EP1914491A2 - Installation de refroidissement - Google Patents

Installation de refroidissement Download PDF

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Publication number
EP1914491A2
EP1914491A2 EP07020003A EP07020003A EP1914491A2 EP 1914491 A2 EP1914491 A2 EP 1914491A2 EP 07020003 A EP07020003 A EP 07020003A EP 07020003 A EP07020003 A EP 07020003A EP 1914491 A2 EP1914491 A2 EP 1914491A2
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EP
European Patent Office
Prior art keywords
pressure
mass flow
refrigerant
cooling
compressor unit
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.)
Granted
Application number
EP07020003A
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German (de)
English (en)
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EP1914491B1 (fr
EP1914491A3 (fr
Inventor
Oliver Javerschek
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Bitzer Kuehlmaschinenbau GmbH and Co KG
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Bitzer Kuehlmaschinenbau GmbH and Co KG
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Publication of EP1914491A3 publication Critical patent/EP1914491A3/fr
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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
    • 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
    • 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
    • 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
    • F25B2400/075—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
    • F25B2400/22—Refrigeration systems for supermarkets
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel

Definitions

  • the invention relates to a refrigeration system, comprising a refrigerant circuit, in which a total mass flow of a refrigerant is guided, arranged in the refrigerant circuit, high-pressure side refrigerant cooling heat exchanger, a refrigerant circuit disposed in the expansion cooling means cools the total mass flow of the refrigerant in the active state and thereby a main mass flow of liquid Generates refrigerant and an additional mass flow of gaseous refrigerant, a reservoir for the main mass flow, at least one normal cooling mass flow from the reservoir taking normal cooling stage with a normal cooling expansion and this downstream, low pressure side, cooling capacity for normal cooling available normal cooling heat exchanger, a Tiefkühlge aparmassenstrom from the reservoir enticalde deep freezing stage with a Tiefkühpansionsorgan and a downstream cooling capacity available Uigh- yielding deep-freeze heat exchanger and with this deep-freeze heat exchanger downstream refrigeration compressor unit, and at least one arranged in the refrigerant circuit refrigerant compressor
  • Such a refrigeration system which is particularly suitable for carbon dioxide as a refrigerant, is from the DE 10 2004 038 640 A1 known, wherein in this refrigeration system, the efficiency, especially in connection with the operated freezing stage, is not optimal.
  • the invention is therefore based on the object to improve a refrigeration system of the type described above in such a way that it has a better efficiency.
  • the advantage of the solution according to the invention lies in the fact that the possibility was created by the Tiefkühplexionskühlinraum to increase the temperature to be absorbed at freezing temperature and thus further increase the efficiency of the refrigeration system according to the invention, wherein the potential for freezing temperature Enthalpieerhöhung by receiving heat energy in the Freezer heat exchanger is optimally adapted to the thermodynamic states of the refrigerant, in particular the thermodynamically possible states of carbon dioxide as a refrigerant.
  • an embodiment provides that this has to increase the available enthalpy difference in the heat exchanger or to further reduce the enthalpy of the main cooling mass flow Lichtkühleexpansions adopted which relaxes the Tiefkühlgelegimassenstrom in the active state and thereby generates a Wegühpulsionsorgan supplied in the freezer accumulator a Wegmaschinenmassenstrom and the Tiefkühlzusatzmassenstrom ,
  • the intermediate cryogenic pressure is between the intermediate pressure in the expansion cooling device and a suction pressure of the deep-freeze compressor unit in order to optimally adapt the enthalpy reduction possible by expansion in the deep-freeze cooling device to the conditions of the refrigeration system.
  • An expedient solution provides that in the deep-frozen expansion cooling device, the intermediate cryogenic pressure is at least approximately 2 bar lower than the intermediate pressure of the expansion cooling device.
  • the intermediate cooling pressure is at least approximately 4 bar lower than the intermediate pressure of the expansion cooling device.
  • an expedient solution provides that in the deep-freeze expansion device the intermediate cryogenic pressure is at least approximately 2 bar higher than the suction pressure of the deep-freeze compressor unit.
  • the intermediate cryogenic pressure is at least approximately 4 bar higher than the suction pressure of the refrigerated compressor unit.
  • a particularly expedient solution provides that in the Tiefksselexpansionskssel adopted an intermediate cryogenic pressure is present, which is located in a middle third of a divided into three thirds pressure difference between the intermediate pressure in the expansion cooling device and the suction pressure of the frozen compactor unit.
  • a particularly simple solution provides that the frozen additional mass flow is supplied to the refrigerant compressor unit, so that no compression takes place via the deep-freeze compressor unit.
  • a simplified embodiment of the refrigeration system according to the invention provides that in this the additional frozen mass flow is fed to a suction port of the refrigerant compressor unit and thus an additional compressor stage is not required.
  • a simple embodiment of the refrigeration system according to the invention provides that the freeze-additive mass flow is supplied to the suction connection of the refrigerant compressor unit in a pressure-regulating manner and thus no additional measures for pressure regulation of the intermediate cryogenic pressure are required.
  • the intermediate cryogenic pressure is selected so that it lies in the region of the low pressure at the suction connection of the refrigerant compressor unit.
  • the intermediate cryogenic pressure approximately corresponds to the low pressure at the suction connection of the refrigerant compressor unit.
  • the refrigerant compressor unit could be constructed such that it has different refrigerant compressors for the normal cooling mass flow and the additional frozen mass flow.
  • a particularly simple solution provides that the frozen additional mass flow is supplied together with the low-pressure expanded normal cooling mass flow of the refrigerant compressor unit, so that the refrigerant compressor unit sucks and compresses the sum of both mass flows.
  • This deep-freeze main mass flow leaving the freezer compressor unit could also be fed to a separate compressor stage.
  • a structurally simple solution provides that the frozen main mass flow compressed by the deep-freeze compressor unit is fed to the refrigerant compressor unit and thus undergoes compression to high pressure by the refrigerant compressor unit.
  • the further compression of the main cooling mass flow can then take place via an additional compressor stage of the refrigerant compressor unit.
  • the deep-freeze main mass flow compressed by the deep-freeze compactor unit is mixed with the expanded normal air mass flow stream and fed to a suction port of the refrigerant compressor unit.
  • the mixing of the compacted, but heated mainstream cooling mass flow with the expanded, but cooler normal cooling mass flow causes the enthalpy of the main low-temperature mass flow to be lowered and thus sets a total enthalpy of the compacted main-body mass flow and the expanded normal-mass flow.
  • the thereby occurring heating of the expanded normal cooling mass flow caused by the frozen main mass flow compressed by the deep-freeze compressor unit causes the refrigerant to be compressed by the refrigerant compressor unit to be supplied substantially free of liquid components and thus superheated.
  • a particularly advantageous solution provides that the frozen main mass flow, the deep-freeze additive mass flow and the expanded normal-mass flow are compressed together and fed to the suction port of the refrigerant compressor unit and thus all of the aforementioned mass flows are compressed together by the refrigerant compressor unit.
  • This solution has the particular advantage that different operating conditions, that is, different cooling capacities of the normal cooling stage and the deep-freezing stage at least partially average and thus simplifies the control of the refrigerant compressor unit.
  • an advantageous solution provides that the Tiefkühplexionskssel founded reduces the enthalpy of the main cooling mass flow by at least 10% compared to the enthalpy of the total frozen cooling mass flow.
  • the deep-freeze cooling device reduces the enthalpy of the main bulk of the cooling mass by at least 20%.
  • thermodynamic state of the main cooling mass flow can be defined by the fact that the deep cooling expansion cooling device generates the main cooling mass flow in a thermodynamic state whose pressure and enthalpy values are lower than those of the normal cooling mass flow.
  • the pressure and enthalpy values of the main cooling mass flow caused by the deep-freeze expansion device are close to the saturation curve in the enthalpy / pressure diagram.
  • an advantageous embodiment provides that the expansion cooling device has an expansion element for the expansion of the total mass flow to the intermediate pressure and that a maximum value of the intermediate pressure is adjustable.
  • the intermediate pressure can be set to a maximum value of 40 bar or less, since this makes it easy to carry out the piping of at least the normal cooling stage.
  • the adjustability is achieved by adjustability of the expansion device, so that standard components usually approved up to this pressure can be used.
  • a further advantageous embodiment provides that the intermediate pressure can be set by supplying at least part of the additional mass flow to an additional suction port of the refrigerant compressor unit.
  • the refrigerant compressor unit from a multiplicity of refrigerant compressors and thereby to provide one of the refrigerant compressors for compressing the additional mass flow.
  • the available at the RajsauganQuery capacity of the refrigerant compressor unit is adjustable, so that on the setting of the available flow rate and the intermediate pressure is adjustable.
  • the adjustment of the delivery rate at toastsauganQuery can be adjusted either by the number of active additional compressor stages or the number of individual provided for compressing the additional mass flow refrigerant compressor and / or the speed thereof.
  • the refrigerant compressor unit provides another solution that the intermediate pressure by supplying at least a portion of the additional mass flow to a suction port of the refrigerant compressor unit is adjustable.
  • This solution has the advantage that it is not necessary to provide additional compressor stages or special refrigerant compressors provided for the additional suction connection, but rather the latter Additional mass flow must be supplied only to the suction port of the refrigerant compressor unit, with which anyway a compression of the main mass flow of the refrigerant.
  • this solution has a slight disadvantage in terms of reducing the efficiency.
  • a particularly favorable solution which allows an optimal operation of the refrigeration system substantially in all operating conditions and in all temperature conditions, provides a control which feeds the additional mass flow either the Rajsaugan gleich or this and in parts the suction port of the refrigerant compressor unit.
  • an intended 1925sauganQuery and the compressor power available at this time can always exploit, but keep the intermediate pressure below an adjustable maximum value in cases where a high additional mass flow, if at a large additional mass flow still a part thereof the suction port of the refrigerant compressor unit can be fed.
  • an advantageous embodiment provides that the expansion cooling device reduces the enthalpy of the main mass flow by at least 10% compared to the enthalpy of the total mass flow.
  • the expansion cooling device reduces the enthalpy of the main mass flow by at least 20%.
  • the expansion cooling device is active in a supercritical operation of the refrigeration system.
  • Such supercritical operation is particularly in the use of carbon dioxide as a refrigerant and conventional ambient temperatures for cooling the heat exchanger.
  • the expansion cooling device generates the main mass flow in a thermodynamic state whose pressure and enthalpy values are lower than those of a maximum of the saturation curve.
  • the pressure and enthalpy values of the main mass flow caused by the expansion cooling device are close to the saturation curve in the enthalpy / pressure diagram.
  • the refrigerant enters into the suction connection of the refrigerant compressor unit incoming refrigerant can be heated by a heat exchanger connected upstream of this.
  • a heat exchanger By means of such a heat exchanger, the refrigerant to be sucked can be heated to such an extent that essentially liquid components are excluded, so that this refrigerant can be designated as overheated.
  • the heat exchanger could be supplied in a variety of ways heat.
  • thermoelectric heat exchanger removes heat from the high-pressure side heat exchanger exiting total mass flow, so that the exiting from the high-pressure side heat exchanger, but still heated total mass flow can be used to heat the refrigerant entering the refrigerant compressor unit, while still cooling the total mass flow in return takes place.
  • a first exemplary embodiment of a refrigeration system according to the invention comprises a refrigerant circuit denoted as a whole by 10, in which a refrigerant compressor unit designated as a whole is arranged, which in the exemplary embodiment illustrated comprises a plurality of individual refrigerant compressors, for example four refrigerant compressors.
  • Each of the refrigerant compressor 14 has a port 16 on the suction side and a port 18 on the pressure side, wherein all suction-side ports 16 are combined to form a suction port 20 of the refrigerant compressor unit 12 and all pressure-side ports 18 are combined to form a pressure port 22 of the refrigerant compressor unit 12.
  • each of the refrigerant compressors 14 also has an additional connection 24, wherein all auxiliary connections 24 of the refrigerant compressors are combined to form an additional suction connection 26 of the refrigerant compressor unit 12.
  • the refrigerant drawn via the auxiliary suction port 26 from the refrigerant compressor unit 12 is also compressed therefrom to high pressure and, together with the suction port 20 sucked and high-pressure compressed refrigerant at the pressure port 22 of the refrigerant compressor unit 12 from.
  • the compressed to high pressure refrigerant at the pressure port 22 of the refrigerant compressor unit 12 forms a total mass flow G and this flows through a high-pressure side heat exchanger 30, through which a cooling of the high-pressure compressed refrigerant.
  • the cooling of the compressed high-pressure refrigerant in the heat exchanger 30 is the same or merely cooling to a lower temperature, wherein the refrigerant remains in the gas phase.
  • carbon dioxide that is CO 2
  • a supercritical cyclic process is present under normal ambient conditions, in which only a cooling takes place to a temperature which corresponds to an isotherm running outside the dew and boiling curve or saturation curve, so that none Liquefaction of the refrigerant occurs.
  • a subcritical cycle process provides that the heat exchanger 30 cools to a temperature that corresponds to an isotherm passing through the dew and boiling or saturation curves of the refrigerant.
  • the cooled by the heat exchanger 30 refrigerant is subsequently expanded via a pressure line 31 by an expansion cooling means 32 representing an expansion valve 32, for example, an expansion valve to an intermediate pressure PZ, which corresponds to a the tau and boiling curve or saturation curve of the refrigerant passing isotherms.
  • an expansion cooling means 32 representing an expansion valve 32, for example, an expansion valve to an intermediate pressure PZ, which corresponds to a the tau and boiling curve or saturation curve of the refrigerant passing isotherms.
  • the entering into the expansion member 32 and coming from the heat exchanger 30 total mass flow G is placed in a thermodynamic state in which a main mass flow H is in the form of liquid refrigerant and an additional mass flow Z in the form of gaseous refrigerant. Both mass flows are collected in a designated as a collector 34 reservoir and separated from each other, and the additional mass flow Z is a via the collector 34 to the RajsauganQuery 26 extending suction line 36 through the refrigerant compressor unit 12th aspirated, wherein the intermediate pressure PZ in the collector 34 can be set by the delivery capacity of the refrigerant compressor unit 12 available at the additional suction connection 26.
  • an adjustment of the intermediate pressure PZ to a pressure of less than 40 bar to interpret the following on the collector 34 line and component system of the refrigerant circuit 10 to a pressure of less than 40 bar.
  • a control unit 40 which detects the intermediate pressure PZ in the collector with a pressure sensor 42 and is also able to connect the individual auxiliary ports 24 of the individual refrigerant compressor 14 to the Rajsaugan gleich 26 or not switch on.
  • the refrigerant compressors 14 may correspond to those of German patent application 10 2005 009 173.3 be formed and, for example, be formed as a suction-side connections of one of a plurality of cylinders of the respective refrigerant compressor 14, wherein this cylinder can either be used for sucking refrigerant from the additional mass flow Z via the RajsauganQuery 26 or for sucking refrigerant from the suction port 20 of Refrigerant compressor unit 12 supplied expanded main mass flow.
  • the collector 34 there is a division of the main mass flow H consisting of liquefied refrigerant into a normal cooling mass flow N, which is supplied to at least one normal-cooling expansion element 50 or two normal-cooling expansion devices 50a, 50b and at least one normal-cooling heat exchanger 52 connected downstream of the respective normal-cooling expansion element 50.
  • the normalized cooling mass flow N expanded to low pressure PN is supplied via a suction line 54 to the suction port 20 of the refrigerant compressor unit 12 and compressed by the latter to high pressure PH.
  • the main cooling mass flow TH and the auxiliary cooling mass flow TZ are separated from one another in a deep-cooling expansion cooling device 62 and designed as a collector 64, wherein the Tiefkühlzusatzmassenstrom TZ is discharged via a 64 leading from the collector 64 to a mixer 66 discharge line.
  • the mixer 66 is preferably arranged in the suction line 54 and mixes the frozen additional mass flow TZ with the expanded normal cooling mass flow N from the at least one normal cooling heat exchanger 52, so that then both the Tiefkühlzusatzmassenstrom TZ and the expanded normal mass flow N mixed with each other are fed to the suction port 20 of the refrigerant compressor unit 12 ,
  • the main cooling main mass flow TH collecting in the collector 64 is then supplied to at least one deep-freeze PTN and supplied to the respective deep-freeze heat exchanger 72 which is connected to the respective at least one deep-freeze expansion element 70, in which the main bulk cooling TH flow cooled by the expansion is able to to absorb heat by increasing the enthalpy at cryogenic temperatures.
  • the frozen main mass flow TH expanded to the low-pressure low-pressure PTN is fed via a freezer heat exchanger 72 connected to a Tiefkühlsaug Ober 74 a deep-freeze unit 82, which for example also includes a plurality of deep-freeze compressors 84, the individual deep-freeze compressors 84 are switchable depending on the required compressor power.
  • the deep-freeze compressors 84 also each have a suction-side connection 86 and a pressure-side connection 88, wherein the suction-side connections 86 are combined to form a suction connection 90 of the deep-freeze compressor unit 82 and the pressure-side connections 88 are combined to form a pressure connection 92 of the deep-freeze compressor unit 82.
  • the suction port 90 of the deep-freeze compressor unit 82 is connected to the deep-freeze suction line 74, while the pressure connection 92 of the deep-freeze compacting unit 82 is connected to a deep-freeze discharge line 94, which is guided to the mixer 66.
  • the mixer 66 mixes not only the normalized air mass flow N expanded to low pressure PN, the frozen auxiliary mass flow TZ expanded to the intermediate deepfreeze pressure PTZ, but also the main low-pressure mass flow TH condensed to a deep freeze pressure PTH from the deepfreeze compressor unit 82, so that all three mass flows N, TZ and TH correspond to the Suction port 20 of the refrigerant compressor unit 12 at the low pressure PN, which corresponds to the suction pressure at the suction port 20, fed and compressed by the refrigerant compressor unit 12 to high pressure PH.
  • the refrigerant present at the suction connection 20 of the refrigerant compressor unit 12 corresponds to the state of the point ZA in FIG. 2.
  • a compression of the refrigerant by the refrigerant compressor unit 12 leads to an increase in pressure with a small enthalpy increase and thus to the thermodynamic state ZB in FIG.
  • thermodynamic state ZC wherein the thermodynamic state ZC above the saturation curve or thawing and boiling line 110 for the refrigerant, in this case carbon dioxide, is located, so that in the thermodynamic state ZC the refrigerant is still gaseous.
  • the expansion cooling device 32 By means of the expansion cooling device 32, starting from the state ZC, an isenthalpic expansion of the refrigerant in an expansion element or the almost isentropic expansion takes place in an expander to the intermediate pressure PZ and thus into a thermodynamic state corresponding to the point ZD, which represents a mixture of a liquid phase and a gas phase , wherein in the collector 34, the liquid phase forms the main mass flow H, while the gas phase forms the additional mass flow Z.
  • the main mass flow H reaches a thermodynamic state corresponding to the point ZE with decrease of the enthalpy h in the range of the saturation curve or boiling line, while the additional mass flow Z achieves the thermodynamic state ZF due to enthalpy increase due to enthalpy removal at the main mass flow H, which lies in the region of the saturation curve or saturated steam line or near the saturation curve or saturated steam line, from which the additional mass flow Z is again compressed to the high pressure PH, by the additional mass flow Z is sucked in via the additional suction port 26 of the refrigerant compressor unit 12 and compressed to the high pressure PH.
  • the refrigerant from the main mass flow H is expanded from the state ZE by isenthalp relaxation to the low pressure PN, once in the form of the normal cooling air flow N by the at least one Normalalkühpansionsorgan 50 and another time by the Tiefkühplexionskühl overlooked 62, wherein the Tiefk Anlagenungpischions PTZ automatically to the pressure level of Low pressure PN at the suction port 20 of the refrigerant compressor unit 12 sets, unless special measures to change this pressure are taken.
  • the refrigerant reaches the main mass flow H once as a normal cooling mass flow N and once as Tiefkühlgementsmassenstrom TG the thermodynamic state corresponding to the point ZG in Figure 2.
  • the deep-cooler expansion cooling device 62 and the subsequent collector 64 form a division into a liquid phase, which forms the main cooling mass flow TH, which passes into the thermodynamic state ZH in the region of the saturation curve or boiling line through enthalpy discharge, while the gas phase forms the additional frozen mass flow TZ which is supplied via the discharge line 68 to the suction port 20 of the refrigerant compressor unit 12, wherein the Tiefkühlzusatzmassenstrom TZ starting from the thermodynamic State ZG by enthalpy removal of the main cooling mass flow TH undergoes an enthalpy increase, so that this reaches a thermodynamic state in the region of the saturation curve or saturated steam line or near the saturation curve or saturated steam line in Figure 2.
  • the at least one normal-cooling expansion element 50 and the subsequent normal-cooling heat exchanger 52 form a normal cooling stage 100
  • the deep-cooling expansion cooling device 62, the collector 64, the discharge line 68, the at least one deep-cooling expansion element 70, the deep-freeze heat exchanger 72 and the deep-freeze compressor unit 82 form a deep-freezing stage integrated in the refrigerant circuit 10 102, which is traversed by a part of the main mass flow H, namely the Tiefkühlgeurgeonmassenstrom TG, while the normal cooling 100 flows through the normal cooling mass flow N, where ultimately both the normal cooling mass flow N and the Tiefkühlgeurgeonmassenstrom TG again at low pressure PN via the suction port 20 of the refrigerant compressor unit Sucked 12 and compressed to high pressure PH, wherein the pressure connection 22 of the refrigerant compressor unit 12 leaving total mass flow G not only from the normal cooling enstrom N and the Tiefkühlgeurgeonmassenstrom TG, but additionally includes the additional mass flow Z,
  • the refrigerant of the main cooling mass flow TH is supplied to the at least one deep-free expansion element 70 and undergoes an isenthalpic expansion to the deep-freeze pressure PTN in it, thus reaching the thermodynamic state ZI in FIG.
  • thermodynamic state ZI in FIG. 2 the main cooling mass flow TH can be absorbed by enthalpy increase at the freezing temperature in the at least one deep-freeze heat exchanger 72, thereby achieving the thermodynamic state ZJ in FIG.
  • the state ZJ in FIG. 2 is achieved by the overheating control of the deep-freeze expansion element 70 in the deep-freeze heat exchanger 72.
  • an additional heat input in the suction line 74 is observed.
  • Another possibility provides one or more heat exchangers between the suction line 74 and the liquid line, starting from the point ZI in FIG.
  • thermodynamic state ZJ the main cooling main mass flow TH expanded to the low-pressure low-pressure PTN is compressed by the deep-freeze compressor unit 82 to the suction pressure at the suction connection 20 of the refrigerant compressor unit 12 corresponding to a high-pressure deep-pressure PTH, an enthalpy increase being associated with this compression so that the thermodynamic state ZK in FIG is reached.
  • a connecting line 120 is provided with a throttle member 122 provided therein, which is controllable via the controller 40 '.
  • the second exemplary embodiment fully corresponds to the first exemplary embodiment, so that reference is made in full to the detailed explanations in the first exemplary embodiment.
  • a third embodiment shown in Figure 4, is provided in a modification to the second embodiment that the refrigerant compressor 14 are not provided with additional connections 24, so that the refrigerant compressor unit 12 has no soirsaugan gleich 26, but the entire additional mass flow Z via the connecting line 120 the Suction port 20 is supplied, wherein the throttle member 122 is to be adjusted so that the intermediate pressure PZ is higher than the low pressure PN, which is present at the suction port 20 of the refrigerant compressor unit 12.
  • a heat exchanger element 130a is provided in the suction line 54 between the mixer 66 and the suction connection 20 in a modification of the second exemplary embodiment, which is coupled to a heat exchanger element 130b in the pressure line 31 that is connected between the heat exchanger 30 and the expansion cooling device 32 is arranged and flowed through by the total mass flow G, so that, depending on specific situations by ambient temperatures and partial load conditions, it is possible to heat the refrigerant supplied to the suction port 20 so far that it is free of liquid components.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP07020003.5A 2006-10-17 2007-10-12 Installation de refroidissement Active EP1914491B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006050232A DE102006050232B9 (de) 2006-10-17 2006-10-17 Kälteanlage

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EP1914491A2 true EP1914491A2 (fr) 2008-04-23
EP1914491A3 EP1914491A3 (fr) 2011-01-05
EP1914491B1 EP1914491B1 (fr) 2024-01-17

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US (1) US8056356B2 (fr)
EP (1) EP1914491B1 (fr)
CN (1) CN101165439B (fr)
DE (1) DE102006050232B9 (fr)

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WO2011054396A1 (fr) 2009-11-06 2011-05-12 Carrier Corporation Système de réfrigération et procédé de fonctionnement d'un système de réfrigération
WO2012095186A1 (fr) * 2011-01-14 2012-07-19 Carrier Corporation Système de réfrigération et procédé de fonctionnement d'un système de réfrigération

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WO2010003590A2 (fr) * 2008-07-07 2010-01-14 Carrier Corporation Circuit de réfrigération
WO2010036540A1 (fr) * 2008-09-29 2010-04-01 Carrier Corporation Augmentation de la capacité pendant la descente
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KR101201567B1 (ko) * 2010-09-27 2012-11-14 엘지전자 주식회사 공기 조화기
DE102011012644A1 (de) 2011-02-28 2012-08-30 Gea Bock Gmbh Kälteanlage
CA2807643C (fr) * 2012-02-23 2017-01-03 Systemes Lmp Inc. Sous-refroidissement mecanique de systemes de refrigeration r-744 transcritiques avec recuperation de chaleur et pression de tete flottante de pompe a chaleur
EP2841855B1 (fr) * 2012-04-27 2021-04-14 Carrier Corporation Système de refroidissement et procédé d'opération dudit système
MX350051B (es) * 2012-05-11 2017-08-23 Hill Phoenix Inc Sistema de refrigeración de dióxido de carbono con módulo de aire acondicionado integrado.
US10429109B2 (en) 2013-07-02 2019-10-01 Mitsubishi Electric Corporation Refrigerant circuit and air-conditioning apparatus
US9657969B2 (en) * 2013-12-30 2017-05-23 Rolls-Royce Corporation Multi-evaporator trans-critical cooling systems
DE102014100916A1 (de) * 2014-01-27 2015-07-30 Bitzer Kühlmaschinenbau Gmbh Kälteanlage
DE102014100917A1 (de) * 2014-01-27 2015-07-30 Bitzer Kühlmaschinenbau Gmbh Kälteanlage
EP3023712A1 (fr) * 2014-11-19 2016-05-25 Danfoss A/S Procédé pour commander un système de compression de vapeur avec un récepteur
US9726411B2 (en) * 2015-03-04 2017-08-08 Heatcraft Refrigeration Products L.L.C. Modulated oversized compressors configuration for flash gas bypass in a carbon dioxide refrigeration system
DE102015112439A1 (de) * 2015-07-29 2017-02-02 Bitzer Kühlmaschinenbau Gmbh Kälteanlage
CN106642786A (zh) * 2016-11-24 2017-05-10 松下冷机系统（大连）有限公司 一种采用中间压力供液的二氧化碳制冷循环系统
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PL3628942T3 (pl) 2018-09-25 2021-10-04 Danfoss A/S Sposób sterowania układem sprężania pary przy zmniejszonym ciśnieniu ssania
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WO2012095186A1 (fr) * 2011-01-14 2012-07-19 Carrier Corporation Système de réfrigération et procédé de fonctionnement d'un système de réfrigération

Also Published As

Publication number Publication date
EP1914491B1 (fr) 2024-01-17
DE102006050232B3 (de) 2008-02-07
US20080110200A1 (en) 2008-05-15
CN101165439B (zh) 2012-10-10
EP1914491A3 (fr) 2011-01-05
CN101165439A (zh) 2008-04-23
DE102006050232B9 (de) 2008-09-18
US8056356B2 (en) 2011-11-15

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