EP2153138B1 - Kühlsystem und verfahren zur steuerung von kompressoranlagen in solch einem kühlsystem - Google Patents

Kühlsystem und verfahren zur steuerung von kompressoranlagen in solch einem kühlsystem Download PDF

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Publication number
EP2153138B1
EP2153138B1 EP07725094A EP07725094A EP2153138B1 EP 2153138 B1 EP2153138 B1 EP 2153138B1 EP 07725094 A EP07725094 A EP 07725094A EP 07725094 A EP07725094 A EP 07725094A EP 2153138 B1 EP2153138 B1 EP 2153138B1
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EP
European Patent Office
Prior art keywords
cold
heat exchanger
compressors
refrigerant
carrier
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EP07725094A
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English (en)
French (fr)
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EP2153138A1 (de
Inventor
Heinz Gassen
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Carrier Corp
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Carrier Corp
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Publication of EP2153138A1 publication Critical patent/EP2153138A1/de
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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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2400/06—Several compression cycles 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
    • F25B2400/07—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
    • F25B2600/00—Control issues
    • F25B2600/01—Timing
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/027—Compressor control by controlling pressure
    • F25B2600/0272—Compressor control by controlling pressure the suction 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21172—Temperatures of an evaporator of the fluid cooled by the evaporator at the inlet
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21171—Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173—Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet

Definitions

  • the invention relates to a refrigerating system having at least one refrigerant circuit and a cold carrier circuit and to a method for controlling compressor sets in such a refrigerating system.
  • Document EP 1 698 843 A discloses both a refrigeration system and a control method according to the preamble of claims 1 and 15, respectively.
  • the refrigeration is effected indirectly by providing a refrigerant circuit and a cold carrier circuit coupled to the refrigerant circuit by means of a heat exchanger as an evaporator.
  • a cold carrier like a glycol water mixture or a solution with organic salts transfers the cold to the cold consumers.
  • Exemplary embodiments of the invention include a refrigerating system comprising at least one refrigerant circuit having a set of compressors, each of said compressors being operable at at least one compressor power stage, a control unit for the set of compressors, a liquefier, an evaporator also forming a heat exchanger, refrigerant conduits connecting the set of compressors, the liquefier, and the evaporator/heat exchanger, and circulating a refrigerant; a pressure sensor arranged between the evaporator/heat exchanger and the set of compressors sensing the refrigerant pressure; a cold carrier circuit having a cold carrier pump, a cold consumer region, where cold is consumed, cold carrier conduits connecting the cold carrier pump, the evaporator/heat exchanger and the cold consumer region and circulating a cold carrier which is refrigerated in the evaporator/heat exchanger, and a temperature sensor sensing the cold carrier temperature; wherein the control unit for the set of compressors is configured such that
  • FIG. 1 For exemplary embodiments of the invention, include a method for controlling compressor sets in a refrigerating system having at least one refrigerant circuit and a cold carrier circuit, the refrigerant circuit having a set of compressors, each of said compressors being operable at at least one compressor power stage, a control unit for the set of compressors, a liquefier, an evaporator also forming a heat exchanger, refrigerant conduits connecting the set of compressors, the liquefier and the evaporator/heat exchanger, and circulating a refrigerant, and a pressure sensor arranged between the evaporator/heat exchanger and the set of compressors sensing the refrigerant pressure; the cold carrier circuit having a cold carrier pump, a cold consumer region, where cold is consumed, cold carrier conduits connecting the cold carrier pump, the evaporator/heat exchanger and the cold consumer region and circulating a cold carrier, which is refrigerated in the evaporator/heat exchanger, and
  • Figure 1 shows a schematic of a first refrigerating system 2 having a refrigerant circuit 4, a heat carrier circuit 18 and a cold carrier circuit 22.
  • the refrigerating circuit 4 comprises a set of three compressors 6, 8, 10, each of these three compressors 6, 8, 10 being operable at two compressor power stages.
  • the refrigerant circuit 4 also comprises a control unit (not shown) for the set of compressors 6, 8, 10, a liquefier 12, an evaporator being formed as a heat exchanger 14 and a pressure sensor 16 arranged between the heat exchanger 14 and the set of compressors 6, 8, 10, that senses the sucking pressure of the refrigerant before the set of compressors 6, 8, 10.
  • Refrigerant conduits connect the set of compressors 6, 8, 10, the liquefier 12 and the heat exchanger 14 and circulate a refrigerant, e.g. Freon.
  • the liquefier 12 is formed as a second heat exchanger, and the heat carrier circuit 18 comprises a heat carrier pump (not shown), at least one recooler 20, and heat carrier conduits connecting the heat carrier pump, the liquefier 12 and the at least one recooler 20 and circulating a liquid heat carrier.
  • the heat carrier circuit 18 comprises a heat carrier pump (not shown), at least one recooler 20, and heat carrier conduits connecting the heat carrier pump, the liquefier 12 and the at least one recooler 20 and circulating a liquid heat carrier.
  • three blowers are provided as recoolers 20.
  • the cold carrier circuit 22 comprises a cold carrier pump (not shown), a cold consumer region comprising two cold consumers 24 connected in parallel and consuming cold, a first temperature sensor 26 arranged at the return line from the cold consumer region 24 to the heat exchanger 14 at the inlet thereof, and a second temperature sensor 28 arranged at the supply line from the heat exchanger 14 to the cold consumer region 24 at the outlet of the heat exchanger 14.
  • Cold carrier conduits connect the cold carrier pump, the heat exchanger 14, and the cold consumer region 24 and circulate a cold carrier, particularly a glycol water mixture or a solution with an organic salt and a brine, respectively.
  • the liquefier 12 and the evaporator 14 can be formed as any kind of heat exchangers.
  • the liquefier 12 is a plate heat exchanger and the evaporator 14 is a finned tube heat exchanger.
  • Figure 2 shows a schematic of a second refrigerating system 30 having a refrigerant circuit 4, a heat carrier circuit 18, and a cold carrier circuit 22.
  • the second refrigerating system 30 substantially corresponds to the first refrigerating system 2, wherein the heat carrier pumps 34 in the supply line from the liquefier 12 to the recoolers 20 of the heat carrier circuit 18 and the cold carrier pumps 36 in the return line from the cold consumer region 24 to the heat exchanger 14 of the cold carrier circuit 22 are depicted, wherein a throttle valve 32 is shown in the refrigerant circuit 4 between the liquefier 12 and the heat exchanger 14, and wherein the set of compressors 6, 8, 10 comprises eight instead of three compressors (four of which are shown in Figure 2 ) and wherein the recoolers comprise eight instead of three blowers (four of which are shown in Figure 2 ).
  • Figure 3 shows a schematic of a third refrigerating system 38 having a first refrigerant circuit 40, a second refrigerant circuit 52, a common heat carrier circuit 64, and a common cold carrier circuit 70.
  • the third refrigerating system 38 corresponds to the second refrigerating system 30 of Figure 2 , wherein the cold consumer region is not depicted and wherein the refrigerant circuit 4 has been replaced by two refrigerant circuits 40 and 52, each of which having a set of two compressors 42, 54, a liquefier being formed as a heat exchanger 44, 56, a throttle valve 46, 58, an evaporator being formed as a heat exchanger 48, 60, and a pressure sensor 50, 62, respectively.
  • the supply lines for the cold consumer region of the cold carrier circuit 70 from the heat exchanger 48 of the first refrigerant circuit 40 and from the heat exchanger 60 of the second refrigerant circuit 52 join to form a common supply line.
  • the common return line from the cold consumer region of the cold carrier circuit 70 divides into a first return line for the heat exchanger 48 of the first refrigerant circuit 40 and into a second return line for the heat exchanger 60 of the second refrigerant circuit 52.
  • first refrigerant circuit 40 and the second refrigerant circuit 52 are connected in parallel to the heat carrier circuit 64.
  • the supply lines for the recooler 68 of the heat carrier circuit 64 from the heat exchanger 44 of the first refrigerant circuit 40 and from the heat exchanger 56 of the second refrigerant circuit 52 join before the heat carrier pumps 66 to form a common supply line.
  • the return line from the recooler 68 of the heat carrier circuit 64 divides into a first return line for the first heat exchanger 44 and into a second return line for the second heat exchanger 56.
  • Figure 4 shows a graph depicting the temporal course of the pressure p sensed by the pressure sensor 16 of the first refrigerating system 2.
  • a threshold or emergency shutdown value p off is drawn as a horizontal dashed line. If the refrigerant pressure falls below p off , the control unit for the set of compressors 6, 8, 10 switches off all compressors 6, 8, 10 at the same time.
  • a critical value p min - ⁇ p 2 is drawn as a horizontal dashed line.
  • the control unit progressively switches off running compressor power stages in order to avoid the refrigerant pressure to fall below the emergency shutdown value p off .
  • the progressive switching off of the compressor power stages is effected by first switching off the compressor power stages of such compressors 6, 8, 10 having had the longest running time. For this purpose, the control unit monitors the running time of the compressors 6, 8, 10 and their compressor power stages.
  • p min - ⁇ p2 a further critical value p min is drawn as a continuous horizontal line. If the refrigerant pressure is above the critical value p min and increases, the control unit switches on additional compressor power stages.
  • p min + ⁇ p 1 a further critical value p min + ⁇ p 1 is drawn as a horizontal dashed line. If the refrigerant pressure p is below this critical value p min + ⁇ p 1 and decreases, the control unit for the set of compressors 6, 8, 10 prevents turning on additional compressor power stages.
  • the refrigerant used is a HFKW refrigerant, type 404A.
  • the first compressor 6 runs at the highest power stage, wherein the second compressor 8 and the third compressor 10 run at the middle (50%) power stage.
  • the control unit prevents turning on additional compressor power stages, since the refrigerant pressure is below the critical value p min + ⁇ p 1 and decreases.
  • the refrigerant pressure p is above the critical value p min and increases, which means that the criterion of switching on additional compressor power stages is fulfilled, and consequently the control unit switches on the second compressor power stage of the second compressor 8 which now runs at a performance of 100%.
  • the refrigerant pressure p increases again, and at t 6 it exceeds the critical value p min again, which means that additional power stages, namely the compressor power stages of the first compressor 6, and the second compressor power stages of the second compressor 8 and the third compressor 10 are allowed to be switched on by the control unit again in order to produce more cold for the cold consumers 24.
  • additional power stages namely the compressor power stages of the first compressor 6, and the second compressor power stages of the second compressor 8 and the third compressor 10 are allowed to be switched on by the control unit again in order to produce more cold for the cold consumers 24.
  • this switching on of additional compressor power stages is also done progressively in order to avoid an abrupt decline of the refrigerant pressure below the emergency shutdown value p off .
  • control according to the invention the decline of the refrigerant pressure p below the emergency shutdown value p off is reliably avoided, and therefore an improved and more uniform refrigeration of the cold consumers is effected, and the switching frequency of the compressors 6, 8, 10 is considerably reduced leading to a longer life cycle of the set of compressors 6, 8, 10.
  • This control can also be performed with refrigerating systems having a larger number of compressors or compressor power stages like the second refrigerating system 30 or with refrigerating systems having more than one refrigerant circuits like the third refrigerating system 38. In the latter case a separate control is carried out for each refrigerant circuit.
  • Exemplary embodiments as described above allow for a more stable and reliable operation of the refrigerating system, in particular of its set of compressors which results in a more effective and more uniform refrigeration of the cold consumers and which avoids unnecessary switching of the compressors, thus enabling a better protection thereof from damage and a longer life cycle of the compressors used.
  • the refrigerating system according to the invention is controlled based on the condition that the cold carrier temperature in the cold consumers is too high and there exists a constant need of switching on further compressor power stages.
  • the control is effected by a control based on the temperature measured in the cold carrier circuit and by an underlying control based on the pressure, particularly the suction pressure in the refrigerant circuit.
  • a control based on the temperature measured in the cold carrier circuit and by an underlying control based on the pressure, particularly the suction pressure in the refrigerant circuit.
  • a stable operation in the refrigerant circuit is effected and the refrigerant pressure is prevented to fall below the emergency shutdown value p off .
  • a stable operating point or operating range is obtained making available the maximum possible refrigerating performance using the maximum possible compressors.
  • the switching frequency of the compressors is reduced and consequently the operation of the refrigerating system is made more uniform and quieter.
  • the control unit of the invention operates to maintain the operation of the maximum amount of compressor power stages, while at the same time preventing the refrigerant pressure falling below the emergency shutdown value p off .
  • the set of compressors can comprise an arbitrary number of compressors, particularly one to eight compressors.
  • the number of compressor and compressor power stages is dependent on the cold performance delivered by the refrigerating system.
  • the pressure sensor should particularly be arranged at a point within the refrigerant circuit before the refrigerant is compressed, in particular between the heat exchanger and the set of compressors.
  • the control unit for the set of compressors is configured such that, in case of the temperature sensor sensing a too high cold carrier temperature, it progressively switches off running compressor power stages, if the refrigerant pressure falls below a second critical value p min - ⁇ p 2 .
  • the refrigerant suction pressure is prevented from falling below the emergency shutdown value p off .
  • control unit When the control unit is configured such that it monitors the running time of the compressors and, particularly, of its compressor power stages, and when the control unit first switches off the compressor stages of such compressors having had the longest running time, a uniformly distributed operation of the compressors is ensured and wearing down of single compressors is avoided.
  • control unit for the set of compressors is configured such that, in case of the temperature sensor sensing a too high cold carrier temperature, it switches on additional compressor power stages, if the refrigerant pressure is above a third critical value p min and increases, the operation of the maximum number of compressor power stages is made possible while minimizing the risk of an unwanted emergency shutdown.
  • a low pressure switch can be provided for switching off all compressors if the refrigerant pressure falls below an emergency shutdown value p off .
  • the low pressure switch can be part of the control unit itself or can be formed separately therefrom.
  • the refrigerant circuit can further comprise a throttle valve.
  • the temperature sensor can be arranged at the heat exchanger, particularly at its inlet or its outlet dependent on the specifications needed. Alternatively the temperature sensor can be arranged near or at the cold consumers.
  • An even enhanced monitoring of the temperatures of the cold carrier can be effected when a first temperature sensor is arranged at the return line from the cold consumer region to the heat exchanger of the cold carrier circuit at the inlet of the heat exchanger, and when a second temperature sensor is arranged at the supply line from the heat exchanger to the cold consumer region of the cold carrier circuit at the outlet of the heat exchanger.
  • the heat exchangers transferring cold from the refrigerant circuit to the cold carrier circuit can be of any commercial kind, particularly a tube heat exchanger, and more particularly a finned tube heat exchanger.
  • the consumer region can comprise at least one cold consumer, particularly a plurality of cold consumers formed as heat exchangers transferring cold.
  • two or more cold consumers can be connected in parallel in the cold consumer region.
  • the cold carrier pump When the cold carrier pump is arranged in the return line from the cold consumer region to the heat exchanger of the cold carrier circuit the influence of the loss heat of the cold carrier pump on the cold carrier can be minimized.
  • the cold carrier is a glycol water mixture or a sole.
  • two refrigerant circuits are connected in parallel to the cold carrier circuit, wherein the supply line for the cold consumer region of the cold carrier circuit from the heat exchangers of the two refrigerant circuits join to form a common supply line, and wherein the common return line from the cold consumer region of the cold carrier circuits divide into a first return line for the first heat exchanger and into a second return line for the second heat exchanger.
  • the liquefier of the refrigerant circuit of the refrigerating system can be formed as conventional liquefier.
  • the liquefier can be formed as a second heat exchanger and a heat carrier circuit can be provided, which comprises a heat carrier pump, at least one recooler, and heat carrier conduits connecting the heat carrier pump, the second heat exchanger and the at least one recooler and circulating a liquid heat carrier.
  • a heat carrier circuit in combination with a second heat exchanger the efficiency of the refrigerating system can be further improved.
  • the heat carrier pump When the heat carrier pump is arranged before the at least one recooler, the influence of its loss heat onto the liquid heat carrier is minimized.
  • two refrigerant circuits can be connected in parallel to the heat carrier circuit, wherein the supply lines for the at least one recooler of the heat carrier circuit from the heat exchangers of the two refrigerant circuits join to form a common supply line, and wherein the return line from the at least one recooler of the heat carrier circuit divides into a first return line for the first heat exchanger and into a second return line for the second heat exchanger.
  • the refrigerating system can be used basically for composite refrigerating systems having several compressors for indirect cooling.
  • the features and embodiments of the refrigerating system as described above can also be realized as corresponding method steps in the method for controlling compressor sets in a refrigerating system having at least one refrigerant circuit and a cold carrier circuit.
  • Such features and embodiments bring about the same advantages as described above. In order to avoid redundancy, such features, embodiments, and advantages are not repeated here.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Air Conditioning Control Device (AREA)

Claims (15)

  1. Kühlsystem (2) aufweisend
    mindestens einen Kältemittelkreislauf (4) mit einem Satz von Verdichtern (6, 8, 10), wobei jeder der Verdichter (6, 8, 10) an mindestens einer Verdichter-Leistungsstufe betreibbar ist, eine Steuereinheit für den Satz von Verdichtern (6, 8, 10), einen Verflüssiger (12), einen Verdampfer, der auch einen Wärmetauscher (14) bildet, Kältemittelleitungen, die den Satz von Verdichtern (6, 8, 10), den Verflüssiger (12) und den Wärmetauscher (14) verbinden und ein Kältemittel zirkulieren;
    einen Kälteträgerkreislauf (22) mit einer Kälteträgerpumpe (36), einer Kälteverbraucherregion (24), Kälteträgerleitungen, die die Kälteträgerpumpe (36), den Wärmetauscher (14) und die Kälteverbraucherregion (24) verbinden und einen Kälteträger zirkulieren, der in dem Wärmetauscher (14) gekühlt wird, und einem Temperatursensor (26, 28), der die Kälteträgertemperatur erfasst;
    dadurch gekennzeichnet, dass ein Drucksensor (16) zwischen dem Wärmetauscher (14) und dem Satz von Verdichtern (6, 8, 10) angeordnet ist und den Kältemitteldruck erfasst, und dass die Steuereinheit für den Satz von Verdichtern (6, 8, 10) derart konfiguriert ist, dass dann, wenn der Temperatursensor (26, 28) eine zu hohe Kälteträgertemperatur erfasst, dieser das Einschalten von zusätzlichen Verdichter-Leistungsstufen verhindert, wenn der Kältemitteldruck unter einem ersten kritischen Wert liegt und geringer wird, und mindestens eine laufende Verdichter-Leistungsstufe ausschaltet, wenn der Kältemitteldruck unter einen zweiten kritischen Wert fällt.
  2. Kühlsystem (2) nach Anspruch 1,
    wobei die Steuereinheit für den Satz von Verdichtern (6, 8, 10) derart konfiguriert ist, dass dann, wenn der Temperatursensor (26, 28) eine zu hohe Kälteträgertemperatur erfasst, dieser laufende Verdichter-Leistungsstufen nacheinander ausschaltet, wenn der Kältemitteldruck unter den zweiten kritischen Wert fällt,
    wobei die Steuereinheit vorzugsweise derart konfiguriert ist, dass sie die Laufzeit der Verdichter (6, 8, 10) überwacht und zuerst die Verdichter-Leistungsstufen von solchen Verdichtern (6, 8, 10) ausschaltet, die die längste Laufzeit hatten.
  3. Kühlsystem (2) nach einem der Ansprüche 1 oder 2,
    wobei die Steuereinheit für den Satz von Verdichtern (6, 8, 10) derart konfiguriert ist, dass dann, wenn der Temperatursensor (26, 28) eine zu hohe Kälteträgertemperatur erfasst, dieser zusätzliche Verdichter-Leistungsstufen einschaltet, wenn der Kältemitteldruck über einem dritten kritischen Wert pmin liegt und ansteigt.
  4. Kühlsystem (2) nach einem der Ansprüche 1 bis 3,
    wobei ein Niedrigdruck-Schalter vorgesehen ist und der Niedrigdruck-Schalter alle Verdichter (6, 8, 10) ausschaltet, wenn der Kältemitteldruck unter einen Schwellenwert poff fällt,
    wobei der Niedrigdruck-Schalter vorzugsweise Teil der Steuereinheit für den Satz von Verdichtern (6, 8, 10) ist.
  5. Kühlsystem (2) nach einem der Ansprüche 1 bis 4,
    wobei der Kältemittelkreislauf (4) ferner ein Drosselventil (32) aufweist.
  6. Kühlsystem (2) nach einem der Ansprüche 1 bis 5,
    wobei der Temperatursensor (26, 28) an dem Wärmetauscher (14), insbesondere an dessen Einlass oder dessen Auslass, angeordnet ist.
  7. Kühlsystem (2) nach einem der Ansprüche 1 bis 6,
    wobei ein erster Temperatursensor (26) an der Rücklaufleitung von der Kälteverbraucherregion (24) zu dem Wärmetauscher (14) des Kälteträgerkreislaufs (22) an dem Einlass des Wärmetauschers (14) angeordnet ist und ein zweiter Temperatursensor (28) an der Zuführleitung von dem Wärmetauscher (14) zu der Kälteverbraucherregion (24) des Kälteträgerkreislaufs (22) an dem Auslass des Wärmetauschers (14) angeordnet ist.
  8. Kühlsystem (2) nach einem der Ansprüche 1 bis 7,
    wobei es sich bei dem Wärmetauscher (14) um einen Rohr-Wärmetauscher handelt, insbesondere einen Rippenrohr-Wärmetauscher.
  9. Kühlsystem (2) nach einem der Ansprüche 1 bis 8,
    wobei die Kälteverbraucherregion eine Mehrzahl von als Wärmetauschern (24) ausgebildeten Kälteverbrauchern aufweist und wobei vorzugsweise zwei oder mehr Kälteverbraucher (24) in der Kälteverbraucherregion parallel geschaltet sind.
  10. Kühlsystem (2) nach einem der Ansprüche 1 bis 9,
    wobei die Kälteträgerpumpe (36) in der Rücklaufleitung von der Kälteverbraucherregion (24) zu dem Wärmetauscher (24) des Kälteträgerkreislaufs (22) angeordnet ist.
  11. Kühlsystem (2) nach einem der Ansprüche 1 bis 10,
    wobei es sich bei dem Kälteträger um ein Glykol-Wasser-Gemisch oder eine Sole handelt.
  12. Kühlsystem (38) nach einem der Ansprüche 1 bis 11,
    wobei zwei Kältemittelkreisläufe (40, 52) dem Kälteträgerkreislauf (70) parallel geschaltet sind,
    wobei die Zuführleitungen für die Kälteverbraucherregion des Kälteträgerkreislaufs (70) von den Wärmetauschern (48, 60) der beiden Kältemittelkreisläufe (40, 52) unter Bildung einer gemeinsamen Zuführleitung verbunden sind; und
    wobei die gemeinsame Rücklaufleitung von der Kälteverbraucherregion des Kälteträgerkreislaufs (70) sich in eine erste Rücklaufleitung für den ersten Wärmetauscher (48) und in eine zweite Rücklaufleitung für den zweiten Wärmetauscher (60) teilt.
  13. Kühlsystem (38) nach einem der Ansprüche 1 bis 12,
    wobei der Verflüssiger (12) als zweiter Wärmetauscher ausgebildet ist; und wobei ein Wärmeträgerkreislauf (18) vorgesehen ist und der Wärmeträgerkreislauf (18) eine Wärmeträgerpumpe (34), mindestens einen Rückkühler (20) und Wärmeträgerleitungen aufweist, die die Wärmeträgerpumpe (34), den zweiten Wärmetauscher (12) und den mindestens einen Rückkühler (20) verbinden und einen flüssigen Wärmeträger zirkulieren,
    wobei die Wärmeträgerpumpe (34) vorzugsweise vor dem mindestens einen Rückkühler (20) angeordnet ist.
  14. Kühlsystem (38) nach einem der Ansprüche 12 oder 13,
    wobei die beiden Kältemittelkreisläufe (40, 52) dem Wärmeträgerkreislauf (64) parallel geschaltet sind,
    wobei die Zuführleitungen für den mindestens einen Rückkühler (68) des Wärmeträgerkreislaufs (64) von den Wärmetauschern (44, 56) der beiden Kältemittelkreisläufe (40, 52) unter Bildung einer gemeinsamen Zuführleitung verbunden sind; und
    wobei die Rücklaufleitung von dem mindestens einen Rückkühler (68) des Wärmeträgerkreislaufs (64) sich in eine erste Rücklaufleitung für den ersten Wärmetauscher (44) und in eine zweite Rücklaufleitung für den zweiten Wärmetauscher (56) teilt.
  15. Verfahren zum Steuern von Verdichtersätzen (6, 8, 10) in einem Kühlsystem, das mindestens einen Kältemittelkreislauf (4) und einen Kälteträgerkreislauf (22) aufweist,
    wobei der Kältemittelkreislauf (4) aufweist: einen Satz von Verdichtern (6, 8, 10), wobei jeder der Verdichter (6, 8, 10) an mindestens einer Verdichter-Leistungsstufe betreibbar ist, eine Steuereinheit für den Satz von Verdichtern (6, 8, 10), einen Verflüssiger (12), einen Verdampfer, der auch einen Wärmetauscher (14) bildet, Kältemittelleitungen, die den Satz von Verdichtern (6, 8, 10), den Verflüssiger (12) und den Wärmetauscher (14) verbinden und ein Kältemittel zirkulieren;
    wobei der Kälteträgerkreislauf (22) eine Kälteträgerpumpe (36), eine Kälteverbraucherregion (24), Kälteträgerleitungen, die die Kälteträgerpumpe (36), den Wärmetauscher (14) und die Kälterverbraucherregion (24) verbinden und einen Kälteträger zirkulieren, der in dem Wärmetauscher (14) gekühlt wird, und einen Temperatursensor (26, 28) aufweist, der die Kälteträgertemperatur erfasst;
    dadurch gekennzeichnet, dass ein Drucksensor (16) zwischen dem Wärmetauscher (14) und dem Satz von Verdichtern (6, 8, 10), angeordnet ist und den Kältemitteldruck erfasst und das Verfahren folgende Schritte aufweist:
    Betreiben des mindestens einen Kältemittelkreislaufs (4) und des Kälteträgerkreislaufs (22);
    Erfassen der Kälteträgertemperatur und der Kältemitteltemperatur; und
    wenn die Kälteträgertemperatur zu hoch ist, Verhindern eines Einschaltens von zusätzlichen Verdichter-Leistungsstufen, wenn der Kältemitteldruck unter einem ersten kritischen Wert liegt und geringer wird, und Ausschalten von mindestens einer laufenden Verdichter-Leistungsstufe, wenn der Kältemitteldruck unter einen zweiten kritischen Wert fällt.
EP07725094A 2007-05-10 2007-05-10 Kühlsystem und verfahren zur steuerung von kompressoranlagen in solch einem kühlsystem Active EP2153138B1 (de)

Priority Applications (1)

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PL07725094T PL2153138T3 (pl) 2007-05-10 2007-05-10 Układ chłodniczy i sposób sterowania zespołami sprężarek w takim układzie chłodniczym

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2007/004174 WO2008138367A1 (en) 2007-05-10 2007-05-10 Refrigerating system and method for controlling compressor sets in such a refrigerating system

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EP2153138A1 EP2153138A1 (de) 2010-02-17
EP2153138B1 true EP2153138B1 (de) 2011-01-05

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ITBO20120152A1 (it) * 2012-03-21 2013-09-22 Irsap Spa Gruppo frigorifero
EP2890940B1 (de) 2012-08-31 2018-01-10 Danfoss A/S Verfahren zur steuerung eines kühlersystems
CN105982673B (zh) 2015-01-30 2020-09-29 西门子(深圳)磁共振有限公司 磁共振成像设备的冷却方法与磁共振成像设备
JP6399979B2 (ja) * 2015-07-31 2018-10-03 三菱重工サーマルシステムズ株式会社 冷凍機システム

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US3675441A (en) * 1970-11-19 1972-07-11 Clark Equipment Co Two stage refrigeration plant having a plurality of first stage refrigeration systems
DE4010770C1 (de) * 1990-04-04 1991-11-21 Danfoss A/S, Nordborg, Dk
US5460008A (en) * 1993-12-22 1995-10-24 Novar Electronics Corporation Method of refrigeration case synchronization for compressor optimization
US6434960B1 (en) * 2001-07-02 2002-08-20 Carrier Corporation Variable speed drive chiller system
JP4727142B2 (ja) * 2003-12-18 2011-07-20 三菱重工業株式会社 ターボ冷凍機およびその圧縮機ならびにその制御方法
US7415838B2 (en) * 2005-02-26 2008-08-26 Lg Electronics Inc Second-refrigerant pump driving type air conditioner
CN101142455B (zh) * 2005-03-18 2010-12-08 丹佛斯公司 用于控制制冷系统的方法

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DE602007011830D1 (de) 2011-02-17
ATE494516T1 (de) 2011-01-15
EP2153138A1 (de) 2010-02-17
WO2008138367A1 (en) 2008-11-20

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