (92), wherein the

Drive media inlet (82) is in fluid communication with the high pressure volume (48) via a drive media section (76) of the second fluid connection (74) disposed between the high pressure volume (48) and the drive media inlet (82), further comprising the injector exit (92). an exit portion (86) of the second fluid connection (74) disposed between the injector exit (92) and the engine compartment (14) being in fluid communication with the engine compartment (14), and wherein the suction media inlet (102) communicates via the third fluid connection (104) disposed between the suction media inlet (102) and the oil outlet (106) of the oil separator (56) is in fluid communication with the oil outlet (106) of the oil separator (56).

7. compressor (10, 200) according to any one of the preceding claims, in particular according to one of claims 4 to 6,

characterized in that

the second fluid connection (74) is in fluid communication with at least one engine room inlet (108; 206) arranged in the engine housing (14), this being arranged in the region of a lubrication point (16; 30) to be lubricated.

8. compressor (10, 200) according to any one of the preceding claims,

characterized in that

the oil separator (56) has an oil separator inlet (66) and an oil separator outlet (72), the oil separator inlet (66) being connected via an oil separator feed section (58) of the first fluid connection (54) between the engine compartment (14) of the first fluid connection (54)

Compressor (10, 200) or a low pressure volume of the refrigeration system and the

Olabscheidereingang (66) is arranged, with the engine room (14) or a

Low-pressure volume of the refrigeration system is in fluid communication, and the Olabscheiderausgang (72) via a Olabscheiderabführabschnitt (60) of the first

Fluid connection (54, 254), which is arranged between the Olabscheiderausgang (72) and the Sauggasvolumen (46), with the Sauggasvolumen (46) in

Fluid communication is.

9. compressor (10, 200) according to any one of the preceding claims,

characterized in that

in the first fluid connection (54, 254) a site reduced or reducible

Cross-section, in particular a valve or a diaphragm is arranged.

10. compressor (10, 200) according to claim 9,

characterized in that

the location of reduced or reducible cross-section is a pulse valve (100).

11. compressor (10, 200) according to claim 9 or 10,

characterized in that

the location of reduced or reducible cross-section is located in the oil separator removal section (60) of the first fluid connection (54, 254).

12. compressor (10, 200) according to any one of the preceding claims,

characterized in that

the engine comprises a swashplate (16) or a swivel ring.

13. compressor (10, 200), in particular according to one of the preceding claims,

characterized in that

the compressor (10, 200) comprises an oil cooling device.

14. A compressor according to claim 13,

characterized in that

the oil cooling device has an expansion element.

15. A compressor according to claim 13 or claim 14,

characterized in that

the oil cooling device is disposed in an injector (84).