EP2795204A2

EP2795204A2 - Compressor

Info

Publication number: EP2795204A2
Application number: EP12824900.0A
Authority: EP
Inventors: Arno Görlich
Original assignee: GEA Bock GmbH
Current assignee: Bock GmbH
Priority date: 2011-12-23
Filing date: 2012-12-24
Publication date: 2014-10-29
Anticipated expiration: 2032-12-24
Also published as: CN104114959B; EP2795204B1; US20150300337A1; CN104114959A; WO2013091899A3; WO2013091899A2

Abstract

The invention relates to a compressor (10, 100), comprising a compressor housing (15), a drive mechanism (12), and a compressing unit (14) having one or several compression levels (14-1, 14-2) for compressing a cooling agent, wherein the compressor (10, 110) is further provided with one or several cooling agent feeder units (20, 36) for feeding cooling agents to the compressing unit (14) and with one or several cooling agent discharge units (24, 38) for discharging cooling agents from the compressing unit (14). At least one segment of the one cooling agent feeder unit or at least one segment of at least one, in particular each one of the several cooling agent feeder units (20, 36), is arranged thermally separated from the one cooling agent discharge unit or at least one, in particular each one of the several cooling agent discharge units (24, 38).

Description

compressor

The invention relates to a compressor according to the preamble of patent claim 1, as well as a refrigeration system according to claim 15.

Compressors, as they are known from the preamble of claim 1, have a drive device and a compression device. For example, the drive device is often an electric motor. The compression device is designed in one or more stages, which means that the compressor, for example, compresses refrigerant from a low pressure (suction pressure) to an intermediate pressure in a first stage, wherein the intermediate pressure refrigerant is then fed to a second stage, in which it High pressure (final pressure) is compressed.

Frequently, however, the efficiency of two-stage compressor is not optimal. This fact is becoming increasingly important when "new natural" refrigerants, such as R744 (C0 ₂ ) are to be used, which make special demands on the conditions of the compression process.

Based on the prior art discussed above, it is therefore an object of the present invention to provide a compressor which has an increased efficiency compared to the compressors according to the prior art or energetically for a

1

CONFIRMATION COPY Operation with all common refrigerants is suitable. Furthermore, it is an object of the present invention to provide a correspondingly designed refrigeration system

This object is achieved by a compressor according to claim 1, and a refrigeration system according to claim 15.

According to the invention, a compressor has a compressor housing, a drive device and a compression device with one or more compression stages for compressing a refrigerant. The compressor further comprises at least one cold ^¬ mittelzuführvorrichtung for supplying refrigerant to the compression device, and at least one Kältemittelabführvorrichtung for discharging refrigerant from the compression device, wherein at least a portion of the Kältemittelzuführvor ^¬ direction is arranged thermally separated from the Kältemittelabführvorrichtung or Kältemittelabführvorrichtungen.

By such a construction it is achieved that no excessive heat transfer of abzuführendem, compressed refrigerant, which has been heated by a preceding compression process, takes place on the one section of the feeder durchströ ^¬ ing refrigerant. In other words, by such a construction, the heat transfer from a compressed and heated by the compression process refrigerant to an uncompressed refrigerant as much as possible prevented. The better the respective portions of the refrigerant supply device (s) are thermally isolated from those of the corresponding refrigerant discharge device (s), the lower the heat transfer. Ideally, not only sections, but in each case the entire devices, ie the devices are completely thermally separated from each other over their entire extent, resulting in a minimal heat transfer. However, it should be noted at this point that individual points of contact or contact areas (heat transfer surfaces) of the respective devices are structurally almost unavoidable, but the amounts of heat transferred thereto are relatively small and can thus be tolerated. With regard to the size of the contact areas (heat transfer surfaces), the respective most economical concept, which takes into account both the production costs and the operating costs, can be selected in individual cases. It should also be mentioned at this point that, for example, also by the smallest possible configuration of the surfaces of the refrigerant discharge device a minimum heat exchange with the environment of the Kältemittelabführvorrich- (s) can be achieved.

Preferably, in compressors having a plurality of refrigerant supply devices, such as multi-stage compressors, at least portions of all refrigerant supply devices for supplying refrigerant to the compression device are one, more, or preferably all of the existing refrigerant discharge devices (e.g., an intermediate pressure or high pressure discharge device) or compression end pressure standing refrigerant) thermally separated. Thereby the heat transfer for all refrigerant supply devices, i. for example, reduced for the supply of all stages of the compressor.

In a further preferred embodiment, in compressors having a plurality of refrigerant supply devices, that is, for example, in multi-stage compressors, at least two or more of the refrigerant supply devices are thermally separated from each other at least over portions thereof. In particular, when the refrigerant to be supplied to a compression stage is provided for cooling, for example, a drive device of the compressor, thermal decoupling from the other or the other refrigerant supply devices is often desired. Generally, it should be noted that such a construction should always be considered when the respective refrigerant supply devices carry refrigerants of different temperatures.

In a further preferred embodiment, in compressors which have a plurality of refrigerant discharge devices, that is to say for example in the case of multistage compressors, at least two or more of the refrigerant discharge devices are thermally separated from each other at least over portions of the same. This is advantageous, for example, if the respective refrigerant discharge devices carry refrigerants with different temperatures. It is conceivable for this case, for example, a two-stage compressor, in which the refrigerant at the output of a compression stage may optionally have a temperature that of the one at the output of the other

Compaction level (s) is different. A heat transfer to the colder refrigerant, which is discharged from the first compression stage, can thus be prevented. This contributes to increasing the efficiency of the system. In summary, it can be stated that a compressor according to the invention, in which at least portions of one or more refrigerant supply devices are thermally isolated or decoupled from one or more of the one or more refrigerant discharge devices present in the compressor, enables an increase in the efficiency of the compressor. By an optional further (additional) thermal separation between the refrigerant supply devices with each other and with respect to the Kältemittelabführvorrichtungen, and the Kältemittelabführvorrichtungen with each other can on respective compressor designs, especially in the case of prevailing in the individual devices temperature differences another

Improvement of the efficiency can be achieved.

At this point, the definition of the wording "thermally separated", as used in the present application, explained in more detail. Thermally separated in the sense of the present application means thermally not or thermally relatively weakly coupled, i. provided with the lowest possible heat transfer. This can be achieved for example by spacing appropriate components and / or training as separate components. An alternative is also to separate the individual sections by an insulating material from each other. This is applicable even if a plurality of the refrigerant supply devices and the refrigerant discharge devices are to be formed as an integral component. It is conceivable that the entire component of a material with a low thermal conductivity, preferably lower than the thermal conductivity of C-45 steel, further preferably less than a thermal conductivity of 20 W / mK, in particular preferably less than a thermal conductivity of 10 W. / mK manufacture. Even wall thicknesses of a few mm are effective. Alternatively, it would also be conceivable to use two-component structures with, for example, insulating layers, in which case the components are in turn spaced apart from one another by the insulating layer. Possibilities for minimizing the heat transfer are therefore an avoidance of contact surfaces, a minimization of existing or required surfaces, the choice of a little conductive material for required surfaces, in particular contact surfaces, and the thermal insulation of surfaces, in particular contact surfaces by appropriate materials or materials (solid state insulation , Gas insulation, insulation if necessary

Liquid) and / or by a corresponding spacing to each other. Although in the following figure description of an inventive compressor is explained using the example of a multi-stage radial piston compressor, the construction according to the invention to any single-stage and multi-stage compressor is inde pendent ^¬ applicable by the compression principle. In addition to radial piston compressors, axial piston compressors, scroll compressors, screw compressors, turbocompressors, rotary compressors, etc. are examples.

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:

Fig. 1 shows a first possible embodiment of a compressor according to the invention;

FIG. 2 shows a schematic illustration of a refrigeration system which has a compressor according to the first possible embodiment, as well as a valid enthalpy pressure diagram for this purpose; FIG. and

Fig. 3 is a schematic representation of a refrigeration system, which has a compressor according to a second possible embodiment of the invention, as well as a valid enthalpy pressure diagram for this purpose;

4 shows a further schematic representation of a (third) refrigeration system, which represents a modified refrigeration system of FIG. 2, as well as a valid enthalpy pressure diagram for this purpose;

Fig. 5 is a schematic representation of a (fourth) refrigeration system, which in turn is a modification of the refrigeration system of FIG. 2, as well as a valid enthalpy pressure diagram;

6 is a schematic representation of a (fifth) refrigeration system, which in turn is a modification of the refrigeration system according to FIG. 2, and a valid enthalpy pressure diagram for this purpose; 7 shows a sixth refrigeration system in a schematic representation, which represents a modification of the system according to FIG. 3, and a valid enthalpy pressure diagram for this purpose; and

Fig. 8 is a view of an engine of the compressor according to the first embodiment, taken perpendicular to the axial direction; and

9 shows a further sectional view of the compressor according to FIG. 8, cut parallel to the axial direction;

In the illustrated in Fig. 1 the first embodiment of an inventive

Compressor is a radial piston compressor 10, which a

Drive device or drive unit in the form of an electric motor 12, and a compression device or compression unit 14 has. Both the electric motor and the compression unit 14 are arranged in a compressor housing 15, which is composed of two parts, namely a motor housing 15-1 and a pressure cover 15-2. The motor housing 15-1 is gas-tightly connected to the pressure lid 15-2. It is therefore a compressor of a hermetic type, in short, a hermetic compressor. In the present embodiment, the two housing components are welded together, although other thermal

Connection methods, such as brazing, etc., or other suitable gas-tight connection methods, such as flanging, gluing, etc. are conceivable.

The compression unit 14 has, in the embodiment described here, six pistons 18 which extend away from a central axis 16 in the radial direction and which are arranged to slide back and forth in the corresponding cylinders or cylinder bores 19 in the radial direction. The drive of the compression unit 14 via a rotatably connected to the electric motor 12 drive shaft 16, which is in operative engagement with the piston 18 via an eccentric mechanism and connecting rod. In alternative embodiments, each of six different number of pistons is conceivable. The number of pistons is determined based on the desired specifications and the desired application. The operation of the compression process itself is possible both for the radial piston compressor described here and for all other possible Compressor types well known and will not be described further here.

The compressor 10 is a two-stage compressor whose

Compression unit 14 is designed to compress refrigerant in two stages. For this purpose, the compressor 10 via a low-pressure Kältemittelzuführvorrichtung 20, the one

Low-pressure volume of the compressor 10 (suction volume) limited supplied refrigerant for a first compression stage 14-1 and in this to a predetermined

Compressed intermediate pressure. It should be noted at this point that the compressor according to the invention alternatively, of course, as a single-stage compressor and as another type of compressor (scroll compressor, etc., in single-stage and multi-stage

Execution) can be designed. In the described embodiment, a reciprocating compressor is used because of this, inter alia, because of its high

Tightness through the use of cylinders (good sealing over the

Piston rings) is conditional, can be used advantageously. Furthermore, the areas around the cylinders, i. for example, z. heavily loaded areas even in the

Compression moment, i. when the cylinder is filled with refrigerant, and the piston is approaching top dead center, thermally loaded (by the heating caused by the compression of the refrigerant). Thereafter, a cooling takes place immediately, for example by inflowing refrigerant, so that the material load is kept as low as possible.

The low-pressure refrigerant supply device 20 has a plurality of portions. This is a first defined by a tubular wall or by a pipe and defined Niederdruck Kältemittelzufhvorungsungsteilbereich 20-1, which extends outside of the compressor housing 15 from the compressor housing 15 to a low pressure port 22, in turn through a tubular wall or formed by a pipe and defined second low-pressure refrigerant supply device portion 20-2, which within the

Compressor housing 15 extends from the compressor housing 15 to the compression unit 14 and a third, formed in the compression unit 14 low-pressure refrigerant supply device portion 20-3. The subareas are in the

described embodiment, each formed by separate components, which are gas-tightly connected at the ends in each case with a corresponding end of one of the other components. It should be noted at this point that the entire low-pressure Refrigerant supply device 20 may alternatively be integrally formed or may have one of three different number of components. The extent of the above-mentioned subregions need not coincide with the extension of the components.

After being supplied to the first compression stage 14-1, which is formed by four of the six cylinders, the refrigerant in the first compression stage is compressed to an intermediate pressure. After compression by the first compression stage 14-1, the refrigerant is discharged into an intermediate-pressure refrigerant discharge device 24, which in turn has three portions: a first intermediate-pressure refrigerant discharge device portion 24-1 which in turn is defined by a tubular wall outside the compressor housing 15 from

Compressor housing 15 extends to a first intermediate pressure port 26; another bounded by a tubular wall or a pipe second

Intermediate pressure refrigerant purge section 24-2, which extends within the compressor housing 15 from the compressor housing 15 to the compression unit 14, and a third intermediate pressure refrigerant discharge device portion 24- 3, which is formed in the compression unit 14 and the connection of the second intermediate pressure -Kältemittelabführvorrichtungs portion 24-2 with the cylinders, more specifically, the outputs of the cylinder of the first compression stage 14-1 is used. The

Intermediate pressure Kältemittelabführvorrichtungs portions are in turn analogous to the low pressure portions at respective ends together and at corresponding other ends to the first intermediate pressure port 26 and the cylinders of the first compression stage 14-1 connected in a gastight manner. Also with regard to the number of components, the statements for the low-pressure supply device 20 apply analogously.

The intermediate pressure refrigerant discharge device 24 discharges the intermediate pressure refrigerant from the compressor and provides it to the first intermediate pressure port 26 for transfer to an intercooler 28 (see FIG. In an exemplary refrigeration system, which is shown in Fig. 2 and which includes a compressor 10 of FIG. 1 comprises the compressor 10 is pressure port via the first intermediate 26 by means of a first conduit 30 to the intercooler verbun ^¬ in which the on Intermediate pressure located refrigerant is cooled. Via a further, second pipe 32, the cooled, intermediate pressure refrigerant is then via a second intermediate pressure associated with the second pipe 32 connected terminal 34 in an intermediate-pressure refrigerant supply device 36 of the compressor 10.

The intermediate-pressure refrigerant supply device 36 comprises, in the described embodiment, two gas-tightly interconnected portions: a first in turn tubular intermediate pressure refrigerant supply portion 36-1 which is interposed between and connected to the compressor housing 15 and the second intermediate pressure port 34, and a tubular second intermediate pressure refrigerant supply device portion 36-2, which extends from the compressor housing 15 in a 90 ° arc curved toward the electric motor 12 and ends in the region of the electric motor 12. This is in the described possible embodiment for a cooling of the electric motor 12 by the on

Intermediate pressure cooled refrigerants provided. Via a, arranged in the compression unit 14 third intermediate-pressure refrigerant supply device portion 36-3, the intermediate pressure, cooled refrigerant after flowing and cooling of the engine then a second compression stage 14-2 consisting of two cylinders supplied, in which this high pressure (high pressure) is compressed. The cylinders of the second compression stage 14-2 are gas-tightly connected to the third intermediate-pressure refrigerant supply portion 36-3 on an inlet side. Also, the intermediate-pressure refrigerant supply device 36 may be composed of any number of components that need not coincide with the respective portions.

After compression to high pressure, the refrigerant is then removed from the cylinders

(Outlets) of the second compression stage 14-2 ejected into a high-pressure refrigerant discharge device 38. The high-pressure refrigerant discharge device 38 has five high-pressure refrigerant discharge device portions respectively gas-tightly connected to each other: a high-pressure first tubular high-pressure refrigerant discharge portion 38-1 extending from the compressor casing 15 to a high-pressure port 40 outside the compressor casing 15; a second tubular high pressure refrigerant discharge device section 38-2, also formed in a tubular shape, which extends within the compressor housing 15 from the compressor housing 15 to a third high pressure refrigerant discharge device section 38-3; the third high-pressure refrigerant discharge device subregion 38-3, which is approximately cuboid-shaped, that is, formed with a rectangular cross section and the pulsation damping in the high pressure volume 38 is used; a fourth high pressure refrigerant purge section 38-4 extending from the third high pressure refrigerant purge section 38-3 toward the compression unit 14; and a fifth high pressure refrigerant discharge section 38-5 formed in the compression unit 14, which is connected to cylinder outputs of the second compression stage 14-2 and serves to discharge refrigerant to high pressure and discharge pressure, respectively. Again, any number of components can be used, the number of subregions does not have to match that of the components and the subregions boundaries do not have to coincide with component boundaries, as is true for the rest of the other supply and discharge devices.

From the high pressure port 40, the refrigerant in the exemplary refrigeration system of Fig. 2 is supplied via a third pipe 42 to a gas cooler 43, in which it is cooled. Thereafter, the high-pressure, cooled refrigerant flows via a fourth pipe 44 into a first expansion member 46, where it is at a medium pressure, which does not have to correspond to the intermediate pressure, is relaxed. Via a fifth pipeline 48, the refrigerant then flows into a collector 50, from where it via a sixth pipe 52 into a second expansion element 54, in which it is depressurized to low pressure (suction pressure), and then via a seventh pipe 56 to an evaporator 58 arrives. From the evaporator 58, the refrigerant then flows via a further, eighth pipe 60 to the compressor 10, more precisely to the low pressure port 22 of the compressor 10th

For the compression of refrigerants and in particular for the compression of natural refrigerants, such as e.g. C02, which is used in the embodiment described here as a refrigerant, it is important that the (gaseous) refrigerant is not unnecessarily heated before entering the respective compression stage. Since the permissible compression end temperature is limited, each heating before the actual compression means a limitation of the achievable compression ratio and an increase in the workload per mass of compressed refrigerant.

Therefore, a portion of each refrigerant supply device 20, 36 is thermally separated from the refrigerant discharge devices. It is in the present Embodiment here by portions which start at respective terminals for the refrigerant (low pressure port 22, second intermediate pressure port 34) and in the case of the low-pressure refrigerant supply device, the first low-pressure refrigerant supply device portion 20-1 and the second low-pressure refrigerant supply device portion 20-2. In the case of the intermediate-pressure refrigerant supply device 36, the first and second intermediate-pressure refrigerant supply device portions 36-1 and 36-2 are included.

In addition, the intermediate-pressure refrigerant discharge device 24 and the high-pressure refrigerant discharge device 38 are thermally separated from each other. In the intermediate-pressure refrigerant discharge device 24, the corresponding portion includes the first and second intermediate-pressure refrigerant discharge device portions 24-1 and 24-2, and in the high-pressure refrigerant discharge device 38, the first to fourth high-pressure refrigerant discharge device portions 38-1 to 38-4 ,

The respective portions, which are thermally separated from each other, are spaced apart and thermally isolated from each other by the respective ambient atmosphere (in the compressor refrigerant, either at intermediate pressure or under suction pressure, outside the compressor, ambient atmosphere).

Further, a corresponding pressure-enthalpy diagram for the refrigeration system is shown in Fig. 2, wherein the states indicated in the pressure-enthalpy diagram with single-digit numbers occur at the places in the plant in circles einiffrig designated locations. The states in the respective pressure-enthalpy diagrams of FIGS. 3 to 7 are indicated analogously. In the following, reference will no longer be made individually, but as already explained, provided that the respective pressure-enthalpy diagrams illustrated in FIGS. 3 to 7 represent the states in the respective refrigeration systems shown in the same figure. The states indicated by a number are respectively present at the location of the refrigeration system provided with a number in a circle.

In Fig. 3, another exemplary refrigeration system is shown, which has a second possible embodiment of a compressor according to the invention. The compressor 110 is in turn designed in two stages, and corresponds essentially to the compressor 10 of first described embodiment of FIG. L. Above all, the differences to the compressor 10 according to FIG. 1 are described at this point. The compressor 110 has two compression stages 114-1 and 114-2.

Notwithstanding the first possible embodiment, the first compression stage 114-1 compresses a low pressure (suction pressure) mainstream coolant provided to the compressor 110 via a low pressure port 122 and a low pressure volume that is similar in construction and function to that of the first embodiment will, on high pressure. Parallel to this, the second compression stage 114-2 is arranged, which also compresses intermediate pressure refrigerant of a secondary coolant flow to high pressure. The intermediate pressure refrigerant is supplied to the compressor 110 via an intermediate pressure port 134 corresponding to the second intermediate pressure port 34 of the first embodiment and an intermediate pressure volume connected thereto which is similar in construction and function to the second intermediate pressure volume of the first embodiment. Here, too, located at intermediate pressure refrigerant is used to cool the electric motor of the compressor.

In contrast to the compressor 10 of the first embodiment, in the compressor 110, the cylinders (cylinder outlets) of both compression stages 114-1 and 114-2 are connected to a common high pressure partial volume 138-5 which is the fifth high pressure partial volume 38-5 of the first embodiment is connected to the cylinders (cylinder outlets) of the second compression stage 14-2 replaced; The remaining partial volumes of the high-pressure volume of the second embodiment are analogous to those of the first embodiment; Also, a corresponding to the first embodiment, high-pressure port 140 is provided.

In the compressor 110 of the second embodiment, this eliminates the first intermediate pressure volume 24, via which the refrigerant compressed in the first compression stage 14-1 of the compressor according to the first embodiment has been supplied to the intercooler without replacement.

From the high-pressure connection 140, the refrigerant flows (again in each case via pipelines) to a gas cooler 143 which, in terms of construction and functionality, flows to the gas cooler 43. speaks and is cooled down there. Thereafter, the refrigerant flow is divided into the main flow H and the bypass flow N, wherein the bypass flow passes through a first expansion element 146-1, where it is expanded to the intermediate pressure of the compressor. Thereafter, the secondary flow N is fed to a heat exchanger 162. The main ^flow H through ^¬ initially runs no expansion element but is fed directly to the heat exchanger 162, so that the main flow H is further cooled by the secondary flow N.

The secondary flow is then directed to the second compression stage 114-2, more specifically to the intermediate pressure port 134, while the main flow H passes through an expansion means 146-2 which relaxes the main flow refrigerant or main flow to a mean pressure different from the intermediate pressure can. After passing through a collector 150, which corresponds in structure and function to the collector 50 of the first embodiment and a further expansion element 154, which corresponds in construction and function to the expansion element 54 of the first embodiment, the refrigerant of the main stream H then passes through the evaporator 158 back to

Low pressure port of the compressor 110th

It should be noted at this point that in both described embodiments of a compressor according to the invention, the rotor of the electric motor 12 acts as an oil separator. In the described embodiments, the compressor housing 15 consists of two parts, which are not thermally connected to each other after the introduction of the drive device and the compression unit. This leads to a high stability of the compressor, since a loosening of connections, for example due to vibrations is unlikely. Alternatively, more than two parts can serve for the formation of the housing 15, which, if appropriate, in spite of a higher number of parts and slightly higher manufacturing costs increase the ease of installation and thus can provide cost savings elsewhere.

A third refrigeration system based on the compressor 10, which is a modification of the refrigeration system shown in FIG. 2, is shown in FIG. In addition to the components present in FIG. 2, the third refrigeration system has a connecting line in the form of a pipeline 64 between the collector 50 and the pipeline 32, which is arranged between the intercooler 28 and the second intermediate pressure connection 34. As a result, a refrigerant side stream from the collector 50 to the second Compression level 14-2 allows.

Another on the compressor 10 based (fourth) refrigeration system is shown in Fig. 5. In this embodiment, the intercooler 28 4 deleted together with the supplied arrange ^¬ th him pipelines, but otherwise the fourth refrigeration system is identical to the third refrigeration system of FIG..

A fifth, shown in Fig. 6 refrigeration system is in turn based on the refrigeration system of Figure 2 (two-stage compressor with serially arranged compression stages), the refrigerant flow, however, after the gas cooler 43 (analogous to the refrigeration system, which is shown in Fig. 3) in a Split main flow H and a secondary flow N, wherein the secondary flow passes through a first expansion element 46-1, where it is expanded to the intermediate pressure of the compressor. Thereafter, the secondary flow N is fed to a heat exchanger 62. The main flow H initially passes through no expansion element but is fed directly to the heat exchanger 62, so that the main flow H is further cooled by the secondary flow N.

The secondary flow is then led to the second compression stage 14-2, more precisely to the intermediate pressure port 34, while the main flow H passes through an internal heat exchanger 66 and then an expansion element 54, then the refrigerant of the main flow H passes through the evaporator 58, another collector 68 and the internal heat exchanger 66 back to the low pressure port of the compressor 10th

Finally, FIG. 7 again shows a further (sixth) refrigeration plant which has a compressor 110 (ie a compressor with parallel compression stages 114-1 and 114-2). In contrast to the refrigeration plant according to FIG. 3, however, the sixth refrigeration plant has no heat exchanger which transfers heat from a cooling medium main stream to a secondary refrigerant stream. The total refrigerant flow, similar to the refrigeration system of FIG. 5, passes through an expansion device 146 and thereafter passes into a collector 150. From the collector 150, a connection in the form of a pipeline 164 extends to the inlet of the compression stage 114-2, whereby a secondary flow N is fed to the compression stage 114-2, whereas a main flow H is supplied to the expansion device 154 and via the subsequently arranged evaporator 58 of the first compression stage 114-1. As already indicated above, in the described first embodiment of a compressor 10 is a compressor 10 with an eccentric mechanism. As a result, let's take a closer look at the corresponding engine, although this is exemplary for a compressor according to the invention, which by no means must be a reciprocating compressor, but may also be a scroll compressor, a screw compressor or any other known type of compressor. In particular, however, for cases in which radial piston compressors due to technical requirements or due to customer wishes and the like. To be used or must, the engine described below is an advantageous variant.

As can be seen in FIGS. 8 and 9, the compressor 10 (which can also be used as the compressor 110) has six pistons 18 which can be reciprocated in a radial direction in corresponding cylinder bores or

Cylinder liners 216 are arranged. The cylinder bores or cylinder liners 216 themselves are designed as corresponding recesses in a cylinder block 218. As already mentioned above, the pistons 18 are designed to be reciprocable in the radial direction. In this reciprocating motion, a disengagement movement and an engagement movement are distinguished as a result, wherein the disengagement movement in the radially outward direction (indicated by arrow 220) and the

Engagement movement in a radially inward direction (indicated by arrow 222) is directed. The compressor 10 is, as already indicated above, for compressing R744 (C0 ₂ ) as a refrigerant. It should be noted, however, that it is also conceivable to use any other refrigerant (for example R134a, etc.).

Furthermore, the compressor 10 has the drive device in the form of the drive shaft 16 (see for example Fig. 9), by means of which the drive of the compressor 10 takes place. The

Drive shaft 16 is coupled to the electric motor 12 in the described embodiment, but in alternative embodiments may also be coupled to a corresponding belt drive device or other device. At this point it should be noted that the axial extent of the drive shaft 16 depending on

provided use can also be significantly shorter than in the embodiment shown in the figures, in which the drive shaft 24 is in operative engagement with the electric motor and extending therethrough. In the context of the extraction and engagement movements of the piston refrigerant is sucked in an engagement movement of the piston 18 into the cylinder bores or cylinder liners 216, compressed in carrying out the disengagement movement and then

pushed out.

The drive device in the form of the drive shaft 16 is in operative engagement with an eccentric 228. More specifically, the drive shaft 16 is formed eccentrically in a corresponding area (eccentric portion of the drive shaft 16). The eccentric 228 is integral therewith and integrally formed with and on the drive shaft 16. In alternative embodiments, the eccentric 228 may also be formed as a separate component and attached to the drive shaft 16, in particular articulated or stored accordingly.

The eccentric 228 has, cut perpendicular to the axial direction, a

circular cross-section and radially outwardly directed eccentric surfaces 230, which are arranged in a region of an eccentric Wirkeabschnitts 232. The eccentric action section 232 serves to drive the pistons 18 and is in operative engagement therewith via a connecting rod 234 assigned to each piston 18. For this purpose, the connecting rods 234 by means of connecting rods 236, which are formed on the piston 18 facing sides of the connecting rod 234, hinged to the piston 18.

On the side facing the eccentric 228, the connecting rods 234 have a connecting rod active section 238, which serves for the operative engagement with the eccentric 228. The eccentric 228 is connected to the connecting rod operative portions 238 via a bearing in the form of a needle bearing 240 in operative engagement, which on the eccentric working portion 232 (circular cross section) and there on the eccentric surface 230 is arranged (fitted). Alternative to

Needle bearing 240 are other bearings, especially plain bearings or bearings conceivable in any possible training.

The bearing 240 provides a low-friction carryover and conversion of the

Movement (rotational movement) of the eccentric 228 in a radially directed movement of a connecting rod active portion receiving 242, which is in operative engagement with the bearing by means of a corresponding fit. The corresponding movement in the radial direction is then correspondingly to the connecting rod 234 and the piston 18 articulated thereon transfer. The corresponding to the circular outer periphery of the bearing 240 conrod-effective portions 238, which are formed on its side facing the bearing 240 circular segment-like, for this purpose at its end facing the bearing on a widened in the axial direction expansion, so that they by means of two, in Cross-section L-shaped shells 244, which form the connecting rod active portion receiving 242, are securely arranged on the bearing 240. The connecting rod active portions of all connecting rods 234 are arranged on a circular path around the eccentric 228 and thus also about the eccentric working portion 232, which is concentric with the same.

Due to the fact that the pendulum point of the device is arranged azentrisch due to the use of the eccentric 228, can be used by the present construction, in the circular segment-like connecting rod Wirkabschnitte238 are used and the connecting rods 234 are thus decoupled in their movement, in the region of the respective Kolbenl8 a different movement takes place. If the connecting rods 18 were rigidly coupled, then there would be an error in the lifting movement and thus an increased dead space in the area of the pistons 18, which are far away from the pendulum point.

It may be noted that the compressor 10 as well as the compressor 110 have, inter alia, the following design features, in particular in addition to at least one section of a refrigerant supply device or at least one section of at least one, in particular each refrigerant supply device being thermally separated from a refrigerant discharge device or at least one in particular, each of a plurality of refrigerant discharge devices is arranged, comprising:

1. compressor for compressing refrigerant with a drive device, in particular

Drive shaft, for driving one or more in a radial direction

arranged and in corresponding cylinder bores in off and

Engaging reciprocating piston reciprocating movements whereby the driving device is operatively engaged with an eccentric which controls the disengagement movement of the pistons, the eccentric also controlling the engagement movement of the pistons.

2. compressor, as described in 1., wherein the eccentric an eccentric working section

over which it is in operative engagement with one or more connecting rods, in particular connecting rod active sections of the respective connecting rod. 3. Compressor, as described in 2., wherein the compressor for each piston has a respective associated connecting rod, which is articulated by means of a connecting rod, which is formed on a side facing the respective piston of the connecting rod.

4. Compressor as described in 2. or 3., with the compressor for each piston

each associated with this connecting rod, which is by means of the connecting rod active portion, which is formed on a side facing the eccentric active portion of the connecting rod, with the eccentric is in operative engagement.

5. Compressor, as described in 2., 3. or 4., wherein the eccentric effective portion has a circular cross section and / or that the eccentric active portion facing sides of the connecting rod, in particular the connecting rod-effective portion are formed like a circle segment.

6. compressor, as described in 2., 3., 4. or 5., wherein the connecting rod-effective portions are arranged on a circular path around the eccentric, in particular about the eccentric active portion concentric to this.

7. compressor, as described under 6., wherein between the connecting rod-effective portion and the eccentric-effective portion of a bearing, in particular a needle bearing is arranged.

8. A compressor as described above, wherein the compressor is a hermetic compressor.

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 or individually in combination with respect to the prior art.

LIST OF REFERENCE NUMBERS , 110 compressors

Elektomotor

compacting device

-1, 114-1 first compression stage

-2, 114-2 second compression stage

drive shaft

piston

cylinder

Low pressure Kältemittelzuführvorrichtung

Low pressure connection

Intermediate pressure refrigerant discharge device first intermediate pressure port

intercooler

, 32 pipeline

second intermediate pressure port

Intermediate pressure Kältemittelzuführvorrichtung

High pressure refrigerant discharge device, 140 high pressure connection

pipeline

, 143 gas cooler

pipeline

, 146 expansion organ

pipeline

, 150 collectors

pipeline

, 154 expansion organ

pipeline

, 158 evaporator

pipeline

, 162 heat exchangers

pipeline

internal heat exchanger

collector

6 cylinder bores / cylinder liners 218 cylinder block

220 arrow

222 arrow

228 eccentric

230 eccentric surface

232 eccentric action section

234 connecting rods

236 connecting rod eye

238 connecting rod working section

240 (needle) bearings

242 Connecting Rod Acting Section Recording

244 shell

Claims

claims

A compressor (10, 110), comprising a compressor housing (15), a drive device (12) and a compression device (14) with one or more compression stages (14-1, 14-2) for compressing a refrigerant, wherein the compressor ( 10, 110) further comprises one or more refrigerant supply devices (20, 36) for supplying refrigerant to the compression device (14) and one or more refrigerant discharge devices (24, 38) for discharging refrigerant from the compression device (14),

characterized in that

at least a portion of the one refrigerant supply device or at least a portion of at least one, in particular, each of the plurality of refrigerant supply devices (20, 36) is thermally separated from the one or more refrigerant discharge devices.

2. compressor (10, 110) according to claim 1,

characterized in that

the compressor has more than one refrigerant supply device,

- Is formed in particular multi-stage, and

- At least a portion of each refrigerant supply device (20, 36) thermally separated from the or the Kältemittelabführvorrichtungen (24, 38) is arranged.

3. compressor (10, 110) according to any one of the preceding claims,

characterized in that

1 the compressor has more than one refrigerant supply device,

- Is formed in particular multi-stage, and

- At least a portion of each refrigerant supply device (20, 36) is thermally separated from any other existing refrigerant supply device (20, 36) is arranged.

4. compressor (10, 110) according to any one of the preceding claims,

characterized in that

the compressor has more than one refrigerant discharge device,

- Is formed in particular multi-stage, and

- At least a portion of each Kältemittelabführvorrichtung (24, 38) thermally separated from any other existing Kältemittelabführvorrichtung (24, 38) is arranged.

5. compressor (10, 110) according to any one of the preceding claims,

characterized in that

the portion (s) thermally separated from, or separate from, other refrigerant supply means (20, 36) or refrigerant discharge means (24, 38) or separate from portions thereof, and / or with or without Minimized contact surface to each other and / or spaced therefrom and / or separated from them by a thermally insulating or thermally low-conductivity material.

6. compressor (10, 110) according to any one of the preceding claims,

characterized in that

one of a plurality of the portions thermally separated from other refrigerant feeder (s) or refrigerant discharge means (24, 38) extends from the inside of the compressor housing (15) to the compression device (14).

7. compressor (10, 110) according to any one of the preceding claims,

characterized in that

a refrigerant supply device (20, 36) in the compressor housing, in particular in the region of or adjacent to the drive device (12) opens.

8. compressor (10, 110) according to claim 7,

2 characterized in that

the refrigerant supply device opening in the compressor housing (15) is a refrigerant supply device (20, 36) for low-pressure refrigerant or intermediate-pressure refrigerant.

9. compressor (10, 110) according to one of the preceding claims,

characterized in that

at least one Kältemittelabführvorrichtung (24, 38), in particular a Kältemittelabführvorrichtung for located at an intermediate pressure refrigerant (24), for connection to an input of a refrigerant intercooler (28) of a refrigeration system is provided or with an input of a refrigerant intercooler of the compressor (10 , 110) in

Fluid communication is.

10. compressor (10, 110) according to any one of claims 7 to 9,

characterized in that

the refrigerant supply device (36), which opens in the compressor housing (15), is provided for connection to an outlet of a refrigerant intercooler (28) of a refrigeration system or is in fluid communication with an output of a refrigerant intercooler of the compressor (10, 110).

11. Compressor (10, 110) according to one of the preceding claims,

characterized in that

the drive device comprises an electric motor (12) with a rotor and a stator, wherein the rotor serves as an oil separator for him supplied refrigerant.

12. compressor (10, 110) according to one of the preceding claims,

characterized in that

the compressor (10, 110) is formed in two stages and a refrigerant supply device (20) for low pressure refrigerant and a refrigerant supply device (36) for intermediate pressure refrigerant, and a refrigerant discharge device (24) for intermediate pressure refrigerant and a refrigerant discharge device (38 ) for at high pressure refrigerant, wherein in each case at least sections, in particular within the compressor (10, 110) arranged portions, each

Refrigerant supply device (20, 36) and each refrigerant discharge device (24, 38)

3 spaced apart from each other.

13. Compressor according to one of the preceding claims,

characterized in that

the compressor (10, 110) is provided for R744 as a refrigerant.

14. compressor (10, 110) according to any one of the preceding claims,

characterized in that

the compressor (10, 110) has at least two housing components (15-1, 15-2) which are connected to one another in a gas-tight and non-removable manner and / or the compressor (10, 110) is designed in hermetic or semi-hermetic design.

15. refrigeration system,

characterized in that

it comprises a compressor (10, 110) according to one of the preceding claims.

16. Refrigeration system according to claim 15,

characterized in that

it has an intercooler (28) for cooling refrigerant provided from a refrigerant discharge device (24, 38) of the compressor (10, 110).

4