EP2590878B1 - Installation frigorifique pour refroidir un conteneur - Google Patents

Installation frigorifique pour refroidir un conteneur Download PDF

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Publication number
EP2590878B1
EP2590878B1 EP11722022.8A EP11722022A EP2590878B1 EP 2590878 B1 EP2590878 B1 EP 2590878B1 EP 11722022 A EP11722022 A EP 11722022A EP 2590878 B1 EP2590878 B1 EP 2590878B1
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EP
European Patent Office
Prior art keywords
compressor
cooling
refrigeration system
pressure
container
Prior art date
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EP11722022.8A
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German (de)
English (en)
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EP2590878A2 (fr
Inventor
Wolfgang Sandkoetter
Dieter Mosemann
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GEA Refrigeration Germany GmbH
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GEA Refrigeration Germany GmbH
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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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0401—Refrigeration circuit bypassing means for the compressor
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/003—Transport containers

Definitions

  • the invention relates to a refrigeration system for cooling the interior of a refrigerated container, which can be used universally, for example, on ships, or a truck, a small van, a refrigerated wagon, which is part of a cold chain for transporting refrigerated and frozen goods.
  • the invention thus relates to a refrigeration system for refrigerated transport.
  • container interior, container or refrigerated container are used for these cold rooms in the following text. Accordingly, the term container cooling is used to represent these mobile cold rooms to be cooled.
  • Cooling air flow and the basic structure of refrigerated containers for ships are in DE 202007008764 described.
  • the interior of a refrigerated container is surrounded by thermally insulated side walls, roof and floor, the interior floor generally being designed with air distribution devices, for example longitudinal ribs, which form channels for guiding cold air.
  • the document US 2006/225445 A1 shows a refrigeration system according to the preamble of claim 1.
  • Refrigerated containers must also be built in such a way that they can be transported using the respective specific transport systems on the road, at sea or by rail (truck-trailer reefers, marine reefers or trail reefers).
  • the useful temperature of such a container interior depends on the cargo to be cooled.
  • Such refrigerated containers must be able to carry out cooling or freezing processes for the cargo and then keep them at a predetermined level, the cold storage temperature.
  • the cooling capacity during the cooling or freezing process and during refrigerated transport storage for the same container size differs very significantly depending on the product properties and the usable temperature level in the container interior.
  • different climatic ambient conditions will generally be present on the outer wall of the container, which are regionally caused by passing through different climatic zones or only by the daily course of the temperature, so that the temperature level of the heat sink changes and thus the condensation temperature of the refrigeration system Container cooling.
  • the refrigeration system for container cooling must be able to be operated efficiently and be variable in such a way that the refrigeration capacity and the useful temperature let vary and can be operated economically and environmentally friendly at the different condensation temperatures without restriction.
  • the refrigerated container with its refrigeration system must be able to be operated in a stack of containers; its operating regime must be individually adaptable to the goods to be cooled.
  • one-stage or two-stage refrigeration systems are used in refrigeration systems for container cooling, which have compressors, condensers, expansion devices and evaporators.
  • the container is cooled directly by circulating refrigerant, which absorbs heat from the room to be cooled on the evaporator.
  • the refrigerant is compressed in one or more stages in one or more compressors to a higher pressure and thus to a condensation temperature above the heat sink (container environment) and then cooled by releasing heat to the environment in a gas cooler or in a condenser and then back in one or more stages to the pressure in the evaporator, which creates liquid refrigerant and flash vapor at the lower evaporation temperature of the refrigerant.
  • This arrangement is each carried out only in one stage or only in several stages, so that this refrigeration system, either in the one-stage or in the two-stage version, is not suitable for the desired application range of a refrigerated container.
  • the patent US 4730464 describes a cooling system for cooling a room with air with a compressor and a turbocharger.
  • the variability of the refrigeration system is very limited in terms of refrigeration capacity and evaporation temperature.
  • the patent DE 3620847 discloses an absorption refrigeration system which is supplemented by a heat pipe solar collector.
  • the lack of stackability of such a refrigerated container is disadvantageous for ship use.
  • Container cooling systems with a storage effect without their own refrigeration, with so-called indirect cooling, are also known.
  • the coolant is cooled away from the container and then introduced into cavities on the container.
  • Slurry ice also known as binary ice, cools the wall of the container.
  • the cooling temperature is defined by the ice, which consists of water and additives, and therefore not very much variable. It is not possible to cool an individual container at a different temperature and the cooling time is limited.
  • DE 9110982U1 discloses a container cooling and the channel system required for this by means of cooled water, which is provided by a cold water production system without heat exchangers on the refrigerated container coming into contact with fluorinated hydrocarbons.
  • the container is disadvantageously not self-sufficient.
  • EP0664426 the wall of the container is provided with tubular heat transfer surfaces. Through which a heat transfer fluid with phase change is passed. The cooling process is very slow, so that no cooling can be achieved.
  • the aim and object of the present invention is to provide a refrigeration system for universal cooling of the interior of a container, the usable temperature of which can be adapted within wide limits to the requirements of the goods to be refrigerated, so that cooling or freezing processes and storage of the goods at an individually predetermined temperature level possible are.
  • Another object of the invention is a refrigeration system for cooling the interior of a container, the usable temperature level and the refrigeration capacity thereof can be adapted during the cooling or freezing process and during refrigerated transport storage.
  • Another object of the invention is that the refrigeration system can be operated in a container stack without restrictions during container transport in a wide variety of climatic conditions.
  • Another object of the invention is that the refrigeration system for the container cooling is so variable that the usable temperature and cooling capacity can be adjusted as required and can be operated economically and in an environmentally friendly manner at the different condensation temperatures.
  • the object of the present invention is achieved by a refrigeration system with the features of independent claim 1. Further possible configurations of the invention are specified in the subclaims.
  • the refrigeration system according to the invention has at least two speed-controlled compressors, an n gas cooler, at least one throttle point, at least one internal heat exchanger or an intermediate-pressure liquid separator, an evaporator and controllable valve devices with opening and closing functions, which relate the relative arrangement of the compressors to one another and thus Change the circulation of the refrigerant in the refrigeration system by opening and closing it.
  • a first controllable valve device is arranged on a first compressor as a controllable bypass between the suction and pressure side
  • a second controllable valve device is arranged on a second compressor as a controllable bypass between the suction and pressure side and is a third controllable valve device between the pressure side of the first and suction side of the second compressor.
  • the communicating connection of the first controllable valve device opens on the pressure side of the first compressor after the third controllable valve device (downstream) and the communicating connection of the second controllable valve device branches off on the suction side of the second compressor before the third controllable valve device (upstream ).
  • the compressors can be operated either in parallel, i.e. at the same suction pressure and at the same back pressure, or one after the other, whereby one compressor as the first compression stage (LP or low pressure compressor) and the second compressor as the second Compression stage works at a higher pressure level (HP or high pressure compressor).
  • the usable temperature, cooling capacity and pressure ratio of the compressors can be adapted to requirements within wide limits.
  • the refrigeration is realized in one stage, since the usable temperature is still above freezing.
  • one of the two compressors is used alone to maintain the useful temperature or both compressors are operated in parallel for lowering the temperature from the introduction temperature to a useful temperature.
  • the first and the second controllable valve device are opened and the third controllable valve device is closed. If both compressors work in parallel, they work at the same pressure levels on their suction and pressure side. This operation is referred to here as operating mode NK.
  • TK operating mode For container transport of frozen goods, i.e. at useful temperatures well below freezing, refrigeration is carried out in two stages.
  • the first and the second controllable valve device are closed and the third controllable valve device is opened. This operation is referred to here as the TK operating mode.
  • the suction pressure of the first compressor which forms the first compression stage and is referred to as the low-pressure compressor or LP compressor
  • the back pressure of the LP compressor is roughly the suction pressure of the second compressor, which is the second compression stage forms uhd
  • Both compressors work at different pressure levels on their suction and pressure sides.
  • the back pressure of the HP compressor is the highest pressure in the refrigeration system. Its pressure level corresponds directly to the condensation temperature at pressures that are lower than the critical pressure of the refrigerant used in the refrigeration circuit of the refrigeration system, or the pressure is regulated at pressures above the critical pressure of the refrigerant used as a function of the gas cooler outlet temperature.
  • the high-pressure refrigerant in the internal heat exchanger is cooled by a partial refrigerant flow that is expanded to the pressure level downstream of the LP compressor before it is expanded to the suction pressure of the LP compressor.
  • the partial refrigerant flow evaporates by absorbing heat from the high-pressure refrigerant.
  • This vaporous partial refrigerant stream emerging from the internal heat exchanger is fed to the low-pressure compressor on the pressure side. It is then pumped into the gas cooler by the HP compressor at the highest pressure level.
  • the pressure after the LP compressor determines the degree of cooling of the high-pressure refrigerant. It is based on the relation of the volume flows of LP and HP compressors and can be adjusted by speed control of both compressors in relation to the most economical mode of operation.
  • the operating modes NK and TK can advantageously be combined when storing uncooled goods in order to reduce the cooling rate due to very high cooling capacity to accelerate to a certain temperature.
  • the operating mode NK is first implemented until a predetermined temperature is reached in the refrigerated container.
  • the controllable valve devices are opened or closed as described above for the NK operating mode. Both compressors work at the same pressure level on their suction and pressure side.
  • the system then switches to TK mode, which changes the pressure levels of both compressors, reduces the cooling capacity and increases the efficiency of the cooling process.
  • the controllable valve devices are opened or closed as described above for the TK operating mode. This combination of the two operating modes NK and TK is referred to here as the "cooling-down" mode
  • the three controllable valve devices are opened or closed according to the NK operating mode, although only one of the two compressors is started up.
  • the operating mode NK is retained until the intake pressure has reached a specified target size. Only then are the three controllable valve devices opened or closed in accordance with the TK operating mode, and the second compressor is started up as an LP compressor. Now both compressors work at different pressure levels.
  • the natural refrigerant CO 2 can advantageously be used in the refrigeration cycle, the direct greenhouse potential of which has the value 1 and the heat of vaporization per cubic meter of vapor volume sucked in is approximately ten times greater than that of R134a.
  • compressors and pipe cross sections can be dimensioned very small.
  • the refrigeration system for mobile refrigerated containers can be designed to be very compact and space-saving. Internal heat exchangers or intermediate pressure liquid separators are arranged as described in the exemplary embodiment, so that the known advantages of a CO 2 refrigeration system for economical operation are realized.
  • the arrangement of the compressors according to the invention can be combined with known arrangements of further plant components. These are plant designs with an intercooler, intermediate pressure liquid separator, economizer connection on the compressor or intermediate pressure feed between the compressors.
  • Fig. 1 shows in very simplified form a known single-stage refrigeration cycle process with the refrigerant R134a shown in a section of a pressure-enthalpy diagram (lg p, h diagram) with the four circuit components of a refrigeration system.
  • Fig. 2 the arrangement of the compressors in operating mode NK is shown according to the invention.
  • the compressors work here in a refrigeration system with a liquid subcooler.
  • these compressors have a second connection, an economizer connection, via which fluid can be fed into the working chambers if the pressure is sufficiently high. This allows multi-stage refrigeration system operation.
  • Fig. 3 the arrangement of the compressors in operating mode TK is shown according to the invention, which corresponds to the two-stage arrangement according to the invention.
  • the refrigeration system has an intermediate pressure liquid separator.
  • Fig. 4 the arrangement of the compressors in operating mode TK according to the invention is shown in a refrigeration system with an internal heat exchanger.
  • Fig. 5 shows the single-stage refrigeration cycle process for the NK operating mode with a small temperature difference between heat sink and usable temperature (both compressors work in one stage in parallel operation).
  • Fig. 6 shows the two-stage refrigeration cycle process for the TK mode with a large temperature difference between the heat sink and the useful temperature (one compressor is LP and one compressor is HP).
  • Fig. 7 shows an arrangement according to the invention with a controller, one of the two possible operating modes (operating mode NK) is shown.
  • the compressor 1 (type piston compressor, scroll compressor or rotary piston compressor) raises the pressure from the evaporation pressure to the condensation pressure, which is determined by the temperature of the heat sink and by the refrigerant.
  • the refrigerant is liquefied in the heat exchanger 2 and then expanded into the evaporator 4 at the throttle point 3. This creates flash vapor and liquid.
  • the liquid evaporates by absorbing heat from the interior of the container and thus cools the interior of the container.
  • Fig. 2 shows a refrigeration system with its components which, according to the invention, allow alternate one and two-stage operation of the refrigeration system for container cooling, that is to say can be operated either in the NK or TK operating mode.
  • the NK operating mode is highlighted by thick lines.
  • evaporators 4 In addition to the heat exchanger 2, which works as a condenser or gas cooler depending on the temperature level in relation to the critical temperature of the refrigerant, evaporators 4, compressors 11 and 21, which are operated at a higher or lower speed depending on the power requirement or the operating condition, are a first controllable bypass 13 and a second controllable bypass 23 as well as the first controllable valve device 12, the second controllable valve device 22 and the third controllable valve device 30.
  • the first controllable valve device 12 is arranged on the first compressor 11 as a controllable bypass 13 between its suction and pressure side
  • the second controllable valve device 22 is arranged on the second compressor 21 as a controllable bypass 23 between its suction and pressure side
  • is a third controllable valve device 30 is arranged between the pressure side of the first compressor 11 and the suction side of the second compressor 21.
  • the communicating connection of the first controllable bypass 13 opens on the pressure side of the first compressor 11 after the third controllable valve device 30 (downstream) and the communicating connection of the second controllable bypass 23 branches off on the suction side of the second compressor 21 before the third controllable valve device 30 ( upstream).
  • the compressors 11, 21 can optionally be operated in parallel, that is to say with the same suction pressure and the same back pressure, or in succession, whereby the first compressor 11 as the first compression stage (ND - or low pressure compressor) and the second compressor 21 works as a second compression stage at a higher pressure level (HP or high pressure compressor).
  • controllable valve devices 12 and 22 are open and controllable valve device 30 is closed.
  • NK which is referred to, the two compressors 11 and 21 are operated in parallel. Both compressors work with the same suction pressure and the same back pressure with one-stage compression.
  • the example relates to the use of scroll compressors with an intermediate pressure connection, a so-called economizer connection.
  • Both compressors are of the same type and size with the same application limits. They are shown here in the NK operating mode and are therefore operated with an intermediate pressure feed in single-stage compression, so that the refrigerant is cooled in the inner heat exchanger 50 after leaving the heat exchanger 2 before it is expanded in the first throttle point 52.
  • the cooling is implemented by a partial refrigerant flow which is expanded in the throttle point 51 to the intermediate pressure level. This increases the efficiency of the refrigeration system even with single-stage compressor operation. Necessary valve devices in front of the economizer connections of the two compressors 11 and 21 are not shown in the figure.
  • compressors are operated in the same refrigeration system for another container application for the transport of frozen goods in the TK operating mode.
  • Figure 3 shows a refrigeration system with its components which, according to the invention, allow alternate one and two-stage operation of the refrigeration system for container cooling, that is to say can be operated either in the NK or TK operating mode.
  • the TK operating mode for container transport of frozen goods is highlighted by thick lines.
  • the refrigeration is implemented in two stages.
  • the first controllable valve device 12 and the second controllable valve device 22 are closed and the third controllable valve device 30 is opened.
  • the suction pressure of the first compressor 11 is roughly approximate to the evaporation pressure, and its back pressure is roughly approximate the suction pressure of the second compressor 21. Both compressors operate at different pressure levels on their suction and pressure sides.
  • the back pressure of the compressor 21 is the highest pressure in the refrigeration system. Its pressure level corresponds directly to the condensation temperature at pressures that are lower than the critical pressure of the refrigerant used in the refrigeration system of the refrigeration system, or it is regulated at pressures above the critical pressure of the refrigerant used as a function of the gas cooler outlet temperature.
  • the refrigeration system in Figure 3 shows an intermediate pressure liquid separator 60, which enables a two-stage expansion at the throttling points 61 and 62. Liquid and flash vapor after the first expansion stage are fed in between the compressors 11 and 21 at intermediate pressure, the desired value of which is aimed at by changing the speed of the compressor 21. This increases the efficiency of refrigeration.
  • Figure 4 shows another refrigeration system with its components, which, according to the invention, enables alternate one and two-stage operation for container cooling, that is to say can be operated either in the NK or TK operating mode.
  • the TK operating mode is highlighted by thick lines.
  • the refrigeration system according to Figure 4 shows after the heat exchanger 2, which works depending on the temperature level in relation to the critical temperature of the refrigerant as a condenser or gas cooler, the inner heat exchanger 50, in which the refrigerant is cooled to an intermediate temperature before it is expanded at the throttle point 52.
  • the inner heat exchanger 50 in which the refrigerant is cooled to an intermediate temperature before it is expanded at the throttle point 52.
  • a partial refrigerant flow at the throttle point 51 is expanded to an intermediate pressure, the setpoint of which is regulated by the speed of the compressor 21.
  • the efficiency of refrigeration increases.
  • Fig. 5 shows the single-stage refrigeration cycle process in a pressure-enthalpy diagram for the refrigerant CO 2 in the NK operating mode at a heat sink temperature lower than 32 ° C and a useful temperature higher than 0 ° C.
  • This representation corresponds to the operation of the compressors in operating mode NK. Compression along line 72, heat removal with subsequent liquefaction of the CO 2 along line 73, throttle relaxation along line 74 and evaporation by heat absorption from the interior of the container along line 71 at 0 ° C.
  • the useful temperature of, for example, 12 ° C for banana transport could thus be achieved.
  • Line 76 illustrates the critical temperature isotherm for CO 2 .
  • Fig. 6 shows the two-stage refrigeration cycle according to Figure 3 in a pressure-enthalpy diagram for the refrigerant CO 2 in the TK operating mode at a heat sink temperature greater than 32 ° C and a useful temperature greater than - 32 ° C.
  • This representation corresponds to the operation of the compressors in operating mode TK. Compression along line 72.1 in compressor 11 and compression along line 72.2 in compressor 21, heat extraction in heat exchanger 2 along line 73.1, first stage throttle relaxation along line 74.1 to the temperature level of 25 ° C. with an intermediate cooling effect along line 73.2 and second stage throttle relaxation along line 74.2, evaporation by heat absorption the container interior along line 71 at -30 ° C. This would enable the usable temperature of, for example, -22 ° C for frozen meat to be achieved.
  • Line 76 illustrates the critical temperature isotherm for CO 2 .
  • Fig. 7 shows an arrangement according to the invention with control 80 and the most important control lines for controlling the shut-off valve devices 12, 22, 30 and for speed control of the drive motors 86, 88 for the two compressors 11, 21 and the points for measuring the temperature in the container interior at the temperature Measuring point 92 and for measuring the ambient temperature at temperature measuring point 94; as well as for measuring the pressures at a pressure measuring point 81 before the compressors and a pressure measuring point 97 after the two compressors and a pressure measuring point 96 after the controllable valve device, which in operating mode NK is equal to the suction pressure of the second compressor during this pressure in the TK operating mode there is an intermediate pressure between the first and the second compressor.
  • the above-mentioned measured variables are the input variable at the control 80.
  • the interior temperature at the temperature measuring point 92 is determined from the container 91 as a singular variable or as an average value from a plurality of measuring points (not shown) and is the input variable at the input 93 of the control 80.
  • the decision about the operating mode NK or TK is made by an algorithm in the control which evaluates the temperature in the container interior at the temperature measuring point 92 and the temperature for cooling air at the temperature measuring point 94, the signal of which reaches the control via measuring line 95.
  • the operating mode NK is shown, in which the two compressors 11 and 21 are operated in parallel.
  • the controllable valve devices 12 and 22, the signals of which are output by the controller 80, are opened via the control lines 83 and 84, while the controllable valve device 30 receives no signal from the controller 80 via control line 85 and remains closed when de-energized.
  • the speed of the two drive motors 86, 88 of the first and second compressors 11, 22 changes the control 80 via the control lines 87 for the first compressor and 89 for the second compressor depending on a target / actual comparison of the pressure at the pressure measuring point 81 , which is fed into the controller at input 82, and a setpoint value preset in controller 80.
  • the controller can also regulate the inside temperature of the container using a target / actual comparison using a second algorithm.
  • the refrigeration system is controlled so that the operating modes NK and TK can be changed during operation. This is particularly advantageous when storing uncooled goods in order to shorten the cooling time due to very high cooling capacity up to a certain temperature and to maintain the quality of the product to be cooled.
  • the operating mode NK is first implemented until a target temperature in the refrigerated container is reached.
  • the controllable valve devices 12, 22, 30 are opened or closed as described above for the NK operating mode.
  • the compressors 11, 21 operate at the same pressure levels on their suction and pressure sides.
  • the mode of operation TK is changed, as a result of which the pressure levels of the compressors 11, 21 change, the cooling capacity drops and the efficiency of the cooling generation increases.
  • the controllable valve devices 12, 22, 30 are opened or closed for the TK operating mode.
  • the controlled variable for the first compressor is the pressure at the pressure measuring point 81, as described above for the NK operating mode.
  • the speed of the second compressor is increased or decreased by the controller 80 so that the pressure at the pressure measuring point 96 with a calculated pressure from the current operating conditions at the two pressure measuring points according to the relationship "square root of the product pressure at the pressure Measuring point 81 and pressure at the pressure measuring point 97 "largely coincide.
  • the combination of the two operating modes NK and TK can be operated as rapid cooling immediately after storage in the container, referred to as "cooling-down" mode.
  • This cooling mode starts with the operating mode NK until a specified setpoint is reached at the pressure measuring point and then switches over to the operating mode TK.
  • the algorithm of the control 80 advantageously also starts both compressors of the refrigeration system with the NK operating mode for deep-freeze storage without rapid cooling and switches over to the TK operating mode as previously described.
  • the operating mode NK is maintained until a set intake pressure is reached. Only then are the controllable valve devices 12, 22, 30 opened or closed in accordance with the TK operating mode, and the compressors 11, 21 operate at different pressure levels.
  • the The useful temperature in the interior of a container can be adapted to the requirements of the refrigerated goods within wide limits, so that both cooling processes and refrigerated and freezer storage are possible at an individually specified temperature level.
  • Operating mode and usable temperature level within the cold store of the container are selected as required during refrigerated transport storage and after changing the refrigerated goods so that the refrigerated container can be used efficiently.

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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)

Claims (8)

  1. Installation frigorifique pour refroidir l'intérieur d'un conteneur frigorifique par diminution de la température à une température utile et évacuation de la chaleur vers un dissipateur thermique, comportant un premier (11) et un deuxième compresseur (21) à vitesse de rotation régulée, un refroidisseur de gaz (2), au moins un point d'étranglement (52), au moins un échangeur de chaleur intérieur (50) ou un séparateur de liquide à pression intermédiaire (60), un évaporateur (4) et des dispositifs de soupape commandables (12, 22, 30), le premier compresseur (11) présentant une première conduite de dérivation (13) qui établit une liaison d'écoulement de son côté pression vers son côté aspiration, dans laquelle est disposé un premier dispositif de soupape commandable (12) avec des fonctions d'ouverture et de fermeture, le deuxième compresseur présentant une deuxième conduite de dérivation (23) qui établit une liaison d'écoulement de son côté pression vers son côté aspiration, dans laquelle est disposé un deuxième dispositif de soupape commandable (22) avec des fonctions d'ouverture et de fermeture, un troisième dispositif de soupape commandable (30) avec des fonctions d'ouverture et de fermeture étant disposé dans une liaison d'écoulement entre le côté pression du premier compresseur (11) et le côté aspiration du deuxième compresseur (21), des moyens étant prévus pour activer lesdits dispositifs de soupape et une commande étant prévue, qui présente au moins des entrées pour la température utile et la température ambiante et des sorties pour activer lesdits dispositifs de soupape et pour modifier séparément la vitesse de rotation des deux compresseurs (11, 21), et la commande comportant des algorithmes pour l'activation différente des trois dispositifs de soupape (12, 22, 30) pour différents modes de fonctionnement de l'installation frigorifique et pour la modification de la vitesse de rotation du premier et du deuxième compresseur en fonction de la température utile et de la température ambiante,
    caractérisée en ce que
    la liaison de communication de la première conduite de dérivation (13) bifurque du côté pression du premier compresseur (11) après le troisième dispositif de soupape commandable (30) (en aval de ce dernier) et la liaison de communication de la deuxième conduite de dérivation (23) bifurque du côté aspiration du deuxième compresseur (21) avant le troisième dispositif de soupape réglable (30) (en amont de ce dernier).
  2. Installation frigorifique pour refroidir l'intérieur d'un conteneur frigorifique pour un fonctionnement à un étage, appelé mode de fonctionnement NK, selon la revendication 1, dans laquelle la commande est configurée de telle sorte que la combinaison des positions d'ouverture et de fermeture est telle que les dispositifs de soupape dans la première et dans la deuxième conduite de dérivation commandable sont ouverts et que le troisième dispositif de soupape commandable est fermé.
  3. Installation frigorifique pour refroidir l'intérieur d'un conteneur frigorifique pour un fonctionnement à deux étages, appelé mode de fonctionnement TK, selon la revendication 1, dans laquelle la commande est configurée de telle sorte que la combinaison des positions d'ouverture et de fermeture des trois dispositifs de soupape est telle que les dispositifs de soupape dans la première et dans la deuxième conduite de dérivation commandable sont fermés et que le troisième dispositif de soupape commandable est ouvert.
  4. Installation frigorifique pour refroidir l'intérieur d'un conteneur frigorifique selon les revendications 1 à 3, dans laquelle le premier et le deuxième compresseur sont du même type et de la même taille.
  5. Installation frigorifique pour refroidir l'intérieur d'un conteneur frigorifique selon les revendications 1 à 4, dans laquelle le réfrigérant CO2 est présent dans le circuit de réfrigération.
  6. Installation frigorifique pour refroidir l'intérieur d'un conteneur frigorifique selon les revendications 1 à 2 et 5, dans laquelle la commande est configurée de telle sorte que les caractéristiques des modes de fonctionnement NK et TK successifs forment une séquence lors du démarrage de l'installation frigorifique et pour un refroidissement rapide.
  7. Installation frigorifique pour refroidir l'intérieur d'un conteneur frigorifique selon les revendications 3 et 6, dans laquelle la commande est configurée de telle sorte qu'en mode de fonctionnement TK, la pression entre le premier et le deuxième compresseur est maintenue à une valeur de consigne par modification de la vitesse de rotation du deuxième compresseur.
  8. Installation frigorifique pour refroidir l'intérieur d'un conteneur frigorifique selon les revendications 1 à 3, dans laquelle la commande est configurée de telle sorte que, dans l'algorithme, le mode de fonctionnement NK est enregistré pour les petites valeurs de différence entre la température du dissipateur thermique et la température utile et le mode de fonctionnement TK pour les grandes valeurs de différence entre la température du dissipateur thermique et la température utile.
EP11722022.8A 2010-07-09 2011-05-28 Installation frigorifique pour refroidir un conteneur Active EP2590878B1 (fr)

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DE102010026648.5A DE102010026648B4 (de) 2010-07-09 2010-07-09 Kälteanlage zur Kühlung eines Containers
PCT/EP2011/002649 WO2012003906A2 (fr) 2010-07-09 2011-05-28 Installation frigorifique pour refroidir un conteneur

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Publication number Publication date
EP2590878A2 (fr) 2013-05-15
US20130104582A1 (en) 2013-05-02
US9945597B2 (en) 2018-04-17
DE102010026648B4 (de) 2015-12-31
WO2012003906A3 (fr) 2012-03-08
DE102010026648A1 (de) 2012-01-12
CN103038146A (zh) 2013-04-10
CN103038146B (zh) 2015-01-07
WO2012003906A2 (fr) 2012-01-12

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