EP3099985B1 - Système de réfrigération - Google Patents

Système de réfrigération Download PDF

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Publication number
EP3099985B1
EP3099985B1 EP15701214.7A EP15701214A EP3099985B1 EP 3099985 B1 EP3099985 B1 EP 3099985B1 EP 15701214 A EP15701214 A EP 15701214A EP 3099985 B1 EP3099985 B1 EP 3099985B1
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EP
European Patent Office
Prior art keywords
mass flow
deep
cooling
intermediate pressure
additional mass
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EP15701214.7A
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German (de)
English (en)
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EP3099985A1 (fr
Inventor
Oliver Javerschek
John Craig
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.)
Bitzer Kuehlmaschinenbau GmbH and Co KG
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Bitzer Kuehlmaschinenbau GmbH and Co KG
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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/04—Desuperheaters
    • 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
    • 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
    • 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 method for operating a refrigeration system comprising a refrigerant circuit, in which a total mass flow of a refrigerant is conducted, a high-pressure-side refrigerant-cooling heat exchanger arranged in the refrigerant circuit, an expansion element arranged in the refrigerant circuit, which in the active state increases the total mass flow of the refrigerant by expansion cools and thereby generates a main mass flow of liquid refrigerant and an additional mass flow of gaseous refrigerant, which enter an intermediate pressure collector and are separated there into the main mass flow and the additional mass flow, at least one normal cooling stage, which discharges a normal cooling mass flow from the main mass flow in the intermediate pressure collector and into at least a normal refrigeration expansion unit expands to a low pressure and thereby provides refrigeration capacity for normal refrigeration, a deep-freeze intermediate pressure expansion unit, which e A frozen total mass flow taken from the main mass flow in the intermediate pressure collector expands to a frozen intermediate pressure, cools down and generates a frozen main
  • the invention is therefore based on the object of improving a method for operating a refrigeration system of the generic type in such a way that the risk of liquid being sucked in by the refrigerant compressor unit is significantly reduced.
  • this object is achieved according to the invention in that the additional mass flow expands from the intermediate pressure collector via an expansion element and is fed to the deep-frozen intermediate pressure collector and thus enters the deep-frozen intermediate pressure collector, that in the deep-frozen intermediate pressure collector a through expansion by means of the expansion element formed liquid phase in the deep-freeze main mass flow within the deep-freeze intermediate pressure collector and that a gas phase of the additional mass flow forming in the deep-freeze intermediate pressure collector is fed together with the additional deep-freeze mass flow to an additional mass flow compressor unit for compression to high pressure and thus enters the additional mass flow compressor unit.
  • a deep-frozen intermediate pressure in the deep-frozen intermediate pressure collector is in a pressure range that extends from the low pressure to the intermediate pressure.
  • the intermediate deep-freeze pressure is preferably at most 5 bar above the low pressure.
  • a particularly favorable solution provides for the intermediate deep-freeze pressure to be in the low-pressure range.
  • a separate compressor unit could be provided as an additional mass flow compressor unit, for example a speed-controlled compressor unit, with which it would be possible to regulate the intermediate deep-freeze pressure to a pressure value favorable for the operation of the refrigeration system.
  • the refrigerant compressor unit forms the additional mass flow compressor unit, so that no separate compressor unit is necessary for this, but the gas phase of the additional mass flow and the additional frozen mass flow from the frozen intermediate pressure collector can be compressed by the refrigerant compressor unit that is present anyway.
  • a particularly favorable solution provides for the gas phase of the additional mass flow to be fed together with the additional frozen mass flow from the frozen intermediate pressure collector together with the normal cooling mass flow expanded to low pressure to the refrigerant compressor unit, so that there is the possibility of connecting the deep-freezing intermediate pressure collector to the line leading the normal cooling mass flow to the refrigerant compressor unit .
  • a particularly advantageous solution provides that the additional mass flow expanded by the expansion element opens into the deep-frozen intermediate pressure collector spatially separated from a discharge line for the deep-frozen intermediate pressure collector leading away from the deep-frozen intermediate pressure collector.
  • the opening of the expanded deep-freeze additional mass flow into the deep-freeze intermediate pressure collector is placed in such a way that it enters the gas volume in the deep-freeze intermediate pressure collector.
  • the distance between the junction of the expanded additional mass flow in the deep-freeze intermediate pressure collector and the discharge line is preferably as large as possible, preferably greater than half the extent of the deep-freeze intermediate pressure collector in the direction of its maximum extent, in order to provide a sufficiently large distance for separating the liquid phase from the expanded additional mass flow to have before a gaseous phase of the expanded additional mass flow is discharged through the discharge line from the deep-freeze intermediate pressure collector.
  • a flow rate of the refrigerant in the discharge line is less than 2 m/s (meters per second), even better less than 0.5 m/s and particularly preferably less than 0.3 m/s.
  • An advantageous solution provides that the additional mass flow from the gas volume forming in the intermediate pressure collector is fed to the deep-frozen intermediate pressure collector via a discharge line and expanded to the deep-frozen intermediate pressure by the expansion element provided in the discharge line.
  • the additional mass flow expanded by the expansion element is fed directly to the gas volume in the deep-freeze intermediate pressure collector, from which the liquid phase of the expanded additional mass flow then separates.
  • the method described so far for operating a refrigeration system works less efficiently when the high pressure is to be at a high pressure level, ie in particular at all times when there is a high temperature at the heat exchanger cooling the high-pressure side refrigerant.
  • the refrigeration system has an additional mass flow removal unit, with which at least part of the additional mass flow is removed from the intermediate pressure collector, at least in certain operating modes, and is fed to a compression to high pressure without further expansion, starting from the intermediate pressure.
  • Such a refrigeration system has the advantage that it can work more efficiently at a very high pressure level of the high pressure.
  • the additional mass flow discharge unit is preferably designed in such a way that it has a heat exchanger for heating up the Has additional mass flow before compressing it to high pressure.
  • Any heat-emitting medium could flow through the heat exchanger.
  • An advantageous solution provides that the additional mass flow discharge unit feeds the discharged part of the additional mass flow to an economizer connection of refrigerant compressors of the refrigerant compressor unit, so that the same refrigerant compressors that are already used in the refrigerant compressor unit can also be used to compress the mass flow from the additional mass flow discharge unit.
  • Another advantageous solution provides that the additional mass flow discharge unit feeds the discharged part of the additional mass flow to a parallel compressor, which is provided in addition to the refrigerant compressor unit.
  • the parallel compressor then works on the basis of the intermediate pressure and compresses the part of the additional mass flow supplied to it by the additional mass flow discharge unit to high pressure.
  • the parallel compressor works in a power-controlled manner, in particular in a speed-controlled manner.
  • the intermediate pressure is regulated to a predetermined value by regulating the capacity of the parallel compressor.
  • the additional mass flow discharge unit can be connected to the intermediate pressure collector by a switching element or is separable from this.
  • the additional mass flow discharge unit can be connected to and separated from the deep-freeze intermediate pressure collector by means of a switching element for discharging the gas phase of the additional mass flow together with the additional deep-freeze mass flow.
  • This switch-on element thus makes it possible when the additional mass flow discharge unit is no longer useful for discharging part of the additional mass flow from the intermediate pressure collector can also use the additional mass flow discharge unit to discharge the gas phase of the additional mass flow together with the additional frozen mass flow from the frozen intermediate pressure collector.
  • the switching element is arranged in such a way that it can be used not only to compress not only the gas phase of the additional mass flow together with the additional frozen mass flow from the frozen intermediate pressure collector, but also, if necessary, at least part of the normal cooling mass flow expanded to low pressure.
  • the performance-controlled parallel compressor is particularly advantageous if it works in parallel with the refrigerant compressor unit.
  • the refrigeration compressor unit could theoretically include several power-controlled refrigeration compressors.
  • At least one of the refrigerant compressors of the refrigerant compressor unit is output-controlled.
  • Operation of the refrigeration system in different operating modes provides, for example, that in a first operating mode the additional mass flow discharge unit is separated from the intermediate pressure collector and that the entire additional mass flow is expanded and fed to the deep-freeze intermediate pressure collector.
  • This solution has the advantage that, with simple means and independently of the temperature in the heat exchanger cooling the refrigerant compressed to high pressure, it can be ensured that the refrigerant compressors used do not suck in any appreciable amounts of liquid.
  • Operation in the various operating modes further provides, for example, that in a second operating mode the additional mass flow discharge unit is connected to the intermediate pressure collector and discharges part of the additional mass flow and another part of the additional mass flow is fed to the deep-freeze intermediate pressure collector.
  • operation in the various operating modes provides that in a third operating mode the additional mass flow discharge unit is connected to the intermediate pressure collector and discharges the entire additional mass flow.
  • a first exemplary embodiment of a refrigeration system for carrying out a method according to the invention shown in 1 , comprises a refrigerant circuit designated as a whole with 10, in which a refrigerant compressor unit designated as a whole with 12 is arranged, which in the exemplary embodiment shown has a plurality of individual refrigerant compressors, for example three refrigerant compressors 14 1 to 14 3 , all of which work in parallel in the refrigerant compressor unit 12 .
  • Each of the refrigerant compressors 14 1 to 14 3 has a suction-side connection 16 1 to 16 3 , all the suction-side connections 16 of the individual refrigerant compressors 14 being connected to a suction connection line 18 of the refrigerant compressor unit 12 .
  • each of the refrigerant compressors 14 has a pressure-side connection 22 1 to 22 3 , all the pressure-side connections 22 of the individual refrigerant compressors 14 being connected to a pressure connection line 24 of the refrigerant compressor unit 12 .
  • All refrigerant compressors 14 thus work in parallel, but there is the possibility of varying the compressor output of the refrigerant compressor unit 12 by having individual refrigerant compressors 14 working and individual refrigerant compressors 14 not working.
  • the refrigerant compressor unit 12 thus compresses refrigerant from a suction pressure present in the suction connection line 18, which corresponds to a low pressure PN of a normal cooling stage to be described below, to a high pressure PH present in the pressure connection line 24 of the refrigerant compressor unit 12, which is, for example, in the range between 45 bar (450 N/ cm 2 ) and 100 bar (1000 N/cm 2 ).
  • the refrigerant present under high pressure PH at the pressure connection line 24 forms a total mass flow G, which flows away from the pressure connection line 24 of the refrigerant compressor unit 12, first flows through an oil separator 32 and, after the oil separator 32, flows through a high-pressure-side heat exchanger 34, through which cooling of the high-pressure compressed refrigerant takes place.
  • the cooling of the total mass flow G of the refrigerant compressed to high pressure in the high-pressure-side heat exchanger 34 liquefies it or merely cools it down to a lower temperature, with only one in the case of a supercritical cycle sensible heat change occurs.
  • CO 2 carbon dioxide
  • a subcritical cycle provides that the high-pressure-side heat exchanger 34 cools down to a temperature that corresponds to an isotherm running through the dew and boiling line or saturation curve of the refrigerant.
  • the refrigerant cooled by the heat exchanger 34 on the high-pressure side is fed to an expansion element 38 arranged in a pressure line 36, which regulates the high pressure PH in accordance with values specified by a controller 40 and which is embodied, for example, as an expansion element 38 actuated by the controller 40 and which expands the high-pressure PH stationary refrigerant of the total mass flow G expands to an intermediate pressure PZ, which corresponds to an isotherm running through the dew and boiling line or saturation curve of the refrigerant.
  • the controller 40 controls the expansion element 38 according to a temperature in the heat exchanger 34 and these predefined application limits of the refrigerant compressor 14.
  • the intermediate pressure PZ is, for example, in the range between 35 bar and 45 bar and is kept at a predetermined value in as many operating states as possible, so that the deviation from the predetermined value is a maximum of ⁇ 3 bar.
  • the expansion element 38 puts the total mass flow G of the refrigerant into a thermodynamic state in which there is a main mass flow H in the form of liquid refrigerant and an additional mass flow Z in the form of gaseous refrigerant.
  • Both mass flows H and Z are collected in an intermediate pressure collector 42, which has a reservoir for both the main mass flow H and the additional mass flow Z, and separated from one another in the intermediate pressure collector 42, with the main mass flow H being in the intermediate pressure collector 42 as a bath 44 of liquid refrigerant forms, over which a gas volume 46 of gaseous refrigerant is located, so that the bath 44 absorbs the main mass flow H and the gas volume 46 absorbs the additional mass flow Z.
  • a normal cooling mass flow N flows out of the intermediate pressure collector 42 as a partial mass flow of the main mass flow H to a normal cooling stage designated as a whole with 52, which has one or more, for example two, parallel normal cooling expansion units 54a and 54b.
  • Each of these normal cooling expansion units 54 comprises a normal cooling expansion element 56, through which the part of the normal cooling mass flow N arriving under intermediate pressure PZ is expanded to low pressure PN, with the refrigerant being cooled in a known manner by this expansion, which opens up the possibility of to take up heat in the normal cooling heat exchanger 58 following the normal cooling expansion element 56, as a result of which an enthalpy increase arises.
  • the low pressure PN is, for example, in the range between 25 bar and 30 bar and is kept as constant as possible in all operating states, i.e. within a maximum of ⁇ 3 bar of the specified value of the low pressure PN.
  • the normal cooling mass flow N expanded overall to low pressure PN is fed from the normal cooling heat exchangers 58 to a suction line 62, which in turn is connected to the suction connection line 18 of the refrigerant compressor unit 12, so that this expanded normal cooling mass flow N can be compressed again by the refrigerant compressor unit 12 to high pressure PH.
  • a frozen intermediate pressure expansion unit 72 which is also designed, for example, as an expansion element or expansion valve.
  • the deep-frozen intermediate pressure expansion unit 72 expands the deep-frozen total mass flow TG to a deep-frozen intermediate pressure PTZ, which preferably corresponds to the low pressure PN and is, for example, between 25 bar and 30 bar, so that the deep-frozen total mass flow TG consisting of liquid refrigerant is converted into a deep-frozen main mass flow TH at a temperature below the temperature of the Main mass flow lying temperature and an additional deep-freeze mass flow TZ from vaporous refrigerant arise, which are fed together to a deep-freeze intermediate pressure collector 74, wherein the deep-freeze intermediate pressure collector 74 has a reservoir for both the deep-freeze main mass flow TH and for the additional deep-freeze mass flow TZ, which collects and separates them from one another, with the deep-freeze main mass flow TH formed as a bath 76 of liquid refrigerant, while the additional deep-freeze mass flow TZ forms a gas volume 78 of gaseous refrigerant lying above the bath 76 in
  • the deep-freeze main mass flow TH is separated from the deep-freeze additional mass flow TZ.
  • the deep-freeze main mass flow TH is fed to a deep-freeze stage 82, which has one or more, for example two, parallel deep-freeze expansion units 84 that are connected in parallel, each of these deep-freeze expansion units 84 having a deep-freeze expansion element 86 which supplies part of the deep-freeze mass flow TH from the intermediate deep-freeze pressure PTZ to a deep-freeze low pressure PTN and thus cools down, the deep-freeze low pressure PTN being kept as constant as possible in all operating states, so that the deviations are a maximum of ⁇ 3 bar and are between 10 bar and 15 bar, for example.
  • the refrigerant cooled to deep-freeze low pressure PTN is then subsequently fed to a deep-freeze low-pressure side heat exchanger 88 and is able in the respective deep-freeze heat exchanger 88 to absorb heat at deep-freeze temperatures, as a result of which the enthalpy is increased.
  • the frozen main mass flow TH expanded overall in the frozen stage 82 to frozen low pressure PTN, is fed to a frozen suction line 92, which is connected to both frozen heat exchangers 88 and feeds the frozen main mass flow TH, expanded to frozen low pressure PTN, to a frozen compressor unit designated as a whole with 102, which, for example, has a plurality of frozen compressors 104 1 to 104 3 , which each have suction-side connections 106 1 to 106 3 , which are connected to a deep-freeze suction connection 108 of the deep-freeze compressor unit 102, which in turn is connected to the deep-freeze suction line 92 and receives the deep-freeze main mass flow TH expanded to deep-freeze low pressure PTN.
  • the deep-freeze compressors 104 also have pressure-side connections 112 1 to 112 3 , which in turn are connected to a deep-freeze pressure connection line 114 of the deep-freeze compressor unit 102 .
  • the deep-freeze compressor unit 102 compresses the deep-freeze main mass flow TH, which has flowed through the deep-freeze stage 82 and has been expanded to the deep-freeze low pressure PTN, in turn to the normal cool low pressure PN, with the deep-freeze mass flow TH compressed to the normal cool low pressure PN being fed via a line 116 to the suction connection line 18 of the refrigerant compressor unit 12.
  • a heat exchanger 118 can optionally also be switched on, which allows an optionally favorable cooling of the compressed deep-freeze main mass flow TH.
  • the frozen intermediate pressure collector 74 In order to discharge the additional frozen mass flow TZ, which is present in the frozen intermediate pressure collector 74 at the frozen intermediate pressure PTZ, in order to keep the frozen intermediate pressure PTZ as constant as possible, the frozen intermediate pressure collector 74 is provided with a discharge line 122, which connects the gas volume 78 in the frozen intermediate pressure collector 74 with the suction line 62. which leads from the normal cooling stage 52 to the suction connection 18 of the refrigerant compressor unit 12 .
  • the frozen intermediate pressure PTZ corresponds approximately to the normal cooling low pressure PN.
  • a discharge line 132 opens out on the one hand into the gas volume 46 of the intermediate pressure collector 42 and on the other hand into the gas volume 78 in the deep-freeze intermediate pressure collector 74, with an additional expansion element 134 in the discharge line 132 is provided, which expands the additional mass flow Z emerging from the intermediate pressure collector 42 from the intermediate pressure PZ to the deep-freeze intermediate pressure PTZ and thus from the saturated gas phase into the wet-steam region and thus causes an additional cooling of the same, so that the additional mass flow Z is further cooled while generating liquid , before entering the refrigerated intermediate pressure accumulator 74.
  • the expansion element 134 regulates the intermediate pressure PZ in the intermediate pressure collector 42 to a predetermined value.
  • the volume of the bath 44 made of liquid refrigerant in the intermediate pressure collector 42 and the volume of the bath 76 made of liquid refrigerant in the deep-frozen intermediate pressure collector 72 are adjusted via the deep-frozen intermediate-pressure expansion unit 72 such that, on the one hand, the bath 44 has a sufficiently large volume and, on the other hand, the bath 44 also has a sufficiently large volume has volume.
  • the part of the additional mass flow Z expanded by the expansion element 134 is fed to the gas volume 78 in the deep-frozen intermediate pressure collector 74 at a separation height of 300 mm to 400 mm above the design-specified maximum achievable liquid level of the bath 76 of the deep-frozen main mass flow TH in the deep-frozen intermediate pressure collector 74.
  • the discharge line 132 opens into the deep-frozen intermediate pressure collector 74 in such a way that the additional mass flow Z entering the deep-frozen intermediate pressure collector 74 is far enough away from the discharge line 122, in particular from a junction of the discharge line 122 into the deep-frozen intermediate pressure collector 74, to ensure that The additional mass flow Z cooled by the expansion element 134 in the gas volume 78 of the deep-frozen intermediate pressure collector 74 separates the entrained liquid portion formed by the cooling due to the expansion in the expansion element 134 in the deep-frozen intermediate pressure collector 74 and then the remaining gaseous additional mass flow Z in turn through the discharge line 122 into the suction line 62 entry.
  • the additional mass flow Z' flowing through the discharge line 122 is reduced by the mass of the liquid portion of the additional mass flow Z separated in the deep-freeze intermediate pressure collector 74, which is however in the range of less than 10%, so that the additional mass flow Z' corresponds approximately to the additional mass flow Z.
  • the liquid fraction of the additional mass flows flowing through the discharge line 122 is preferably less than 5 m% (mass percent), even better less than 3 m% and preferably less than 1 m% of the total mass flows passing through the discharge line 122, so that it is ensured that the refrigerant compressor 14 of the refrigerant compressor unit 10 sucks in substantially liquid-free refrigerant in all operating states.
  • the specification of the mass flows is an average value that occurs when the refrigeration circuit 10 is operated in the manner described during the respective operating periods.
  • the refrigerant compressors 14 in the second exemplary embodiment are designed in such a way that they not only have a suction-side connection 16 and a pressure-side connection 22, but also an economizer connection 21, with all economizer connections 21 1 to 21 3 having a common connection line 152 are connected.
  • each of the refrigerant compressors 14' has its own valve 154 1 to 154 3 which is used to establish a connection between the economizer connection 21 and the common connection line 152 for all refrigerant compressors 14'. can be interrupted.
  • Connecting line 152 leads to a heat exchanger 156, and from this heat exchanger 156 leads a receiving line 158 for the additional mass flow Z from the intermediate pressure collector 42 to the discharge line 132 and opens into this between the point where discharge line 132 opens into the gas volume 46 and the expansion element 134, so that at least part of the additional mass flow Z or the entire additional mass flow Z can be discharged with the intake line 158 without this part of the additional mass flow Z or this discharged entire additional mass flow Z flowing into the gas volume 78 of the deep-freeze intermediate pressure collector 74.
  • Heat exchanger 156 is also located in line 116, which leads from deep-freeze pressure connection line 114 to suction connection line 18, so that heat exchanger 156 makes it possible to heat that part of additional mass flow Z that is discharged via receiving line 158 to such an extent that it no longer contains any liquid contains before this part of the additional mass flow Z is fed via the economizer connections 21 to the individual refrigerant compressors 14 of the refrigerant compressor unit 12, which compress the sucked-in part of the additional mass flow Z from the intermediate pressure PZ to high pressure PH.
  • valves 154 also make it possible to regulate or, if necessary, completely suppress the proportion of the additional mass flow Z that is fed to the economizer connections 21, so that in this case at least a significant part, if not the entire additional mass flow Z, enters the gas volume 78 of the deep-freeze intermediate pressure collector 74 via the expansion element 134 .
  • connection line 152 with the valves 154, the heat exchanger 156 and the receiving line 158 form an additional mass flow discharge unit 160, with which at least part of the additional mass flow Z can be discharged from the intermediate pressure collector 42 without that an expansion is required, so that this part of the additional mass flow Z can be compressed from the intermediate pressure PZ to high pressure PH and the efficiency of the refrigeration system is thus improved.
  • the receiving line 158 is provided in the same way as in the second exemplary embodiment, which leads to the heat exchanger 156, and in this case a suction line 162 leads from the heat exchanger 156 to a parallel compressor 164 provided in addition to the refrigerant compressor unit 12, namely to a suction connection 166 of the same , the pressure connection 172 of which is in turn connected to the pressure connection line 24, so that by appropriate speed-controlled activation of the parallel compressor 164 there is the possibility of discharging a part of the additional mass flow Z from the intermediate pressure collector 42.
  • the elements that are identical to the first and second exemplary embodiment are provided with the same reference symbols, so that with regard to the description of the same, reference can be made in full to the explanations relating to the first and second exemplary embodiment.
  • a switching valve 182 is provided in the receiving line 158 , which allows refrigerant to be prevented from being received from the gas volume 46 of the intermediate-pressure collector 42 .
  • a controller 192 is provided, which on the one hand controls the switching valve 182 and on the other hand the parallel compressor 164, in accordance with the existing load conditions.
  • the refrigerant circuit 10 is operated in such a way that the high pressure PH is approximately 90 bar, for example.
  • the intermediate pressure PZ in the intermediate pressure collector 42 is kept at approximately 40 bar.
  • the low pressure PN is approximately 28 bar.
  • the parallel compressor 164 works with the switching valve 182 open, so that the entire additional mass flow Z is fed via the intake line 158, the heat exchanger 156 and the suction line 162 to the suction port 166 of the parallel compressor 164, which then compresses the additional mass flow to the high pressure PH, the at the pressure connection 172 of the same.
  • the controller 192 closes the switching valve 182 and the parallel compressor 164 operates in parallel with the refrigerant compressor unit 12, for which purpose refrigerant is drawn in from the suction line 62 into the receiving line 158 via the branch line 184 and the check valve 186, flows through the heat exchanger 156 and is supplied to the suction connection 166 of the parallel compressor 164 via the suction line 162 .
  • the additional mass flow Z flows via the expansion element 134, which is arranged in the discharge line 132, from the gas volume 46 in the intermediate pressure collector 42 into the gas volume 78 of the deep-freeze intermediate pressure collector 74, wherein, as already mentioned in connection with the The first exemplary embodiment is described in detail, in which liquid produced by expansion of the additional mass flow Z is separated in the gas volume 78 in the deep-frozen intermediate pressure collector 74 in the deep-frozen intermediate pressure collector 74 .
  • the parallel compressor 164 sucks in refrigerant from the suction line 62 at low pressure PN and compresses the refrigerant to the high pressure PH, which, however, is only in the range of, for example, 45 bar in this case.
  • a three-way valve 202 is provided in the receiving line 158 instead of the switching valve 182, which is able to either connect the branch line 184 to the receiving line 158 and to interrupt the connection between the receiving line 158 and the discharge line 132 or to Establish connection between the receiving line 158 and the discharge line 132 and to interrupt the connection between the branch line 184 and the receiving line 158.
  • This three-way valve 202 can also be controlled by a controller 192, which also controls the parallel compressor 164, in the same way as was described in connection with the fourth exemplary embodiment, with the three-way valve 202 now being controlled instead of the switching valve 182 being controlled.
  • a three-way valve 204 is provided instead of the three-way valve 202, which is connected on the one hand to the suction connection line 18 and on the other hand to the suction line 162 and is able to connect one of these lines 18 or 162 to the suction connection 166 of the parallel compressor 164.
  • Three-way valve 204 thus makes it possible to supply either part of the additional mass flow Z or the entire additional mass flow Z to parallel compressor 164 via suction line 162, heat exchanger 156 and intake line 158, or to supply expanded refrigerant from normal cooling mass flow N and to parallel compressor 164 via suction connection line 18 fed to the deep-freeze main mass flow TH for compression.
  • the three-way valve 204 can also be controlled by the controller 192, which also actuates the parallel compressor 164, in the same way as was described in connection with the fourth exemplary embodiment, with the three-way valve 204 being actuated instead of the switching valve 182 being actuated in order to to realize operating conditions.
  • a refrigeration system 10 according to the exemplary embodiments described above can be - as in 7 shown - use in particular for the energy-optimized operation of a building 210, in particular a food market, wherein 210 facilities are provided in an interior 212 of the building.
  • a cooling device 214 is provided, for example, in which refrigerated goods or objects, for example food, are kept at a normal cooling temperature, i.e. a temperature in the range of usually 0° C. to 5° C., the cooling of this cooling device takes place through the normal cooling stage 52 of the refrigeration system 10 according to the invention.
  • a deep-freeze device 216 is provided in the interior 212, in which deep-frozen goods or objects, for example frozen goods, are kept at deep-frozen temperature, for example at a temperature in the range from -30°C to -10°C.
  • the deep-freeze device 216 is cooled by the deep-freeze stage 82 of the refrigeration system 10 according to the invention.
  • all other components of the refrigeration system 10 according to the invention are preferably arranged in a room 218 which can either be part of the building 210 or can be arranged next to the building 210.
  • the heat exchanger 34 arranged outside of the space 218 in turn draws in ambient air 222, for example, in order to use this ambient air 222 to cool the refrigerant which is under high pressure PH.
  • a heat exchanger 224 which is assigned to building 210 and is used to transfer heat to the interior 212, is connected in parallel with the high-pressure-side heat exchanger 34, which is arranged outside of building 210 and is used for heat exchange with the ambient air 222 of the building 210 to be heated inside air 226, for which purpose the heat exchanger 224 can draw in ambient air 222 of the building 210 and/or inside air of the building 210 for heating, as required.
  • the heat produced on the high-pressure side of the refrigeration systems 10 according to the invention can thus be used in an energy-efficient manner for heating the building, particularly at times when the outside temperature of the building 210 is below the room temperature to be aimed for in the interior 212 of the same.
  • a cooling heat exchanger 232 is provided in the building 210, in particular in the interior 212 thereof, which serves to cool the interior 212 of the building 210 when the outside temperatures are too high or when the sun is shining.
  • the cooling heat exchanger 232 is fed, for example, by a parallel circuit 242 assigned to the intermediate-pressure collector 42, which takes in liquid refrigerant from the bath 44 of the liquid refrigerant in the intermediate-pressure collector 42 via a supply line 244 at a temperature corresponding to the intermediate pressure PZ in the intermediate-pressure collector 42, and evaporates it in an evaporator 246 and feeds it back to the gas volume 46 of the intermediate pressure collector 42 via a discharge line 248 .
  • the evaporator 246 is preferably designed as a flooded evaporator, which is cooled by liquid refrigerant entering it due to gravity, this refrigerant then evaporating in this evaporator 246 .
  • a control element 252 is preferably also provided for controlling or regulating the parallel circuit 242, which in the simplest case can be a valve or, in the somewhat more complex case, a power-controlled pump for liquid refrigerant.
  • Evaporator 246, cools an exchanger circuit 262, in which, for example, a heat exchanger medium such as air, brine, or water circulates, which then in turn flows through cooling heat exchanger 232 in building 210 and can be used there to cool an air flow 264, with this air flow 264 in the In the simplest case, an air flow from circulated interior air 226 of the building 210 can be.
  • a heat exchanger medium such as air, brine, or water circulates
  • Temperatures between 5° C. and 0° C. are typically present in the intermediate pressure collector 42, so that the cooling heat exchanger 232 can be operated at these temperatures and the air flow 264 which flows through the cooling heat exchanger 232 can thus be cooled in a simple manner.
  • such cooling causes an increased additional mass flow Z, which occurs in the intermediate pressure collector 42 and must be introduced either via the discharge line 132 and the expansion element 134 into the deep-freeze intermediate pressure collector 74 and then, after flowing through it, must be compressed by the refrigerant compressor unit 12 or via the Additional mass flow discharge unit 160 must be discharged.
  • more heat is generated on the high-pressure side, which can either be dissipated by the heat exchanger 34 to the surroundings of the building 210 or, under favorable conditions, can be used by the heat exchanger 224 to heat the building 210, for example after dehumidification of outside air, which can be supplied to the inside air 226 of the building 210 as supply air.
  • a parallel circuit 272 is also assigned to the deep-freeze intermediate pressure collector 74, which has a supply line 274 which receives liquid refrigerant from the bath 76 in the deep-freeze intermediate pressure collector 74, which feeds this refrigerant to an evaporator 276, which in turn evaporates the liquid refrigerant and, via a discharge line 278, in turn to the gas volume 78 in the deep-freeze intermediate pressure collector 74.
  • the evaporator 276 is embodied, for example, as a flooded evaporator, so that the liquid refrigerant enters it due to gravity, is evaporated in the evaporator 276 and is then fed back in gaseous form via the supply line 274 to the gas volume 78 in the deep-freeze intermediate pressure collector 74.
  • a control element 282 is also provided in the supply line 274, which can be designed either in the form of a switching valve or possibly also in the form of a power-controlled pump.
  • the evaporator 276 is also coupled to a circuit 292 in which an external heat exchanger 294 is arranged, which is arranged outside the building 210 and also outside the room 218 .
  • this heat exchanger 294 it is possible, for example, to absorb heat at low ambient temperatures and to feed this heat to the refrigerant circuit 12 in order to have more heat available at the heat exchanger 224 for cooling the refrigerant compressed to high pressure PH and thus, for example, in winter at low outside temperatures to be able to heat the interior 212 of the building 210 .
  • the refrigeration system 10 not only serves to operate the cooling device 214 and the deep-freezing device 216 in the building 210 , but also to heat the interior 212 of the building via the heat exchanger 224 at the same time.
  • the refrigerant is at a temperature between -12° C. and -5° C., so that at outside temperatures that are higher than the saturated temperature in the deep-frozen intermediate pressure collector 74, heat can always be absorbed via the heat exchanger 294 , which in turn can then be released into the interior 212 of the building 210 via the heat exchanger 224 .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (17)

  1. Procédé pour faire fonctionner une installation frigorifique comprenant un circuit de réfrigération (10), dans lequel est guidé un débit massique total (G) d'un frigorigène, un échangeur de chaleur (34) disposé dans le circuit de réfrigération (10), refroidissant le frigorigène côté haute pression, un organe de détente (38) disposé dans le circuit de réfrigération (10), qui dans l'état actif refroidit le débit massique total (G) du frigorigène par détente et ce faisant produit un débit massique principal (H) de frigorigène liquide et un débit massique supplémentaire (Z) de frigorigène gazeux, qui entrent dans un collecteur de pression intermédiaire (42) et sont séparés dans celui-ci en le débit massique principal (H) et le débit massique supplémentaire (Z), au moins un étage de refroidissement normal (52), lequel évacue un débit massique de refroidissement normal (N) du débit massique principal (H) dans le collecteur de pression intermédiaire (42) et le détend à une basse pression (PN) dans au moins une unité de détente de refroidissement normal (54) et ce faisant fournit une puissance frigorifique pour un refroidissement normal, une unité de détente à pression intermédiaire de congélation (72), laquelle détend un débit massique total de congélation (TG) prélevé du débit massique principal (H) dans le collecteur de pression intermédiaire (42) à une pression intermédiaire de congélation (PTZ), ce faisant refroidit et produit un débit massique principal de congélation (TH) de frigorigène liquide ainsi qu'un débit massique supplémentaire de congélation (TZ) de frigorigène gazeux et amène ceux-ci à un collecteur de pression intermédiaire de congélation (74), dans lequel une séparation du débit massique principal de congélation (TH) du débit massique supplémentaire de congélation (TZ) s'effectue, un étage de congélation (82) évacuant le débit massique principal de congélation (TH) du collecteur de pression intermédiaire de congélation (74), lequel présente au moins une unité de détente de congélation (84) et par détente du débit massique principal de congélation (TH) à une basse pression de congélation (PTN) fournit une puissance frigorifique pour la congélation, une unité de compresseur de congélation (102), laquelle comprime le débit massique principal de congélation (TH) détendu à une basse pression de congélation (PTN) et l'amène à une unité de compresseur de frigorigène (12) comprimant le débit massique de refroidissement normal (N) d'une basse pression (PN) à une haute pression (PH) également pour la compression à une haute pression (PH),
    caractérisé en ce que le débit massique supplémentaire (Z) provenant du collecteur de pression intermédiaire (42) se détend par l'intermédiaire d'un organe de détente (134) et entre dans le collecteur de pression intermédiaire de congélation (74), que dans le collecteur de pression intermédiaire de congélation (74), une phase liquide formée par détente au moyen de l'organe de détente (134) se sépare en le débit massique principal de congélation (TH) à l'intérieur du collecteur de pression intermédiaire de congélation (74) et qu'une phase gazeuse du débit massique supplémentaire (Z) se réalisant dans le collecteur de pression intermédiaire de congélation (74) entre conjointement avec le débit massique supplémentaire de congélation (TZ) dans une unité de compresseur de débit massique supplémentaire pour la compression à une haute pression (PH).
  2. Procédé selon la revendication 1, caractérisé en ce que la phase gazeuse du débit massique supplémentaire (Z) est amenée conjointement avec le débit massique supplémentaire de congélation (TZ) à partir du collecteur de pression intermédiaire de congélation (74) sans détente à l'unité de compresseur de débit massique supplémentaire, qu'en particulier une pression intermédiaire de congélation (PTZ) dans le collecteur de pression intermédiaire de congélation (74) se situe dans une plage de pressions qui va de la basse pression (PN) à la pression intermédiaire (PZ) et qu'en particulier la pression intermédiaire de congélation (PTZ) se situe dans la plage de la basse pression (N).
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que l'unité de compresseur de frigorigène (12) forme une unité de compresseur de débit massique supplémentaire.
  4. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que la phase gazeuse du débit massique supplémentaire (Z) est amenée conjointement avec le débit massique supplémentaire de congélation (TZ) à partir du collecteur de pression intermédiaire de congélation (74) conjointement avec le débit massique de refroidissement normal (N) détendu à une basse pression (PN) à l'unité de compresseur de frigorigène (12).
  5. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que le débit massique supplémentaire détendu par l'organe de détente (134) débouche dans le collecteur de pression intermédiaire de congélation (74) de manière séparée dans l'espace d'une conduite d'évacuation (122) pour le collecteur de pression intermédiaire de congélation (74) s'écartant du collecteur de pression intermédiaire de congélation (74).
  6. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce que le débit massique supplémentaire (Z) est amené au collecteur de pression intermédiaire de congélation (74) à partir du volume de gaz (46) se formant dans le collecteur de pression intermédiaire (42) par l'intermédiaire d'une conduite d'évacuation (132) et détendu par l'organe de détente (134) prévu dans la conduite d'évacuation (132) à la pression intermédiaire de congélation (PTZ) et qu'en particulier le débit massique supplémentaire (Z) détendu par l'organe de détente (134) est amené à un volume de gaz (78) dans le collecteur de pression intermédiaire de congélation (74).
  7. Procédé selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une unité d'évacuation de débit massique supplémentaire (160) est prévue, avec laquelle au moins dans des modes de fonctionnement définis au moins une partie du débit massique supplémentaire (Z) est prélevée du collecteur de pression intermédiaire (42) et amenée sans autre détente à partir de la pression intermédiaire (PZ) à une compression à une haute pression (PH).
  8. Procédé selon la revendication 7, caractérisé en ce que l'unité d'évacuation de débit massique supplémentaire (160) présente un échangeur de chaleur (156) pour le chauffage du débit massique supplémentaire (Z) avant la compression de celui-ci à une haute pression (PH).
  9. Procédé selon la revendication 8, caractérisé en ce que l'échangeur de chaleur (156) est traversé par le débit massique principal de congélation (TH) comprimé par l'unité de compresseur de congélation (102).
  10. Procédé selon l'une quelconque des revendications 7 à 9, caractérisé en ce que l'unité d'évacuation de débit massique supplémentaire (160) amène la partie évacuée du débit massique supplémentaire (Z) à un raccord d'économiseur (21) de compresseurs de frigorigène (14') de l'unité de compresseur de frigorigène (12').
  11. Procédé selon l'une quelconque des revendications 7 à 9, caractérisé en ce que l'unité d'évacuation de débit massique supplémentaire (160) amène la partie évacuée du débit massique supplémentaire (Z) à un compresseur parallèle (164), qui est prévu en plus de l'unité de compresseur de frigorigène (12).
  12. Procédé selon la revendication 11, caractérisé en ce que le compresseur parallèle (164) fonctionne de manière régulée en puissance, et qu'en particulier une régulation de la pression intermédiaire (PZ) à une valeur prédéfinie s'effectue par régulation de puissance du compresseur parallèle (164).
  13. Procédé selon l'une quelconque des revendications 7 à 12, caractérisé en ce que l'unité d'évacuation de débit massique supplémentaire (160) peut être reliée au collecteur de pression intermédiaire (42) ou séparée de celui-ci par un organe de commutation (182, 202, 204).
  14. Procédé selon l'une quelconque des revendications 7 à 13, caractérisé en ce que l'unité d'évacuation de débit massique supplémentaire (160) peut être reliée au collecteur de pression intermédiaire de congélation (74) pour l'évacuation de la phase gazeuse du débit massique supplémentaire (Z) conjointement avec le débit massique supplémentaire de congélation (TZ) et séparée de celui-ci par un organe de commutation (186, 202, 204).
  15. Procédé selon l'une quelconque des revendications 7 à 14, caractérisé en ce que dans un premier mode de fonctionnement l'unité d'évacuation de débit massique supplémentaire (160) est séparée du collecteur de pression intermédiaire (42) et que tout le débit massique supplémentaire (Z) est détendu et amené au collecteur de pression intermédiaire de congélation (74).
  16. Procédé selon l'une quelconque des revendications 7 à 15, caractérisé en ce que dans un deuxième mode de fonctionnement l'unité d'évacuation de débit massique supplémentaire (160) est reliée au collecteur de pression intermédiaire (42) et évacue une partie du débit massique supplémentaire (Z) et une autre partie du débit massique supplémentaire (Z) est amenée au collecteur de pression intermédiaire de congélation (74).
  17. Procédé selon l'une quelconque des revendications 7 à 16, caractérisé en ce que dans un troisième mode de fonctionnement l'unité d'évacuation de débit massique supplémentaire (160) est reliée au collecteur de pression intermédiaire (42) et évacue tout le débit massique supplémentaire (Z).
EP15701214.7A 2014-01-27 2015-01-26 Système de réfrigération Active EP3099985B1 (fr)

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WO2017157924A2 (fr) * 2016-03-15 2017-09-21 Hsl Energy Holding Aps Appareil du type pompe à chaleur
EP3446048A1 (fr) * 2016-04-18 2019-02-27 Johnson Controls Technology Company Système condenseur évaporateur doté de sous-refroidisseur, pour systèmes frigorifiques
US10808966B2 (en) 2017-03-02 2020-10-20 Heatcraft Refrigeration Products Llc Cooling system with parallel compression
US20210239366A1 (en) * 2020-02-05 2021-08-05 Carrier Corporation Refrigerant vapor compression system with multiple flash tanks
CN115077114A (zh) * 2022-06-08 2022-09-20 松下冷机***（大连）有限公司 Co2跨临界船用碳捕集制冷机组

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DE19920734A1 (de) * 1999-05-05 2000-11-09 Linde Ag Kälteanlage und Verfahren zum Betreiben einer Kälteanlage
DE102006050232B9 (de) 2006-10-17 2008-09-18 Bitzer Kühlmaschinenbau Gmbh Kälteanlage
WO2010003590A2 (fr) * 2008-07-07 2010-01-14 Carrier Corporation Circuit de réfrigération
CN103282729B (zh) * 2011-01-14 2015-09-30 开利公司 制冷***和用于操作制冷***的方法
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DE102014100917A1 (de) 2015-07-30

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