WO2019185121A1 - Kälteanlage - Google Patents
Kälteanlage Download PDFInfo
- Publication number
- WO2019185121A1 WO2019185121A1 PCT/EP2018/057773 EP2018057773W WO2019185121A1 WO 2019185121 A1 WO2019185121 A1 WO 2019185121A1 EP 2018057773 W EP2018057773 W EP 2018057773W WO 2019185121 A1 WO2019185121 A1 WO 2019185121A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- pressure
- compressor
- refrigeration system
- refrigerant compressor
- Prior art date
Links
Classifications
-
- 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
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- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B27/053—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders
- F04B27/0536—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders with two or more series radial piston-cylinder units
- F04B27/0538—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with an actuating element at the inner ends of the cylinders with two or more series radial piston-cylinder units directly located side-by-side
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- 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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
-
- 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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
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- 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
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- 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
- F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
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- 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
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- 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
- F25B31/00—Compressor arrangements
- F25B31/006—Cooling of compressor or motor
-
- 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
-
- 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
Definitions
- the invention relates to a refrigeration system, in particular a transport refrigeration system comprising a working in particular with CO2 refrigerant refrigerant circuit in which a total mass flow of the refrigerant is guided, arranged in the refrigerant circuit, compressed to high pressure refrigerant cooling high-pressure side heat exchanger, in the refrigerant circuit on the high-pressure side Heat exchanger following arranged expansion element which cools the total mass flow of the refrigerant in the active state by expansion and thereby generates a main mass flow of liquid refrigerant and an additional mass flow of gaseous refrigerant, which enter an intermediate pressure accumulator and in this in the main mass flow and the Additional mass flow to be separated, at least one cooling stage, which expands the main mass flow from the intermediate pressure accumulator in at least onedeexpansionsorgan to a low pressure and thereby a low pressure side heat exchanger provides cooling capacity, and a the main mass flow of low pressure to high pressure compressing refrigerant compressor unit.
- Compressor stage for compressing the compressed to medium pressure refrigerant of the main mass flow to high pressure and that the additional mass flow from the intermediate pressure accumulator enters the second compressor stage of the refrigerant compressor unit for compression to high pressure.
- the solution according to the invention thus provides an easy way to operate a refrigeration system with a refrigerant compressor unit, in which the main mass flow and the additional mass flow can be compressed in an optimal manner to high pressure.
- the refrigeration system according to the invention provides the option of using CO2 as a refrigerant, while optimally operating the refrigeration system.
- the first compressor stage of the refrigerant compressor unit is connected to a medium-pressure side heat exchanger which cools the compressed to medium pressure main mass flow before it enters the second compressor stage.
- This solution especially when using CO2 as a refrigerant, makes it possible to cool the refrigerant, which has been significantly heated during compression to medium pressure, before compressing to high pressure.
- the medium-pressure side heat exchanger could be cooled by any media.
- the medium-pressure-side heat exchanger so that it is cooled by the refrigerant flowing at low pressure to the refrigerant compressor unit.
- the medium-pressure side heat exchanger is an external heat exchanger arranged outside the refrigerant compressor unit.
- This external heat exchanger can be cooled by a variety of media. It is particularly advantageous if ambient air is used for cooling.
- the intermediate pressure is higher than the medium pressure and that the additional mass flow is expanded by an effetsenstromexpansions- organ to medium pressure and at medium pressure in the second
- Compressor stage occurs.
- the intermediate pressure essentially corresponds to the medium pressure, so that the total mass flow can be expanded to medium pressure by the expansion element following the first external heat exchanger.
- the low pressure in the case of CO2 as refrigerant lies in the range from 1 bar to 60 bar.
- the mean pressure is in the range from 20 bar to 120 bar. Furthermore, it is preferably provided that for CO 2 as refrigerant the high pressure is in the range from 50 bar to 160 bar.
- the refrigerant compressor unit comprises a refrigerant compressor and an electric drive motor.
- the additional mass flow is supplied to an engine compartment of the refrigerant compressor unit for cooling the electric drive motor before entering the second compressor unit.
- a further advantageous solution provides that the compressed to medium pressure main mass flow after cooling by the medium-pressure side heat exchanger and before entering the second compressor stage enters the engine compartment for cooling the electric drive motor.
- a drive space of the refrigerant compressor, from which a drive of the compressor stages takes place is maintained at medium pressure.
- Compressor levels can be kept as low as possible.
- the drive space communicates with the engine compartment via a connection channel and or if the refrigerant flows through the drive space after cooling of the electric drive motor in the engine compartment.
- the refrigerant compressor unit is designed as a semi-hermetic compressor, wherein in an overall housing of the same both the electric drive motor and the refrigerant compressor are arranged.
- the refrigerant compressor of the refrigerant compressor unit is designed as a piston compressor, since can be achieved with reasonable mechanical effort, in particular with such a piston compressor, the pressures mentioned for CO2 as refrigerant.
- the reciprocating compressor has a plurality of cylinder units, of which at least one forms the first compressor stage and at least one forms the second compressor stage.
- the two compressor stages are designed so that the ratio of the stroke volume of the first compressor stage to the stroke volume of the second compressor stage is in the range of 1.5 / 1 to 2/1.
- At least two cylinder units form the first compressor stage. Furthermore, it is preferably provided that the at least one second
- Cylinder unit of the second compressor stage is arranged relative to the at least one cylinder unit of the first compressor stage with respect to a central axis of the drive shaft of the cylinder units at an angular distance, so that thereby, for example, the cylinder units of the two compressor stages V-shaped or can be arranged in opposite directions, in particular an advantageous torque distribution to reach.
- Another advantageous solution provides that all cylinder units of the compressor stages are arranged in a row.
- the housing of the refrigerant compressor and in particular the overall housing of the refrigerant compressor unit is formed of aluminum.
- the overall housing of the refrigerant compressor unit has a housing sleeve and bearing caps arranged on both sides of the housing sleeve, which are all made of aluminum.
- the housing has cylinder heads which are formed from aluminum.
- Refrigerant compressor unit is arranged on a cylinder head of the second compressor stage.
- a further advantageous solution provides that a low-pressure connection of the refrigerant compressor unit is arranged on a cylinder head of the first compressor stage.
- a medium-pressure outlet of the refrigerant compressor unit is arranged on a cylinder head of the first compressor stage.
- a medium-pressure inlet of the refrigerant compressor unit is arranged in the region of a motor housing.
- the invention relates to a refrigerant compressor unit, in particular for compressing CO2 as a refrigerant, comprising a refrigerant compressor and an electric drive motor, wherein the
- Refrigerant compressor has a first compressor stage for compressing supplied at low pressure refrigerant, in particular CO2, to medium pressure and a second compressor stage for compressing the medium pressure compressed refrigerant, in particular CO2, at high pressure and wherein
- the refrigerant compressor unit has a medium-pressure outlet connected to the first compressor stage and a medium-pressure inlet communicating with the second compressor stage.
- the medium-pressure inlet not only with the medium-pressure outlet, but via the medium-pressure inlet in a refrigerant circuit accumulating refrigerant, which is also present, for example, at medium pressure, the second compressor stage and to compress in this to high pressure.
- the refrigerant compressor according to the invention can thus be advantageously used in particular in a refrigerant circuit with expansion of the refrigerant to an intermediate pressure to compress not only the refrigerant compressed to medium pressure in the first compressor stage, but also the refrigerant expanded to an intermediate pressure to high pressure again.
- a drive space of the refrigerant compressor, from which a drive of the compressor stages takes place is maintained at medium pressure.
- the drive space communicates with the engine compartment via a connection channel.
- the connecting channel can be designed so that it leads only to a pressure equalization between the drive chamber and the engine compartment, but the connecting channel can also be designed so that the refrigerant flowing through the engine compartment refrigerant is supplied through the latter of the second compressor stage.
- the refrigerant compressor unit is designed as a semi-hermetic compressor, wherein in an overall housing of the same both the electric drive motor and the refrigerant compressor are arranged.
- this solution has the advantage that it is very compact and, on the other hand, has the advantage that in this way the refrigerant can be used in a simple manner before being fed to the second compressor stage for cooling the electric drive motor.
- a particularly favorable solution provides that the refrigerant compressor is designed as a reciprocating compressor, as can be achieved with a piston compressor with reasonable mechanical effort, the pressure differences, which are required in particular for the compression of CO2 as a refrigerant.
- the reciprocating compressor is designed such that the reciprocating compressor has a plurality of cylinder units, of which at least one forms the first compressor stage and at least one forms the second compressor stage.
- At least two cylinder units form the first compressor stage. Furthermore, it has proven to be advantageous for constructive reasons, when the at least one cylinder unit of the second compressor stage is arranged relative to the at least one cylinder unit of the first compressor stage with respect to a central axis of the drive shaft of the cylinder units at an angular distance to either the respective cylinder units V-shaped or in opposite directions to each other.
- Another expedient solution provides that the cylinder units of the compressor stages are arranged in a row, resulting in a very compact design results.
- the housing of the refrigerant compressor in particular the housing of the refrigerant compressor unit is formed of aluminum.
- such a housing of the refrigerant compressor unit is able to withstand the high pressures and thus has sufficient stability and, on the other hand, has the lowest possible mass, in particular when used in a transportable cooling unit.
- the overall housing of the refrigerant compressor unit has a housing sleeve and bearing caps arranged on both sides of the housing sleeve, which are all made of aluminum.
- Has cylinder heads which are formed of aluminum. With regard to the various connections for high pressure and low pressure so far no further details have been made.
- an advantageous solution provides that a high-pressure connection of the refrigerant compressor unit is arranged on a cylinder head of the second compressor stage.
- a further advantageous solution provides that a low-pressure connection of the refrigerant compressor unit is arranged on a cylinder head of the first compressor stage.
- a further expedient solution provides that a medium-pressure outlet of the refrigerant compressor unit is arranged on a cylinder head of the first compressor stage.
- a medium-pressure inlet of the refrigerant compressor unit is arranged in the region of a motor housing.
- the low pressure is at values in the range of 1 bar to 60 bar.
- the medium pressure in the range from 20 bar to 120 bar for CO2 as refrigerant.
- the high pressure is in the range from 50 bar to 160 bar.
- FIG. 1 is a schematic representation of a cooling unit, in particular designed as a transport refrigeration unit, with a refrigeration system according to the invention.
- FIG. 2 shows a schematic illustration of a first exemplary embodiment of a refrigeration system according to the invention
- FIG. 3 is a schematic enlarged view of a refrigerant compressor unit for the first embodiment of the refrigeration system according to the invention
- FIG. 4 is a schematic representation of a second embodiment of a refrigeration system according to the invention.
- Fig. 6 shows a third embodiment of a refrigeration system according to the invention.
- a cooling unit generally designated 10, includes a thermally insulated housing 12 which encloses an interior 14 in which temperature sensitive goods 16 or temperature sensitive cargo 16 can be stored, the temperature sensitive articles 16 or the temperature sensitive cargo 16 being from a gaseous medium 18, in particular Air, which is maintained at a defined temperature level to keep the temperature-sensitive cargo 16 or the temperature-sensitive goods 16 within a certain temperature range.
- a gaseous medium 18, in particular Air which is maintained at a defined temperature level to keep the temperature-sensitive cargo 16 or the temperature-sensitive goods 16 within a certain temperature range.
- the cooling unit 10 is preferably designed as a transportable cooling unit, for example as a construction for a truck or freight wagon or as a conventional transport container for transporting temperature-sensitive freight 16 either by a truck or the train or a ship.
- a circulation flow 22 of the gaseous medium 18 runs in the interior 14, wherein, starting from a temperature control unit 24, an inlet flow 26 enters the interior space 14, flows through it and flows through Outlet stream 28 in turn enters the temperature control unit 24.
- the circulation flow 22 is thereby generated by a blower unit 32, which is arranged in the temperature control unit 24 and is maintained at the desired temperature by an internal heat exchanger 34 which is arranged in the temperature control unit 24.
- the inlet stream 26 preferably exits the tempering unit 24 in a region near a top wall 36 of the insulated housing 12, and the circulation stream 22 is preferably returned to the tempering unit 24 near a bottom wall 38 of the insulated housing 12, thereby forming the outlet flow 28 flowing back to the tempering unit 24 ,
- the temperature control unit 24 is disposed near the top wall 36 of the insulated housing 12 and, for example, near a front wall 48 or near a rear wall 48 thereof.
- An aggregate unit 52 comprising a refrigerant compressor unit 54 with a refrigerant compressor 56 and an electric drive motor 58 is preferably arranged close to the temperature control unit 24 on the thermally insulated housing 12, wherein the unit unit 52 preferably additionally comprises a first external heat exchanger 62 and an external fan unit 64, which For example, generates an air flow 66 from ambient air, which enforces the first external heat exchanger 62.
- the refrigerant compressor unit 54, the internal heat exchanger 34, and the first external heat exchanger 62 are arranged in a refrigerant circuit 70, as a whole, of a refrigeration unit 60 integrated in the refrigeration unit.
- the refrigerant circuit 70 is connected to a high-pressure port 72 of the refrigerant compressor unit 54, starting from which
- Supply line 74 leads to the first external heat exchanger 62, which a total mass flow G of the refrigerant compressor 54 at high pressure PH compressed refrigerant, in the present case, in particular CO2 cools, wherein the refrigerant is in the case of CO2 in a transcritical state.
- the cooling of the refrigerant in the first external high-pressure side heat exchanger unit 62 either by ambient air or by contact with a heat-absorbing medium of any kind, for example, cooling water done.
- the at the high pressure port 72 of the refrigerant compressor unit 54 in the refrigerant circuit 70 supplied total mass flow G flows through the external heat exchanger 62, in the case of CCh in a transcritical state, arranged in the refrigerant circuit 70 expander 76 is expanded by these to an intermediate pressure PZ and then enters a Intermediate pressure accumulator 82, in which the total mass flow G cooled by expansion is divided into a main mass flow H of liquid refrigerant, which deposits as liquid refrigerant bath 84 in the intermediate pressure accumulator 82, and an additional mass flow Z, which a gas bubble 86 above the liquid bath 84 forms.
- the main mass flow H of liquid refrigerant is supplied from the intermediate pressure accumulator 82 to a cooling stage 92 which has a cooling expander 94 which cools the main mass flow H by expansion to low pressure PN and from which the main mass flow H enters the internal low pressure side heat exchanger 34, in which he is able to extract heat by the provision of cooling capacity of the circulation flow 22 in the interior 18 of the cooling unit 10.
- the main mass flow H heated in the heat exchanger 34 then enters the refrigerant compressor unit 54 at low pressure PN via a low-pressure connection 102.
- the refrigerant compressor 56 of the refrigerant compressor unit 54 is designed as a reciprocating compressor and preferably comprises a first compressor stage 112, formed by two cylinder units 114a and 114b respectively driven by a cylinder drive 115a, 115b, in particular an eccentric drive each of which draws the refrigerant of the main mass flow H from an inlet chamber 116a, 116b, and for example, in a common outlet chamber 118 emits.
- the first compressor stage 112 compresses the refrigerant supplied thereto at low pressure, for example at values from 1 bar to 60 bar
- Main mass flow H to a medium pressure PM which is for example at values in the range of 20 bar to 120 bar.
- the main mass flow H compressed to medium pressure PM is then fed to a second external medium-pressure side heat exchanger 124 which, for example, likewise is arranged in the unit unit 52 and, for example, also flows through the external air flow 66.
- the medium pressure supply line 126 is also connected to the gas bubble 86 of the intermediate pressure accumulator 82, so that the additional mass flow Z from the intermediate pressure accumulator 82 via the medium pressure supply line 126 also the medium pressure port 128 of the refrigerant compressor unit 54 is supplied and the mean pressure PM adjusted so that it the intermediate pressure PZ corresponds.
- the medium-pressure inlet 128 is preferably arranged on the motor housing 132 such that the entering refrigerant enters an engine compartment 134, the engine compartment 134 is cooled by the electric drive motor 58, in particular by cooling a rotor 136 and a stator 138 thereof, and then into a second compressor stage 142 of the refrigerant compressor unit 54 occurs.
- the second compressor stage 142 also comprises two each of a cylinder drive 145a, 145b, in particular an eccentric drive,
- the cylinder units 114a and 114b of the first embodiment In the first embodiment of the reciprocating compressor 54 according to the invention, the cylinder units 114a and 114b of the first
- the refrigerant compressor unit 54 is the one receiving the drive shaft 152 and the cylinder drives 115a, 115b, 145a, 145b, and the cylinder units 114a and 114b, respectively
- Cylinder drive space 156 is at medium pressure. This has the advantage that, in particular in the second compressor stage 142, only pressure differences between medium pressure and high pressure occur in the cylinder units 144a and 144b and thereby the load on cylinder drives 145a and 145b for the cylinder units 144a, 144b is lower than in the case of FIG Low pressure in the cylinder drive space 156.
- the load on the cylinder units 144a and 144b itself, especially the pistons thereof, is lower than in the case of low pressure in the cylinder drive space 156.
- refrigerant compressor unit 54 designed as a semi-hermetic compressor, in which the refrigerant compressor 56 and the electric drive motor 58 are arranged in an overall housing 130, the housing sleeve 162, on both sides of the housing sleeve 162 arranged bearing caps 164 and 166 and to the bearing caps 164 and 166 integrally formed bearing receivers 174th and 176 formed of aluminum, wherein in the bearing receivers 174 and 176 rolling bearings 184 and 186th
- an overall drive shaft 188 comprising the drive shaft 152 and the rotor shaft 154, store.
- cylinder heads 192 and 194 which are also made of aluminum, are arranged on the housing sleeve 162, wherein the cylinder head 192 is assigned to the cylinder units 114a and 114b and has the low-pressure connection 102 which is connected to the inlet chambers 116a and 116b , and the outlet chamber 118 connected to the middle pressure outlet 122.
- the cylinder head 194 is associated with the cylinder units 144a and 144b, wherein the inlet chambers 146a and 146b are connected to the engine compartment 134 and / or the cylinder drive space 156 and the outlet chamber 148 is connected to the high-pressure port 72.
- the refrigerant compressor unit 54 is preferably arranged as a stationary compressor, that is to say that a central axis 202 of the overall drive shaft 188 extends substantially vertically, that is, deviates from a vertical by a maximum of ⁇ 30 °.
- cylinder drives 115a, 115b, 145a, 145b for example, in the total drive shaft 188 an obliquely to the central axis 202 extending conveying channel 204 is provided, which forms from a lowermost in the direction of gravity lid 166 lubricant sump lubricant 206 due to the in the conveyor channel acting centrifugal force in the cylinder drive space 156 promotes.
- a driven by the electric drive motor 58 lubricant pump unit for conveying the lubricant in the cylinder drive space 156 is provided.
- a converter 212 is further provided, which is preferably also arranged in the unit unit 52.
- the electric drive motor 58 is controlled speed controlled and thus the cooling capacity of the refrigerant compressor unit 54 steplessly controlled within a designated power range.
- FIGS. 4 and 5 a second exemplary embodiment of a refrigeration system 60 'according to the invention, illustrated in FIGS. 4 and 5, those elements which are identical to those of the first exemplary embodiment are provided with the same reference numerals, so that with regard to the description of the same, reference is made in full to the comments on the first exemplary embodiment can be referenced.
- the refrigerant compressor unit 54 ' is provided with a refrigerant compressor 56', which is used for
- Forming the first compressor stage 112 comprises two cylinder units 114a and 114b, but to form the second compressor stage 142, only one cylinder unit 144 wherein all cylinder units 114a, 114b and 144 are driven by the common drive shaft 152.
- the ratio of the stroke volume of the first compressor stage 112 to the stroke volume of the second compressor stage 142 is approximately in the range of 1.5 / 1 to 2/1.
- a particularly advantageous solution provides, however, that the cylinder units 114a, 114b and 144 are arranged in a row.
- the cylinder head 192 assigned to the first compressor stage 112 and the cylinder head 194 assigned to the second compressor stage 142 are thus preferably also combined to form an overall cylinder head 222, in which both the low-pressure connection 102, the medium-pressure outlet 122 and the high-pressure connection 72 are provided during the medium-pressure inlet 128 is provided on the motor housing 132, for example on a cylinder drive space 156 opposite side of the electric drive motor 58th
- the total drive shaft 188 is arranged so that its central axis 202 extends substantially horizontally, that is, for example, deviates from a precisely horizontal orientation by a maximum of ⁇ 30 °, which in particular in the lowermost region in the direction of gravity of the cylinder drive space 156, a lubricant sump 206 'is formed, from which starting, a lubrication of the cylinder drives 115a, 115b, 145 takes place.
- a valve 232 which in particular between the intermediate pressure accumulator 82 and a junction of a from the second external heat exchanger 124 to the medium pressure supply 126 leading medium pressure line 125 and thus enables an adjustment of an intermediate pressure PZ in insects- collectors 82 such that this intermediate pressure does not necessarily have to be identical to the mean pressure PM, but the possibility exists, the intermediate pressure PZ higher than the mean pressure PM.
- valve 232 is designed as an expansion valve, it is possible in the expansion of the additional mass flow through the
- Expansion valve 232 to additionally cool the additional mass flow, so that it has an improved cooling effect in the cooling of the electric drive motor 58 result.
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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)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressor (AREA)
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2018/057773 WO2019185121A1 (de) | 2018-03-27 | 2018-03-27 | Kälteanlage |
CN201880090632.8A CN111801536B (zh) | 2018-03-27 | 2018-03-27 | 制冷设备 |
EP18716155.9A EP3775716A1 (de) | 2018-03-27 | 2018-03-27 | Kälteanlage |
BR112020017944-2A BR112020017944B1 (pt) | 2018-03-27 | Sistema de refrigeração | |
RU2020134519A RU2782721C2 (ru) | 2018-03-27 | Холодильная установка | |
US17/029,555 US11754321B2 (en) | 2018-03-27 | 2020-09-23 | Refrigeration system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2018/057773 WO2019185121A1 (de) | 2018-03-27 | 2018-03-27 | Kälteanlage |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US17/029,555 Continuation US11754321B2 (en) | 2018-03-27 | 2020-09-23 | Refrigeration system |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2019185121A1 true WO2019185121A1 (de) | 2019-10-03 |
Family
ID=61911548
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2018/057773 WO2019185121A1 (de) | 2018-03-27 | 2018-03-27 | Kälteanlage |
Country Status (4)
Country | Link |
---|---|
US (1) | US11754321B2 (de) |
EP (1) | EP3775716A1 (de) |
CN (1) | CN111801536B (de) |
WO (1) | WO2019185121A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN113833633A (zh) * | 2020-06-24 | 2021-12-24 | 比泽尔制冷设备有限公司 | 制冷介质压缩机 |
EP3929436A1 (de) * | 2020-06-24 | 2021-12-29 | BITZER Kühlmaschinenbau GmbH | Kältemittelverdichter |
US11754321B2 (en) * | 2018-03-27 | 2023-09-12 | Bitzer Kuehlmaschinenbau Gmbh | Refrigeration system |
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CN108533490A (zh) * | 2018-06-22 | 2018-09-14 | 珠海格力电器股份有限公司 | 压缩机及空调*** |
CN115235132A (zh) * | 2022-09-21 | 2022-10-25 | 山东天瑞重工有限公司 | 一种磁悬浮冷水机组 |
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CN113833633A (zh) * | 2020-06-24 | 2021-12-24 | 比泽尔制冷设备有限公司 | 制冷介质压缩机 |
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Also Published As
Publication number | Publication date |
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CN111801536A (zh) | 2020-10-20 |
US20210003321A1 (en) | 2021-01-07 |
EP3775716A1 (de) | 2021-02-17 |
CN111801536B (zh) | 2023-04-28 |
RU2020134519A (ru) | 2022-04-27 |
RU2020134519A3 (de) | 2022-04-27 |
BR112020017944A2 (pt) | 2020-12-22 |
US11754321B2 (en) | 2023-09-12 |
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