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EP2795204B1 - Compresseur - Google Patents

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Publication number
EP2795204B1
EP2795204B1 EP12824900.0A EP12824900A EP2795204B1 EP 2795204 B1 EP2795204 B1 EP 2795204B1 EP 12824900 A EP12824900 A EP 12824900A EP 2795204 B1 EP2795204 B1 EP 2795204B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
compressor
pressure
discharge device
refrigerant discharge
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP12824900.0A
Other languages
German (de)
English (en)
Other versions
EP2795204A2 (fr
Inventor
Arno Görlich
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bock GmbH
Original Assignee
GEA Bock GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE201110122248 external-priority patent/DE102011122248A1/de
Priority claimed from DE102012005297A external-priority patent/DE102012005297A1/de
Application filed by GEA Bock GmbH filed Critical GEA Bock GmbH
Publication of EP2795204A2 publication Critical patent/EP2795204A2/fr
Application granted granted Critical
Publication of EP2795204B1 publication Critical patent/EP2795204B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B25/00—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/072—Intercoolers therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/11—Reducing heat transfers

Definitions

  • the invention relates to a compressor according to the preamble of claim 1 and 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.
  • the drive device is often an electric motor, for example.
  • the compression device is designed in one or more stages, which means that the compressor, for example, in a first stage compresses refrigerant from a low pressure (suction pressure) to an intermediate pressure, the refrigerant at intermediate pressure then being fed to a second stage in which it is applied to a High pressure (final pressure) is compressed.
  • Such or similar compressors are for example from the JP 2002 106 989 A , of the U.S. 3,913,346 A , of the WO 2011/049 767 A2 , of the EP 1 562 012 A1 , of the US 2011/203304 A1 , as well as the DE 10 2005 009 173 A1 known.
  • 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 also has at least one refrigerant supply device for supplying refrigerant to the compression device and at least one refrigerant discharge device for discharging refrigerant from the compression device, at least one section of the refrigerant supply device being arranged thermally separated from the refrigerant discharge device or the refrigerant discharge devices.
  • Such a construction ensures that there is no excessive heat transfer from the compressed refrigerant to be discharged, which has been heated by a preceding compression process, to the refrigerant flowing through a section of the supply device.
  • such a construction largely prevents the heat transfer from a compressed refrigerant, which is heated by the compression process, to an uncompressed refrigerant.
  • the entire devices ie the devices over their entire extent, are completely thermally separated from one another, which leads to a minimal heat transfer.
  • compressors that have several refrigerant supply devices, i.e. for example multi-stage compressors
  • at least sections of all refrigerant supply devices for supplying refrigerant to the compression device from one, several or preferably all of the existing refrigerant discharge devices (for example device for discharging under an intermediate pressure or under high pressure) are preferred or final compression pressure standing refrigerant) arranged thermally separated. This reduces the heat transfer for all refrigerant supply devices, i.e. for example for the supplies to all stages of the compressor.
  • compressors that have a plurality of refrigerant supply devices, that is to say for example in the case of multi-stage compressors, at least two or more of the refrigerant supply devices are each thermally separated from one another at least over sections of the same.
  • 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.
  • thermal decoupling from the other or the other refrigerant supply devices is often desired.
  • such a construction should always be considered when the corresponding refrigerant supply devices carry refrigerants of different temperatures.
  • compressors that have several refrigerant discharge devices, that is to say for example in the case of multi-stage compressors, at least two or more of the refrigerant discharge devices are thermally separated from one another at least over sections of the same.
  • the respective refrigerant discharge devices carry refrigerants at different temperatures.
  • a two-stage compressor is conceivable for this case, in which the refrigerant at the outlet of one compression stage can possibly have a temperature that is different from that at the outlet of the other compression stage (s).
  • a transfer of heat 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.
  • a compressor according to the invention in which at least sections of one or more refrigerant supply device (s) are thermally separated or decoupled from one or more of the one or more refrigerant discharge device (s) present in the compressor enables an increase in the efficiency of the compressor.
  • An optional further (additional) thermal separation between the refrigerant supply devices and from the refrigerant discharge devices, as well as the refrigerant discharge devices from one another, can further improve the efficiency of the respective compressor designs, especially in the case of temperature differences in the individual devices.
  • Thermally separated in the context of the present application means thermally not coupled or thermally relatively weakly coupled, ie provided with the lowest possible heat transfer. This can be achieved, for example, by spacing corresponding components and / or designing them as separate components. It is also an alternative to separate the individual sections from one another with an insulating material. This can also be used when several of the supply devices and the discharge devices for refrigerant are to be designed as an integral component.
  • the entire component is made of a material with a low thermal conductivity, preferably lower than the thermal conductivity of C-45 steel, further preferably lower than a thermal conductivity of 20 W / mK, in particular preferably lower than a thermal conductivity of 10 W. / mK to produce. Wall thicknesses of a few mm are effective.
  • two-component structures with, for example, insulating layers, in which case the components are again spaced apart from one another by the insulating layer.
  • Possibilities for minimizing the heat transfer are therefore avoiding contact surfaces, minimizing existing or required surfaces, choosing a less conductive material for required surfaces, in particular contact surfaces, and thermal insulation of surfaces, in particular contact surfaces, using appropriate materials or substances (solid-state insulation , Gas insulation, if necessary insulation by liquid) and / or by a corresponding spacing from one another.
  • a compressor according to the invention is explained in the following description of the figures using the example of a multistage radial piston compressor, the construction according to the invention can be applied to any single-stage and multistage compressor regardless of its compression principle.
  • radial piston compressors axial piston compressors, scroll compressors, screw compressors, turbo compressors, rotary compressors, etc. may be mentioned as examples.
  • the illustrated first embodiment of a compressor according to the invention is a radial piston compressor 10 which has a drive device or drive unit in the form of an electric motor 12 and a compression device or compression unit 14. 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 connected to the pressure cover 15-2 in a gas-tight manner.
  • the two housing components are welded to one another, other thermal connection methods such as brazing etc. or other suitable gas-tight connection methods such as flanging, gluing etc. also being conceivable.
  • the compression unit 14 has six pistons 18 which extend away from a central axis 16 in the radial direction and which are arranged in corresponding cylinders or cylinder bores 19 such that they can be displaced back and forth in the radial direction.
  • the drive of the compression unit 14 takes place via a drive shaft 16 which is connected to the electric motor 12 in a rotationally fixed manner and which is in operative engagement with the piston 18 via an eccentric mechanism and a connecting rod.
  • any number of pistons other than six is conceivable.
  • the number of pistons is determined on the basis of the desired specifications and the desired area of application.
  • the functioning of the compression process itself is possible both for the radial piston compressor described here and for all others Compressor types are well known and will not be further described here.
  • the compressor 10 is a two-stage compressor, the compression unit 14 of which is designed to compress refrigerant in two stages.
  • the compressor 10 is supplied with refrigerant for a first compression stage 14-1 via a low-pressure refrigerant supply device 20 which limits a low-pressure volume of the compressor 10 (suction volume) and is compressed in this to a predetermined intermediate pressure.
  • a low-pressure refrigerant supply device 20 which limits a low-pressure volume of the compressor 10 (suction volume) and is compressed in this to a predetermined intermediate pressure.
  • the compressor according to the invention can of course alternatively also be designed as a single-stage compressor and also as a different type of compressor (scroll compressor, etc., in a single-stage and multi-stage design).
  • a reciprocating piston compressor is used because it can be used advantageously because of, among other things, its high degree of tightness, which is due to the use of cylinders (good sealing via the piston rings). Furthermore, the areas around the cylinder, that is, for example, some heavily loaded areas, are only thermally loaded during the compression moment, i.e. when the cylinder is filled with refrigerant and the piston is approaching top dead center (due to the heating caused by the compression of the refrigerant caused). Afterwards, 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 subregions. This is a first low-pressure refrigerant supply device sub-area 20-1 formed and defined by a tubular wall or a pipe, which extends outside the compressor housing 15 from the compressor housing 15 to a low-pressure connection 22, one in turn through a tubular wall or . By a pipe formed and defined second low-pressure refrigerant supply device sub-area 20-2, which extends within the compressor housing 15 from the compressor housing 15 to the compression unit 14, and a third, formed in the compression unit 14 low-pressure refrigerant supply device sub-area 20-3 on.
  • the subregions are each formed by separate components which are each connected in a gas-tight manner at the ends to 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 can alternatively be formed in one piece or can have one of three different numbers of components. The extent of the above-mentioned sub-areas does not have to coincide with the extent of the components.
  • the refrigerant After being fed to the first compression stage 14-1, which is formed by four of the six cylinders, the refrigerant is compressed to an intermediate pressure in the first compression stage.
  • the refrigerant After compression by the first compression stage 14-1, the refrigerant is ejected into an intermediate-pressure refrigerant discharge device 24, which in turn has three sub-areas: a first intermediate-pressure refrigerant discharge device sub-area 24-1, which is again delimited by a tubular wall or a pipe extends outside the compressor housing 15 from the compressor housing 15 to a first intermediate pressure connection 26; a second intermediate-pressure refrigerant discharge device sub-area 24-2, likewise bounded by a tubular wall or pipe, 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 sub-area 24-3, which is formed in the compression unit 14 and serves to connect the second intermediate-pressure refrigerant discharge device section 24-2 to the cylinders, more precisely, to the outlets of the
  • the intermediate pressure refrigerant discharge device sub-areas are in turn connected in a gastight manner to the first intermediate pressure connection 26 and the cylinders of the first compression stage 14-1 in a gas-tight manner analogous to the low pressure sub-areas at respective ends and at corresponding other ends.
  • the statements for the low-pressure feed device 20 also apply analogously with regard to the number of components.
  • the intermediate pressure refrigerant is led out of the compressor via the intermediate pressure refrigerant discharge device 24 and made available at the first intermediate pressure connection 26 for transfer to an intermediate cooler 28 (see FIG Fig. 2 ).
  • the compressor 10 is connected via the first intermediate pressure connection 26 by means of a first pipe 30 to the intermediate cooler, in which the intermediate pressure refrigerant is cooled.
  • the cooled, intermediate-pressure refrigerant is then supplied via a second intermediate-pressure connection connected to the second pipe 32 34 brought into an intermediate pressure refrigerant supply device 36 of the compressor 10.
  • the intermediate pressure refrigerant supply device 36 has two sub-areas connected to one another in a gas-tight manner: a first intermediate-pressure refrigerant supply device sub-area 36-1, which is again tubular and which is arranged between the compressor housing 15 and the second intermediate pressure connection 34 and is connected to it in a gas-tight manner, a tubular second intermediate-pressure refrigerant supply device sub-area 36-2, which extends from the compressor housing 15 in a 90 ° curve towards the electric motor 12 and ends in the area of the electric motor 12.
  • the electric motor 12 is cooled by the cooled refrigerant at intermediate pressure.
  • a third intermediate-pressure refrigerant supply device sub-area 36-3 arranged in the compression unit 14 After flowing through and cooling the engine, the cooled refrigerant is then supplied to a second compression stage 14-2 consisting of two cylinders, in which it is fed to one high pressure (high pressure) is compressed.
  • the cylinders of the second compression stage 14-2 are connected in a gas-tight manner on an inlet side to the third intermediate-pressure refrigerant supply device section 36-3.
  • the intermediate-pressure refrigerant supply device 36 can also consist of any number of components that do not have to match the corresponding subregions.
  • the high-pressure refrigerant discharge device 38 has five high-pressure refrigerant discharge device subareas, each connected to one another in a gas-tight manner: a first tubular high-pressure refrigerant discharge device subarea 38-1, which extends outside the compressor housing 15 from the compressor housing 15 to a high-pressure connection 40; a likewise tubular second high-pressure refrigerant discharge device sub-area 38-2, which extends within the compressor housing 15 from the compressor housing 15 to a third high-pressure refrigerant discharge device sub-area 38-3; the third high-pressure refrigerant discharge device section 38-3, which is roughly cuboid, that is, is designed with a rectangular cross-section and serves to dampen pulsations in the high-pressure volume 38; a fourth high pressure refrigerant discharge device section 38-4 extending from the third high pressure
  • the refrigerant is in the exemplary refrigeration system of Fig. 2 is fed via a third pipe 42 to a gas cooler 43 in which it is cooled.
  • the cooled refrigerant which is at high pressure, then flows via a fourth pipe 44 into a first expansion element 46, where it is expanded to a mean pressure which does not have to correspond to the intermediate pressure.
  • the refrigerant then flows via a fifth pipe 48 into a collector 50, from where it flows via a sixth pipe 52 into a second expansion element 54, in which it is expanded to low pressure (suction pressure), and then via a seventh pipe 56 to an evaporator 58 arrives.
  • the refrigerant then flows from the evaporator 58 via a further, eighth pipe 60 to the compressor 10, more precisely to the low-pressure connection 22 of the compressor 10.
  • each refrigerant supply device 20, 36 is arranged to be thermally separated from the refrigerant discharge devices. It is in the present Embodiment here to sections which begin at respective connections for the refrigerant (low pressure connection 22, second intermediate pressure connection 34) and in the case of the low pressure refrigerant supply device comprises the first low pressure refrigerant supply device sub-area 20-1 and the second low pressure refrigerant supply device sub-area 20-2 . In the case of the intermediate-pressure refrigerant supply device 36, the first and the second intermediate-pressure refrigerant supply device sub-regions 36-1 and 36-2 are included.
  • intermediate-pressure refrigerant discharge device 24 and the high-pressure refrigerant discharge device 38 are also thermally separated from one another.
  • the corresponding section comprises the first and second intermediate-pressure refrigerant discharge device subareas 24-1 and 24-2, and in the high-pressure refrigerant discharge device 38 the first to fourth high-pressure refrigerant discharge device subareas 38-1 to 38-4 .
  • the respective sections which are arranged thermally separated from one another, are arranged at a distance from one another and thermally separated or decoupled from one another by the respective ambient atmosphere (in the compressor refrigerant, either under intermediate pressure or under suction pressure, outside the compressor ambient atmosphere).
  • FIG. 2 a corresponding pressure-enthalpy diagram for the refrigeration system is shown, with the states marked with single-digit numbers in the pressure-enthalpy diagram occurring at the single-digit points in the system in circles.
  • the states in the respective pressure-enthalpy diagrams are analogous Figures 3 to 7 marked. In the following, reference is no longer made to this individually, but rather, as already explained, it is assumed that the respective in the Figures 3 to 7
  • the pressure-enthalpy diagrams shown represent the states in the refrigeration systems shown in the same figure.
  • the states identified by a number are in each case at the point of the refrigeration system provided with a number in a circle.
  • FIG. 3 a further exemplary refrigeration system is shown, which has a second possible embodiment of a compressor according to the invention.
  • the compressor 110 is again designed in two stages, and essentially corresponds to the compressor 10 of FIG first described embodiment according to Fig. 1 . At this point, the differences to the compressor 10 are above all in accordance with Fig. 1 described.
  • the compressor 110 has two compression stages 114-1 and 114-2.
  • the first compression stage 114-1 compresses a main coolant flow at low pressure (suction pressure), which is made available to the compressor 110 via a low-pressure connection 122 and a low-pressure volume that corresponds in structure and function to that of the first embodiment will, at high pressure.
  • the second compression stage 114-2 is arranged, which also compresses the 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 connection 134, which corresponds to the second intermediate pressure connection 34 of the first embodiment, and an associated intermediate pressure volume, which corresponds in structure and function to the second intermediate pressure volume of the first embodiment.
  • the intermediate pressure refrigerant is used to cool the electric motor of the compressor.
  • the cylinders (cylinder outlets) of both compression stages 114-1 and 114-2 are connected to a common high-pressure sub-volume 138-5, which is the fifth high-pressure sub-volume 38-5 of the first embodiment, which is only connected to the Cylidern (cylinder outlets) of the second compression stage 14-2 is connected, replaced;
  • the remaining partial volumes of the high pressure volume of the second embodiment are designed analogously to those of the first embodiment;
  • a high pressure connection 140 corresponding to the first embodiment is also provided.
  • 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 was supplied to the intercooler without replacement is thus omitted.
  • the refrigerant flows from the high-pressure connection 140 (again via pipelines in each case) to a gas cooler 143, which corresponds to the gas cooler 43 in terms of structure and functionality and is cooled there.
  • the refrigerant flow is then divided into the main flow H and the secondary flow N, the secondary flow passing through a first expansion element 146-1, where it is expanded to the intermediate pressure of the compressor.
  • the secondary stream N is then fed to a heat exchanger 162.
  • the main stream H initially does not pass through an expansion device but is fed directly to the heat exchanger 162, so that the main stream H is further cooled by the secondary stream N.
  • the secondary flow is then led to the second compression stage 114-2, more precisely to the intermediate pressure connection 134, while the main flow H passes through an expansion element 146-2, which expands the refrigerant of the main flow or the main flow to a mean pressure that is different from the intermediate pressure can.
  • an expansion element 146-2 which expands the refrigerant of the main flow or the main flow to a mean pressure that is different from the intermediate pressure can.
  • the rotor of the electric motor 12 functions as an oil separator.
  • the compressor housing 15 consists of two parts that are thermally connected to one another in a non-removable manner after the drive device and the compression unit have been introduced. This leads to a high level of stability of the compressor, since loosening of connections, for example due to vibrations, is unlikely.
  • more than two parts can also be used to form the housing 15, which, in spite of a higher number of parts and slightly higher manufacturing costs, may increase the ease of assembly and thus ensure cost savings elsewhere.
  • a third refrigeration system based on the compressor 10, which is a modification of the in Fig. 2 refrigeration system shown is in Fig. 4 shown.
  • the third refrigeration system has a connecting line in the form of a pipe 64 between the collector 50 and the pipe 32, which is arranged between the intercooler 28 and the second intermediate pressure connection 34. This creates a secondary refrigerant flow from collector 50 to the second Compression level 14-2 allows.
  • FIG Fig. 5 Another (fourth) refrigeration system based on the compressor 10 is shown in FIG Fig. 5 shown.
  • the intercooler 28 and the pipelines assigned to it are omitted, but otherwise the fourth refrigeration system is identical to the third refrigeration system according to FIG Fig. 4 .
  • FIG. 6 A fifth, in Fig. 6
  • the refrigeration system shown is based on the refrigeration system of Figure 2 (two-stage compressor with serially arranged compression stages), whereby the refrigerant flow after the gas cooler 43 (analogous to the refrigeration system, which in Fig. 3 is shown) divided into a main flow H and a secondary flow N, the secondary flow passing through a first expansion element 46-1, where it is expanded to the intermediate pressure of the compressor.
  • the secondary stream N is then fed to a heat exchanger 62.
  • the main stream H initially does not run through an expansion element but is fed directly to the heat exchanger 62, so that the main stream H is further cooled by the secondary stream N.
  • the secondary flow is then led to the second compression stage 14-2, more precisely to the intermediate pressure connection 34, while the main flow H passes through an internal heat exchanger 66 and then an expansion element 54, the refrigerant of the main flow H then passes via the evaporator 58, another collector 68 and the internal heat exchanger 66 back to the low pressure connection of the compressor 10.
  • FIG. 7 Finally, another (sixth) refrigeration system is shown, which has a compressor 110 (ie a compressor with parallel compression stages 114-1 and 114-2). In contrast to the refrigeration system according to Fig. 3 however, the sixth refrigeration system does not have a heat exchanger which transfers heat from a main refrigerant flow to a secondary refrigerant flow. The total refrigerant flow passes through, similar to the refrigeration system Fig. 5 an expansion element 146 and then passes into a separator or collector 150.
  • a compressor 110 ie a compressor with parallel compression stages 114-1 and 114-2
  • the sixth refrigeration system does not have a heat exchanger which transfers heat from a main refrigerant flow to a secondary refrigerant flow.
  • the total refrigerant flow passes through, similar to the refrigeration system Fig. 5 an expansion element 146 and then passes into a separator or collector 150.
  • a connection in the form of a pipe 164 extends from the collector 150 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 is fed to the expansion element 154 and via the evaporator 58 arranged thereafter to the first compression stage 114-1.
  • a compressor 10 is a compressor 10 with an eccentric mechanism.
  • the corresponding engine will be discussed in more detail, although this is an example of a compressor according to the invention, which by no means has to be a reciprocating compressor, but may also be a scroll compressor, a screw compressor or any other known type of compressor.
  • the drive unit described below is an advantageous variant.
  • the compressor 10 (which can also be used as the compressor 110) has six pistons 18 which are arranged in corresponding cylinder bores or cylinder sleeves 216 such that they can be moved back and forth in a radial direction.
  • the cylinder bores or cylinder liners 216 themselves are designed as corresponding recesses in a cylinder block 218.
  • the pistons 18 are designed to be movable to and fro in the radial direction.
  • the compressor 10 serves to compress R744 (CO 2 ) as a refrigerant. It should be noted, however, that any other refrigerant (for example R134a, etc.) can also be used.
  • the compressor 10 has the drive device in the form of the drive shaft 16 (cf. for example FIG 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, but in alternative embodiments it can also be coupled to a corresponding belt drive device or some other device.
  • the axial extent of the drive shaft 16 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 extends through it.
  • the drive device in the form of the drive shaft 16 is in operative engagement with an eccentric 228. More precisely, the drive shaft 16 is formed eccentrically in a corresponding region (eccentric section of the drive shaft 16).
  • the eccentric 228 is thus formed integrally and in one piece with and on the drive shaft 16.
  • the eccentric 228 can also be designed as a separate component and attached to the drive shaft 16, in particular articulated or supported accordingly.
  • the eccentric 228, cut perpendicular to the axial direction, has a circular cross section and radially outwardly directed eccentric surfaces 230 which are arranged in a region of an eccentric active section 232.
  • the eccentric active section 232 serves to drive the pistons 18 and is in operative engagement therewith via a connecting rod 234 assigned to each piston 18.
  • the connecting rods 234 are articulated to the piston 18 by means of connecting rod eyes 236, which are formed on the sides of the connecting rods 234 facing the pistons 18.
  • the connecting rods 234 On the side facing the eccentric 228, the connecting rods 234 have an active connecting rod section 238 which is used for operative engagement with the eccentric 228.
  • the eccentric 228 is in active engagement with the connecting rod active sections 238 via a bearing in the form of a needle bearing 240, which is arranged (fitted) on the eccentric active section 232 (circular cross section) and there on the eccentric surface 230.
  • a needle bearing 240 As an alternative to the needle bearing 240, other bearings, in particular plain bearings or roller bearings in any possible design, are conceivable.
  • the bearing 240 ensures a low-friction transfer and a conversion of the movement (rotary movement) of the eccentric 228 into a movement in the radial direction of a connecting rod active section receptacle 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 applied to the connecting rods 234 and the pistons 18 articulated thereon transfer.
  • the connecting rod active sections 238 corresponding to the circular outer circumference of the bearing 240 which are configured in the manner of a segment of a circle on their side facing the bearing 240, have for this purpose a widened extension in the axial direction at their end facing the bearing, so that they can be expanded by means of two, im Cross-section of L-shaped shells 244, which form the connecting rod active section receptacle 242, are securely arranged on the bearing 240.
  • the connecting rod active sections of all connecting rods 234 are arranged on a circular path around the eccentric 228 and thus also around the eccentric active section 232, which is concentric therewith.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (16)

  1. Compresseur (10, 110) comprenant un carter (15), un dispositif d'entraînement (12) et un dispositif de compression (14) comptant un ou plusieurs étage(s) de compression (14-1, 14-2) en vue de comprimer un agent frigorigène, ledit compresseur (10, 110) comportant, en outre, un ou plusieurs dispositif(s) (20, 36) d'amenée d'agent frigorigène, conçu(s) pour délivrer de l'agent frigorigène audit dispositif de compression (14), et un ou plusieurs dispositif(s) (24, 38) d'évacuation d'agent frigorigène, conçu(s) pour évacuer de l'agent frigorigène hors dudit dispositif de compression (14), sachant qu'au moins une zone de l'un des dispositifs d'amenée d'agent frigorigène, ou au moins une zone d'au moins l'un, notamment de chacun des multiples dispositifs (20, 36) d'amenée d'agent frigorigène, est agencée de manière à être séparée thermiquement d'avec l'un des dispositifs d'évacuation d'agent frigorigène, ou au moins d'avec l'un, notamment d'avec chacun des multiples dispositifs (24, 38) d'évacuation d'agent frigorigène,
    caractérisé par le fait que
    le dispositif (38) d'évacuation d'agent frigorigène comprend cinq régions partielles de haute pression respectivement reliées les unes aux autres avec étanchéité aux gaz, à savoir une première région partielle tubulaire de haute pression (38-1) partant du carter (15) du compresseur et gagnant un raccord (40) de haute pression, à l'extérieur dudit carter (15) du compresseur ; une deuxième région partielle de haute pression (38-2) pareillement de réalisation tubulaire, qui part dudit carter (15) du compresseur et gagne une troisième région partielle de haute pression (38-3), à l'intérieur dudit carter (15) du compresseur ; ladite troisième région partielle de haute pression (38-3) qui présente une réalisation sensiblement parallélépipédique, c'est-à-dire une section transversale rectangulaire, et sert à l'amortissement de pulsations dans le volume sous haute pression ; une quatrième région partielle de haute pression (38-4), qui part de ladite troisième région partielle de haute pression (38-3) et gagne le dispositif de compression (14) ; et une cinquième région partielle de haute pression (38-5) ménagée dans ledit dispositif de compression (14), reliée à des sorties cylindriques de l'étage de compression (14-2) et servant à évacuer de l'agent frigorigène soumis, respectivement, à une haute pression ou à une pression finale de compression.
  2. Compresseur (10, 110) selon la revendication 1,
    caractérisé par le fait que
    - ledit compresseur comprend plus d'un dispositif d'amenée d'agent frigorigène,
    - est notamment de réalisation à étages multiples, et
    - au moins une zone de chaque dispositif (20, 36) d'amenée d'agent frigorigène est agencée de manière à être séparée thermiquement d'avec le ou les dispositif(s) (24, 38) d'évacuation d'agent frigorigène.
  3. Compresseur (10, 110) selon la revendication 1,
    caractérisé par le fait que
    - ledit compresseur comprend plus d'un dispositif d'amenée d'agent frigorigène,
    - est notamment de réalisation à étages multiples, et
    - au moins une zone de chaque dispositif (20, 36) d'amenée d'agent frigorigène est agencée de manière à être séparée thermiquement d'avec un quelconque autre dispositif (20, 36) d'amenée d'agent frigorigène.
  4. Compresseur (10, 110) selon la revendication 1,
    caractérisé par le fait que
    - ledit compresseur comprend plus d'un dispositif d'évacuation d'agent frigorigène,
    - est notamment de réalisation à étages multiples, et
    - au moins une zone de chaque dispositif (24, 38) d'évacuation d'agent frigorigène est agencée de manière à être séparée thermiquement d'avec un quelconque autre dispositif (24, 38) d'évacuation d'agent frigorigène.
  5. Compresseur (10, 110) selon l'une des revendications précédentes,
    caractérisé par le fait que
    la ou les zone(s), agencée(s) de manière à être séparée(s) thermiquement d'avec un autre ou d'autres dispositif(s) (20, 36) d'amenée d'agent frigorigène ou dispositif(s) (24, 38) d'évacuation d'agent frigorigène, ou séparée(s) d'avec des zones de ces derniers, est (sont) réalisée(s) de manière à être séparée(s) d'avec ces derniers et/ou à ne présenter mutuellement aucune surface de contact ou une telle surface réduite à un minimum et/ou à être espacée(s) de ces derniers et/ou à être séparée(s), d'avec ces derniers, par un matériau thermiquement isolant ou doté d'une faible conductivité thermique.
  6. Compresseur (10, 110) selon l'une des revendications précédentes,
    caractérisé par le fait
    qu'une ou plusieurs des zones, agencées de manière à être séparées thermiquement d'avec un autre ou d'autres dispositif(s) d'amenée d'agent frigorigène ou dispositif(s) (24, 38) d'évacuation d'agent frigorigène, s'étend(ent) jusqu'au dispositif de compression (14) à partir de la face intérieure du carter (15) dudit compresseur.
  7. Compresseur (10, 110) selon l'une des revendications précédentes,
    caractérisé par le fait
    qu'un dispositif (20, 36) d'amenée d'agent frigorigène débouche dans le carter dudit compresseur, en particulier dans la région du dispositif d'entraînement (12) ou au voisinage de celui-ci.
  8. Compresseur (10, 110) selon la revendication 7,
    caractérisé par le fait que
    le dispositif d'amenée d'agent frigorigène, qui débouche dans le carter (15) dudit compresseur, est un dispositif d'amenée (20, 36) dédié à un agent frigorigène soumis à une basse pression ou à un agent frigorigène soumis à une pression intermédiaire.
  9. Compresseur (10, 110) selon l'une des revendications précédentes,
    caractérisé par le fait
    qu'au moins un dispositif (24, 38) d'évacuation d'agent frigorigène, en particulier un dispositif d'évacuation dédié à un agent frigorigène (24) soumis à une pression intermédiaire, est prévu pour être raccordé à une entrée d'un refroidisseur intermédiaire (28) d'agent frigorigène d'une installation frigorifique, ou peut être en communication fluidique avec une entrée d'un refroidisseur intermédiaire d'agent frigorigène dudit compresseur (10, 110).
  10. Compresseur (10, 110) selon l'une des revendications 7 à 9,
    caractérisé par le fait que
    le dispositif (36) d'amenée d'agent frigorigène, qui débouche dans le carter (15) dudit compresseur, est prévu pour être raccordé à une sortie d'un refroidisseur intermédiaire (28) d'agent frigorigène d'une installation frigorifique, ou peut être en communication fluidique avec une sortie d'un refroidisseur intermédiaire d'agent frigorigène dudit compresseur (10, 110).
  11. Compresseur (10, 110) selon l'une des revendications précédentes,
    caractérisé par le fait que
    le dispositif d'entraînement comporte un moteur électrique (12) muni d'un rotor et d'un stator, ledit rotor remplissant la fonction d'un séparateur d'huile dédié à de l'agent frigorigène qui lui est délivré.
  12. Compresseur (10, 110) selon l'une des revendications précédentes,
    caractérisé par le fait que
    ledit compresseur (10, 110) est de réalisation à deux étages et comprend un dispositif (20) d'amenée d'agent frigorigène, dédié à un agent frigorigène soumis à une basse pression, ainsi qu'un dispositif (36) d'amenée d'agent frigorigène dédié à un agent frigorigène soumis à une pression intermédiaire, de même qu'un dispositif (24) d'évacuation d'agent frigorigène, dédié à un agent frigorigène soumis à une pression intermédiaire, et un dispositif (38) d'évacuation d'agent frigorigène dédié à un agent frigorigène soumis à une haute pression, sachant qu'au moins des zones, en particulier des zones de chaque dispositif (20, 36) d'amenée d'agent frigorigène et de chaque dispositif (24, 38) d'évacuation d'agent frigorigène, situées à l'intérieur dudit compresseur (10, 110), sont respectivement agencées avec espacement mutuel.
  13. Compresseur selon l'une des revendications précédentes,
    caractérisé par le fait que
    ledit compresseur (10, 110) est prévu pour du R744 en tant qu'agent frigorigène.
  14. Compresseur (10, 110) selon l'une des revendications précédentes,
    caractérisé par le fait que
    ledit compresseur (10, 110) comprend au moins deux parties structurelles (15-1, 15-2) de carter, reliées l'une à l'autre avec étanchéité aux gaz et de manière non démontable, et/ou ledit compresseur (10, 110) est d'un type de réalisation hermétique ou semi-hermétique.
  15. Installation frigorifique
    caractérisée par le fait
    qu'elle est munie d'un compresseur (10, 110) conforme à l'une des revendications précédentes.
  16. Installation frigorifique selon la revendication 15,
    caractérisée par le fait
    qu'elle est pourvue d'un refroidisseur intermédiaire (28) conçu pour refroidir de l'agent frigorigène fourni par un dispositif (24, 38) d'évacuation d'agent frigorigène hors du compresseur (10, 110).
EP12824900.0A 2011-12-23 2012-12-24 Compresseur Active EP2795204B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE201110122248 DE102011122248A1 (de) 2011-12-23 2011-12-23 Verdichter
DE102012005297A DE102012005297A1 (de) 2012-03-19 2012-03-19 Verdichtereinheit, sowie Verdichter
PCT/EP2012/005379 WO2013091899A2 (fr) 2011-12-23 2012-12-24 Compresseur

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EP2795204A2 EP2795204A2 (fr) 2014-10-29
EP2795204B1 true EP2795204B1 (fr) 2021-03-10

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WO (1) WO2013091899A2 (fr)

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DE102024100767A1 (de) * 2024-01-11 2025-07-17 Konvekta Aktiengesellschaft Flexible Verdichtungseinrichtung und Kältemittelkreislauf damit sowie Verfahren dazu

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Publication number Publication date
CN104114959A (zh) 2014-10-22
CN104114959B (zh) 2021-02-05
EP2795204A2 (fr) 2014-10-29
WO2013091899A2 (fr) 2013-06-27
US20150300337A1 (en) 2015-10-22
WO2013091899A3 (fr) 2013-10-17

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