EP4168723B1 - Dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration et procédé d'actionnement d'un dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration - Google Patents

Dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration et procédé d'actionnement d'un dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration Download PDF

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Publication number
EP4168723B1
EP4168723B1 EP21731989.6A EP21731989A EP4168723B1 EP 4168723 B1 EP4168723 B1 EP 4168723B1 EP 21731989 A EP21731989 A EP 21731989A EP 4168723 B1 EP4168723 B1 EP 4168723B1
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EP
European Patent Office
Prior art keywords
evaporator
pressure tube
low
tube section
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP21731989.6A
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German (de)
English (en)
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EP4168723A1 (fr
Inventor
Andreas BABUCKE
Niels Liengaard
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BSH Hausgeraete GmbH
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BSH Hausgeraete GmbH
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Publication of EP4168723A1 publication Critical patent/EP4168723A1/fr
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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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • 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
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • 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
    • F25B2700/2103—Temperatures near a heat exchanger
    • 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
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser

Definitions

  • the present invention relates to a refrigeration appliance, in particular a household refrigeration appliance, with a refrigerant circuit having a suction pipe heat exchanger, and a method for operating such a refrigeration appliance.
  • the object of the present invention is to provide a refrigeration device with two parallel evaporators or evaporator groups and a suction pipe heat exchanger as well as a method for operating such a refrigeration device, in which an estimate of the mass flow of the refrigerant through an evaporator or an evaporator group in relation to the total mass flow of the refrigerant can be obtained.
  • the object is achieved by a refrigeration device and a method for operating a refrigeration device according to the independent claims.
  • the invention relates to a refrigeration device with a refrigerant circuit which has a compressor, a first evaporator group with at least one first evaporator and with a high-pressure pipe connected upstream of the first evaporator group, a second evaporator group connected in parallel to the first evaporator group with at least one second evaporator, a low-pressure pipe connected downstream of the first evaporator group and the second evaporator group, and an intake manifold heat exchanger in which a high-pressure pipe section of the high-pressure pipe and a low-pressure pipe section of the low-pressure pipe are coupled in a heat-conducting manner.
  • the intake manifold heat exchanger has three temperature sensors at three positions from a group of positions at the inlet and outlet of the low-pressure pipe section, and at the inlet and outlet of the high-pressure pipe section.
  • Such a refrigeration appliance is in particular a household refrigeration appliance in which normal household quantities of food are stored in different compartments at different temperatures and may be subjected to temperature treatment. Storage compartments can be kept or operated at different temperatures using evaporators that operate at different temperatures.
  • the invention can be used advantageously with parallel-connected evaporators or evaporator groups, in which an evaporator group has evaporators with a variable selectable temperature.
  • a storage compartment that can be operated with a variable selectable temperature is referred to below as a flex compartment, and the associated evaporator is referred to as a flex compartment evaporator.
  • the invention can be used particularly advantageously with evaporators or evaporator groups connected in parallel, in which a first evaporator or the evaporators of a first evaporator group are operated at low temperatures and the second evaporator or the evaporators of the second evaporator group are optionally operated at a lower temperature than the ambient temperature or a higher temperature than the ambient temperature.
  • a flex compartment can be set to temperatures in a particularly wide temperature range.
  • the invention describes a refrigeration device with a refrigerant circuit with two parallel strands, each with at least one evaporator.
  • An important application is one in which there is only one evaporator in one or both strands.
  • the invention is described with regard to the first evaporator and the second evaporator in order to simplify the description. The person skilled in the art will recognize the generalization to the strands.
  • intake manifold and low-pressure pipe are used synonymously and the terms intake manifold heat exchanger and internal heat exchanger are also used synonymously.
  • the parallel evaporators typically have an adjustable throttle point each, in particular an expansion valve at the inlet and outlet of the evaporator.
  • an expansion valve is referred to as a representative of an adjustable throttle point.
  • the pressure in the evaporator can be influenced by the valve positions so that the corresponding compartment is cooled to different degrees.
  • the evaporator groups are seen as branches of the refrigerant circuit. It is advantageous to group the evaporators together in such a way that a first evaporator group only contains evaporators that operate storage compartments below the ambient temperature, and a second evaporator group only contains evaporators that operate storage compartments either below or above the ambient temperature.
  • Storage compartments of the first evaporator group are, for example, a cooling compartment, a cold storage compartment, a freezer compartment or a simple flex compartment. Since all of these compartments are cooled, it is advantageous that the refrigerant line of the first evaporator group is part of an internal heat exchanger or intake manifold heat exchanger.
  • a special feature of the refrigerant line to the second evaporator group is that it is not part of the internal heat exchanger in order to heat a flexible compartment with an extended temperature range by means of refrigerant condensing in the flexible compartment evaporator.
  • the advantage here is that the second evaporator can be supplied with warm or hot refrigerant at approximately the condenser temperature.
  • the distribution of the mass flow depends not only on the valve positions but also on the gas content or subcooling at the respective valve inlet. Gas content and subcooling are not accessible for the device control, so the exact distribution of the mass flows to the individual evaporators is difficult to determine.
  • the invention is based on the idea that a ratio of mass flows in an internal heat exchanger with two strands can be determined if the two mass flows are essentially single-phase and at least three temperatures at the inlets and outlets of the internal heat exchanger are known. If four If the temperatures at the inlets and outlets of the internal heat exchanger are known, the calculation is simplified.
  • a refrigerant line transfers heat to the intake manifold. Since different mass flows on the warm and cold sides result in different temperatures of the intake gas, this can be used to determine the mass flow portion flowing through the first evaporator, since this is essentially single-phase in the high-pressure pipe section.
  • the refrigerant in the intake manifold should be completely evaporated and thus be in single-phase gaseous form.
  • the temperature distribution on the intake manifold heat exchanger is therefore used as an internal heat exchanger to determine the mass flow rate through the first evaporator.
  • liquid refrigerant is present on the warm side and gaseous refrigerant with the respective specific heat capacities is present on the intake manifold side.
  • thermodynamics it is now possible to determine the ratio of the mass flows with good accuracy using three temperatures at the inlets and outlets of the intake manifold heat exchanger. See, for example, Fundamentals of Heat and Mass Transfer, lecture notes at the University of Magdeburg, WS2009/2010.
  • a third evaporator which follows the parallel evaporators and is passed through by the entire mass flow of the refrigerant, and whose suction pipe leads directly into the suction pipe heat exchanger, it is possible to use the temperature of the third evaporator as the temperature at the inlet of the suction pipe line or to replace a temperature sensor at the inlet of the suction pipe line with the temperature sensor in the third evaporator if no heat transfer takes place between the third evaporator and the suction pipe.
  • the suction gas density can be determined using the evaporation temperature in the third evaporator and the suction gas temperature at the outlet of the internal heat exchanger, and the conveying mass flow and thus the total mass flow can be determined using the speed of the compressor.
  • This method therefore also provides the absolute value of the mass flow flowing through the first evaporator line from the ratio of the mass flows and the total mass flow.
  • the mass flow through the second evaporator line is then determined from the difference to the total mass flow. In the case that the second
  • the mass flow through this evaporator is determined.
  • the high-pressure pipe section leads exclusively to the first evaporator group and does not lead to the second evaporator group. This has the advantage that the high-pressure pipe section has exactly the mass flow that flows through the first evaporator group.
  • the high-pressure pipe section follows the condenser, it essentially carries liquid refrigerant.
  • the mass flow through the high-pressure pipe section is therefore essentially a mass flow of liquid refrigerant with at most a very small proportion of gas.
  • a variably adjustable throttle element in particular an expansion valve, is connected upstream and downstream of the first evaporator and the second evaporator.
  • This provides the advantage that a mass flow can be set in the first evaporator and in the second evaporator independently of the other evaporator.
  • Each of these evaporators can be operated as an evaporator with a variable temperature. The pressure of the coolant and thus the evaporator temperature can be set for each of the evaporators independently of other evaporators.
  • the intake manifold heat exchanger has a temperature sensor at each position from a group of positions. This has the advantage that the calculation of the ratio of the mass flows is simplified.
  • the refrigeration device has a device for determining a ratio of the mass flows in the high-pressure pipe section and in the low-pressure pipe section.
  • a device for determining a ratio of the mass flows in the high-pressure pipe section and in the low-pressure pipe section can advantageously be integrated into the control of the refrigeration device.
  • the refrigeration device has a device for determining a ratio of the mass flows to the first evaporator group and the second evaporator group. This results from the fact that the Total mass flow is the sum of the mass flows to the first evaporator group and the second evaporator group.
  • the refrigeration device has a third evaporator between the parallel arranged first and second evaporators and the low-pressure pipe. This enables a further cooled compartment, preferably a compartment with a lower temperature than the previous compartments.
  • the refrigeration device has a further suction pipe heat exchanger in which a further high-pressure pipe section of the high-pressure pipe and a further low-pressure pipe section of the low-pressure pipe are coupled in a heat-conducting manner.
  • a further suction pipe heat exchanger in which a further high-pressure pipe section of the high-pressure pipe and a further low-pressure pipe section of the low-pressure pipe are coupled in a heat-conducting manner.
  • the third evaporator has a temperature sensor which replaces a temperature sensor at the inlet of the low-pressure pipe section, and the outlet of the third evaporator is connected directly to the inlet of the intake manifold heat exchanger.
  • the coolant temperature in the third evaporator and at the inlet of the intake manifold heat exchanger is the same. Therefore, the temperature sensor for the temperature at the inlet of the intake manifold of the heat exchanger can also be arranged in the third evaporator. This is particularly advantageous in a no-frost evaporator, which usually already has a temperature sensor for controlling the defrosting process.
  • the third evaporator is preferably assigned to a freezer compartment.
  • the refrigeration device has a fourth evaporator in the flow direction of the coolant immediately before the third evaporator. This enables an additional cooled compartment.
  • the fourth evaporator can advantageously be assigned to a refrigerator compartment or a cold storage compartment, which is supplied with gaseous refrigerant from the previous freezer compartment evaporator. This enables very good energy efficiency.
  • the compressor is a continuously running compressor with variable speed. This has the advantage that a constant temperature can be set in the evaporators, which avoids the usual temperature hysteresis in an intermittently operating compressor.
  • the evaporators of the first evaporator group do not necessarily have to be assigned to flexible compartments, but can also be assigned to compartments with a narrow target temperature range, for example a refrigerator compartment, a cold storage compartment or a freezer compartment.
  • thermodynamics can be used to determine the ratio of the refrigerant mass flows from the temperatures at the inlets and outlets. Another application of thermodynamics can be used to determine the ratio of the refrigerant mass flows from just three temperatures at the inlets and outlets.
  • One embodiment of the method includes the additional step of determining temperatures at all positions in the group of positions. If three temperatures are determined by sensors, the fourth temperature can either be determined from another sensor or can be well estimated by applying thermodynamics.
  • the ratio of the mass flow through the high-pressure pipe section to the mass flow through the low-pressure pipe section is determined with the aid of specific heat capacities of a refrigerant, assuming a liquid refrigerant in the high-pressure pipe section and a gaseous refrigerant in the low-pressure pipe section.
  • a further embodiment of the method includes the additional method step of determining a mass flow through the low-pressure pipe section from a delivery of the compressor.
  • the delivery mass flow is a function of the speed, the displacement, the volumetric efficiency and the suction gas density.
  • the suction gas density is a function of the evaporation temperature of the evaporator upstream of the intake manifold heat exchanger and the temperature at the gas outlet of the intake manifold heat exchanger.
  • the volumetric efficiency is a function of the condenser pressure and the evaporator pressure.
  • a further embodiment of the method includes the further method step of determining a mass flow through the second evaporator group from the ratio of the mass flow through the high-pressure pipe section to the mass flow through the low-pressure pipe section and the mass flow through the low-pressure pipe section.
  • the mass flows are therefore determined from the ratio of the mass flows and the conveying mass flow. This has the advantage that a mass flow that would otherwise be difficult to determine can be absolutely determined by the second evaporator group.
  • a further embodiment of the method includes the additional step of controlling the refrigeration device based on the determined temperatures. If the mass flow through the second evaporator group or the second evaporator is known, this knowledge can be used to better control the second evaporator group or the second evaporator.
  • a further embodiment of the method includes the additional method step of controlling the refrigeration device based on the ratio of the mass flow through the high-pressure pipe section to the mass flow through the low-pressure pipe section. This advantageously allows the refrigeration device to be controlled with improved energy efficiency.
  • Fig.1 shows a refrigerator representative of a refrigeration device 10 according to the invention with a refrigeration compartment door 12 to a refrigeration compartment 15, a flexible compartment door 13 to a flexible compartment 16 with an extended temperature range and a door 14 to a simple flexible compartment 17.
  • the refrigerator is used, for example, for storing food and comprises a refrigeration compartment, a flexible compartment with an extended temperature range and a simple flexible compartment as storage chambers. These storage chambers are each cooled by an associated evaporator.
  • the refrigeration device 10 also has a display and control unit 18 that controls the refrigeration device.
  • the display and control unit 18 has a device 19 for determining a ratio of mass flows.
  • the refrigeration device 10 has a refrigerant circuit that can be designed in different embodiments of the invention.
  • Fig.2 shows a refrigerant circuit 20 of a refrigeration device according to the invention.
  • the refrigerant circuit 20 has a compressor 22, a condenser 24, a first evaporator group 26 with a first evaporator 28 and a further evaporator 30 of the first evaporator group 26, and a second evaporator group 32 with a second evaporator 34 parallel to the first evaporator group 26.
  • the compressor is a speed-controlled compressor with variable speed.
  • the compressor is designed to operate continuously.
  • the first evaporator 28 and the further evaporator 30 of the first evaporator group 26 are arranged parallel to one another.
  • an expansion valve 36 is arranged, which controls the flow of coolant into the evaporator 28.
  • an expansion valve 38 is arranged, which controls the flow of coolant from the first evaporator 28.
  • Expansion valves 40 and 42 are also arranged in front of and behind the further evaporator 30 of the first evaporator group 26.
  • further evaporators of the first evaporator group could be arranged parallel to the first Evaporators can be arranged to provide separate evaporators for additional storage compartments.
  • the evaporators 28, 30 of the first evaporator group 26 are assigned to storage compartments that can be cooled to temperatures below the ambient temperature.
  • the first evaporator 28 is assigned to a cooling compartment
  • the further evaporator 30 of the first evaporator group 26 is assigned to a simple flex compartment with variable temperature, so that this compartment can be operated optionally as an additional cooling compartment, cold storage compartment or freezer compartment.
  • the variable temperatures of the evaporators of the first evaporator group 26 are made possible by the expansion valves in front of and behind the evaporators, which allow an evaporation pressure of the coolant in the evaporator to be set so that the desired temperatures are achieved independently of temperatures in other evaporators.
  • the second evaporator 34 In the second evaporator group 32, in the Fig.2 In the embodiment shown, there is only a single evaporator, the second evaporator 34. In the flow direction upstream of the second evaporator 34, an expansion valve 44 is arranged, which controls the refrigerant inflow into the evaporator 34. In the flow direction downstream of the second evaporator 34, an expansion valve 46 is arranged, which controls the refrigerant outflow from the second evaporator 34.
  • the second evaporator 34 of the second evaporator group 32 is assigned to a flex compartment with an extended temperature range that can be operated in a wide temperature range both below and above the ambient temperature.
  • the variable temperatures of the second evaporator 34 are made possible by the expansion valves in front of and behind the second evaporator 34, which allow an evaporation pressure of the refrigerant to be set so that the desired temperatures are achieved independently of temperatures in other evaporators.
  • Fig.2 The arrangement shown with the evaporators 28, 30 and 32 corresponds to an embodiment of the refrigeration device 10 from Fig.1 , whereby the evaporators 28, 30 and 32 are assigned to the storage compartments 15, 17 and 16.
  • the refrigerant circuit 20 has a line system with pipes which connect the described elements of the refrigerant circuit 20 to one another.
  • the refrigerant circuit 20 has a high-pressure area between the outlet of the compressor 22 and the expansion valves 36, 40 and 44.
  • the refrigerant circuit 20 has a low-pressure area between the valves 36, 40 and 46 and the inlet of the compressor 22.
  • the allocation of the line area between the expansion valve 44 upstream of the second evaporator 34 and the expansion valve 46 downstream of the second evaporator 34 to the high-pressure area or the low-pressure area depends on the respective operating state of the second evaporator 34 and the pressure prevailing therein. If the second evaporator 34 is operated at a temperature higher than the ambient temperature, it has the function of a condenser in this operating state and can be operated at high pressure.
  • the refrigerant circuit 20 has a high-pressure pipe 48, which is connected upstream of the evaporators of the first evaporator group.
  • the high-pressure pipe 48 ends at the throttles of the evaporators of the first evaporator group, i.e. here at the expansion valves 36 and 40.
  • the refrigerant circuit 20 has a low-pressure pipe 49 which is connected downstream of the first evaporator group 26 and the second evaporator group 32.
  • the low-pressure pipe 49 runs between the expansion valves 38, 42 and 46 and the inlet of the compressor 22.
  • the refrigerant circuit 20 further comprises a suction pipe heat exchanger 50 in which a high-pressure pipe section 52 of the high-pressure pipe 48 and a low-pressure pipe section 54 of the low-pressure pipe 49 are coupled in a heat-conducting manner.
  • the intake manifold heat exchanger 50 has four preferred positions for temperature sensors, namely position 56 at the inlet of the high pressure pipe section 52, position 58 at the outlet of the high pressure pipe section 52, position 60 at the inlet of the low pressure pipe section 54 and position 62 at the outlet of the low pressure pipe section 54. These positions for temperature sensors are preferred because, during operation of the refrigeration device in the heat exchanger 50, a maximum temperature difference of the refrigerant of the high-pressure pipe section 52 occurs due to the heat exchange between the positions 56 and 58 and a maximum temperature difference of the refrigerant of the low-pressure pipe section 54 occurs between the positions 60 and 62.
  • the refrigerant circuit 20 has a temperature sensor at each of the four positions 56, 58, 60 and 62.
  • This embodiment has the advantage that the temperature differences in the high-pressure pipe section 52 and in the low-pressure pipe section 54 can be determined by simple temperature measurements with the temperature sensors.
  • the display and control unit 16 of the refrigeration device 10 can use this to determine a ratio of the mass flows in the high-pressure section and the low-pressure section to one another.
  • the coolant circuit 20 has a temperature sensor at three positions from the group of positions 56, 58, 60 and 62.
  • This embodiment has the advantage that one less temperature sensor is required.
  • the temperature at the position of the missing temperature sensor can be determined using thermodynamic considerations. All four temperatures are then known again and the ratios of mass flows can be determined as in the previously described embodiment.
  • the evaporators of the first evaporator group 26, here the evaporators 28 and 30, are exclusively intended for compartments that are cooled, so that the evaporators 28 and 30 are also operated as evaporators.
  • the second evaporator group 32 with the single evaporator 34 is according to the invention for flexible compartments with an extended temperature range, such as the flexible compartment 16 from Fig.1 , provided.
  • the refrigerant is supplied to the second evaporator group 32 via a branch 64 of the high-pressure pipe 48 which is not involved in a suction pipe heat exchange. Therefore, the second evaporator group can receive refrigerant which has approximately the temperature of the condenser 24.
  • the improvement in energy efficiency made possible by the intake manifold heat exchange is exploited by additionally cooling the refrigerant supplied to the first evaporator group by the intake manifold heat exchange.
  • the condenser 24 has a fan 66.
  • the fan 66 has the task of preventing excessively high condenser temperatures and can cool the condenser 24 if no evaporator in the second evaporator group is operated in a heating mode to achieve a temperature above the ambient temperature in the evaporator or in its flex compartment with an extended temperature range.
  • the evaporators 28, 30 and 34 have fans 68, 70 and 72. These fans can be used to improve the heat transfer between the evaporator and the respective compartment or to control the humidity in the respective compartment.
  • further evaporators of the second evaporator group could be arranged parallel to the second evaporator in order to provide separate evaporators for further storage compartments, in particular flexible compartments with an extended temperature range.
  • the evaporators of these compartments are preferably arranged parallel to the second evaporator 34, also each with an expansion valve before and after each evaporator.
  • Fig.3 shows schematically the intake manifold heat exchanger 50, also called internal heat exchanger or intake manifold heat exchanger, from Fig.3 with the high pressure pipe section 52 of the high pressure pipe 48 and the low pressure pipe section 54 of the low pressure pipe 49.
  • the flow direction of the refrigerant is indicated by arrows 74 and 76.
  • the intake manifold heat exchanger 50 has four preferred positions for temperature sensors, namely on the outside of the pipe of the respective pipe section, position 56 at the inlet of the high-pressure pipe section 52, position 58 at the outlet of the high-pressure pipe section 52, position 60 at the inlet of the low-pressure pipe section 54 and position 62 at the outlet of the low-pressure pipe section 54.
  • a coordinate line 77 is given as an example, with end points 78 and 79 of a section over which a heat exchange takes place in the intake manifold heat exchanger 50. With the help of the coordinate line 77, a temperature profile within the intake manifold heat exchanger 50 can be determined using thermodynamics.
  • Fig.4 shows schematically a refrigerant circuit 80 of a refrigeration device of an embodiment of the invention in a configuration with a different arrangement of evaporators compared to the configuration in Fig.2 Therefore, the differences to the Fig.2 described.
  • the first evaporator group 26' has only the first evaporator 28 and the second evaporator group 32 has only the second evaporator 34.
  • the expansion valves already described are arranged before and after the evaporators 28, 34.
  • a suction pipe heat exchanger 50' is also arranged at the same location with respect to the first evaporator group.
  • the refrigerant circuit has a third evaporator 82 between the parallel arranged first and second evaporator groups 26', 32 and the low-pressure pipe 49'.
  • the third evaporator 82 follows the evaporators 28, 34 of the parallel evaporator groups 26', 32 in series.
  • the low pressure pipe 49' runs from the third evaporator 82 to the compressor 22.
  • a low pressure pipe section 54' of the low pressure pipe 49' is located in the intake manifold heat exchanger 50'.
  • the refrigerant circuit 80 has an optional additional internal heat exchanger 84 in which an additional pipe section 81 of the low-pressure pipe 49' and a refrigerant pipe section 83 at the outlet of the first evaporator 28 are coupled in a heat-conducting manner.
  • the additional internal heat exchanger 84 does not provide any information about a mass flow distribution, since the refrigerant is two-phase at the outlet of the evaporator 28. The suction gas then sees an isothermal heat source in the additional internal heat exchanger 84, so to speak.
  • the refrigerant circuit 80 is suitable for a refrigeration appliance 10 according to Fig.1
  • the evaporator 28 is again assigned to a cooling compartment 15, the evaporator 34 to a flexible compartment with an extended temperature range 16, and the evaporator 82 to a simple flexible compartment, which can be operated, for example, as a cold storage compartment or as a freezer compartment.
  • the evaporator 82 has a fan 85.
  • the refrigerant circuit 80 advantageously uses the low suction pressure of the compressor 22 for a serially arranged evaporator 82, which is assigned to a particularly cold compartment.
  • the evaporator 82 is associated with a cold compartment, preferably a freezer compartment, and has a temperature sensor 86.
  • the refrigerant circuit 80 has the following advantage. At the location of the temperature sensor 86, the temperature and pressure are known for the entire refrigerant mass flow, and from this the suction gas density there can be determined using a temperature sensor at the end of the low-pressure pipe section, position 62'. This in turn can be used to determine the absolute total mass flow using the compressor speed via the compressor delivery.
  • An embodiment of the invention without the further internal heat exchanger 84 also makes it possible to use a temperature sensor at the inlet of the Low pressure pipe section 54' at position 60' the temperature sensor 86 is used to determine the temperature at the inlet of the low pressure pipe section 54'.
  • Fig.5 shows a refrigerant circuit in a further embodiment based on the Fig.4 shown embodiment.
  • a fourth evaporator 88 has now been added downstream of the third evaporator 82' in a serial arrangement.
  • the third evaporator 82' has a temperature sensor 86'.
  • the third evaporator 82' has a fan 85' and the fourth evaporator 88 has a fan 90.
  • the evaporator 86' is operated as a freezer compartment evaporator to supply a freezer compartment and the additional evaporator 88 is operated as an evaporator for a cold storage compartment or a refrigerator compartment.
  • the control of the refrigeration device with this refrigerant circuit is carried out in such a way that the refrigerant supplied to the evaporator 86' essentially evaporates in the evaporator 86' and the following evaporator 88 is cooled by cold gaseous refrigerant.
  • the temperature sensor 86' is in turn in the coldest compartment, so the temperature and evaporation pressure can be determined at its position based on the temperature prevailing there, and with this information the suction gas density there can be determined using a temperature sensor at the end of the low-pressure pipe section, position 62'. This in turn can be used to determine the absolute total mass flow using the compressor speed via the compressor delivery.
  • Fig.6 shows a flow chart 100 of an embodiment of the method according to the invention for determining a ratio of mass flows in a refrigeration device.
  • the refrigeration device for example the refrigeration device ten from Fig.1 , has a refrigerant circuit, for example the refrigerant circuit 20 from Fig.2 or the refrigerant circuit 80 from Fig.4 , the refrigerant circuit 20, 80 has a compressor 22, a first evaporator group 26, 26' with at least one first evaporator 28 and with a high-pressure pipe 48 connected upstream of the first evaporator group 26, 26', a second evaporator group 32 connected in parallel to the first evaporator group 26, 26' with at least one second evaporator 34, a first evaporator group 26, 26' and a low-pressure pipe 49, 49' downstream of the second evaporator group 32, and a suction pipe heat exchanger 50, 50' in which a high-pressure pipe section 52, 52' of the high-pressure pipe 48 and a low
  • the suction pipe heat exchanger has a group of positions 60, 60'; 62, 62'; 56, 56'; 58, 58' at the inlet and outlet of the low-pressure pipe section, and at the inlet and outlet of the high-pressure pipe section.
  • the determination of a temperature at one of the positions on the intake manifold heat exchanger is usually carried out by a temperature sensor at the position on the intake manifold heat exchanger.
  • the temperature can also be determined using a temperature sensor at a neighboring position on the intake manifold outside the intake manifold heat exchanger in the refrigerant circuit if no heat transfer from or to the intake manifold takes place between the two positions. In this case, it is justified to assume that the same temperature prevails at both positions.
  • d) Determining 114 a mass flow through the second evaporator group from the ratio of the mass flow through the high-pressure pipe section to the mass flow through the low-pressure pipe section.
  • the entire mass flow of the refrigerant required by the compressor 22 flows through the low-pressure pipe section 52 of the intake manifold heat exchanger 50. The entire mass flow can then be determined from the delivery of the compressor 22.
  • e' Controlling 118 the refrigeration device 10 based on the ratio of the mass flow through the high-pressure pipe section to the mass flow through the low-pressure pipe section.
  • the ratio of the mass flow through the high-pressure section to the mass flow through the low-pressure section is determined using the temperatures from method step a).

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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 (14)

  1. Appareil frigorifique (10) comprenant un circuit de réfrigérant (20, 80, 90), qui présente un compresseur (22), un premier ensemble évaporateur (26) comportant au moins un premier évaporateur (28) et une tubulure à haute pression (48) raccordée en amont du premier ensemble évaporateur (26), un deuxième ensemble évaporateur (32) connecté en parallèle avec le premier ensemble évaporateur (26) comportant au moins un deuxième évaporateur (34), une tubulure à basse pression (49, 49') raccordée en aval du premier ensemble évaporateur (26) et du deuxième ensemble évaporateur (32) et un échangeur de chaleur à tube d'aspiration (50, 50'), dans lequel une section tubulaire à haute pression (52, 52') de la tubulure à haute pression (48) et une section tubulaire à basse pression (54, 54') de la tubulure à basse pression (49, 49') sont couplées de façon thermoconductrice,
    caractérisé en ce que l'échangeur de chaleur à tube d'aspiration (50, 50') présente trois capteurs de température à trois positions d'un groupe de positions (60, 60', 62, 62', 56, 56', 58, 58') au niveau de l'entrée et de la sortie de la section tubulaire à basse pression (54, 54') et au niveau de l'entrée et de la sortie de la section tubulaire à haute pression (52, 52').
  2. Appareil frigorifique selon la revendication 1, caractérisé en ce que la section tubulaire à haute pression (52, 52') conduit exclusivement au premier ensemble évaporateur (26, 26') et ne conduit pas au deuxième ensemble évaporateur (32).
  3. Appareil frigorifique selon la revendication 1 ou 2, caractérisé en ce qu'un élément d'étranglement réglable de façon variable, en particulier une soupape de détente (36, 38, 44, 46) est connecté respectivement en amont et en aval du premier évaporateur (28) et du deuxième évaporateur (34).
  4. Appareil frigorifique selon la revendication 1, 2 ou 3, caractérisé en ce que l'échangeur de chaleur à tube d'aspiration (50, 50') présente un capteur de température à chaque position d'un groupe de positions (60, 60', 62, 62', 56, 56', 58, 58').
  5. Appareil frigorifique selon l'une des revendications précédentes, caractérisé en ce que l'appareil frigorifique présente un moyen pour déterminer un rapport des débits massiques dans la section tubulaire à haute pression (52, 52') et dans la section tubulaire à basse pression (54, 54').
  6. Appareil frigorifique selon la revendication 5, caractérisé en ce que l'appareil frigorifique présente un moyen (19) pour déterminer un rapport des débits massiques vers le premier ensemble évaporateur (26) et le deuxième ensemble évaporateur (32).
  7. Appareil frigorifique selon l'une quelconque des revendications précédentes, caractérisé en ce que l'appareil frigorifique (10) présente un troisième évaporateur (82, 82') entre les premier et deuxième évaporateurs (28, 28', 34) connectés en parallèle et la tubulure à basse pression (49, 49').
  8. Appareil frigorifique selon la revendication 7, caractérisé en ce que l'appareil frigorifique présente un échangeur de chaleur à tube d'aspiration supplémentaire, dans lequel une section tubulaire de réfrigérant (83) à la sortie du premier évaporateur (28) et une section tubulaire supplémentaire (81) de la tubulure à basse pression (49, 49') sont couplées de manière thermoconductrice, ou le troisième évaporateur (82) présente un capteur de température (86) qui remplace un capteur de température à l'entrée de la section tubulaire à basse pression (54, 54').
  9. Procédé de détermination d'un rapport de débits massiques dans un appareil frigorifique comprenant un circuit de réfrigérant, qui présente un compresseur, un premier ensemble évaporateur (26) comportant au moins un premier évaporateur et une tubulure à haute pression (48) raccordée en amont du premier ensemble évaporateur (26), un deuxième ensemble évaporateur (32) connecté en parallèle avec le premier ensemble évaporateur (26) et comportant au moins un deuxième évaporateur, une tubulure à basse pression (49, 49') raccordée en aval du premier ensemble évaporateur (26) et du deuxième ensemble évaporateur et un échangeur de chaleur à tube d'aspiration (50, 50'), dans lequel une section tubulaire à haute pression (52, 52') de la tubulure à haute pression (48) et une section tubulaire à basse pression (54, 54') de la tubulure à basse pression (49, 49') sont couplées de façon thermoconductrice,
    dans lequel l'échangeur de chaleur à tube d'aspiration (50, 50') présente un groupe de positions (60, 60', 62, 62', 56, 56', 58, 58') au niveau de l'entrée et de la sortie de la section tubulaire à basse pression (54, 54') et au niveau de l'entrée et de la sortie de la section tubulaire à haute pression (52, 52'), le procédé comprenant les étapes :
    a) détermination (102) de températures à trois positions du groupe de positions,
    b) détermination (104) d'un rapport d'un débit massique à travers la section tubulaire à haute pression (52, 52') à un débit massique à travers la section tubulaire à basse pression (54, 54') en se servant des températures déterminées.
  10. Procédé selon la revendication 9, caractérisé par l'étape supplémentaire :
    a') détermination (102) des températures à toutes les positions du groupe de positions (60, 60', 62, 62', 56, 56', 58, 58').
  11. Procédé selon la revendication 9 ou 10, caractérisé en ce que la détermination du rapport du débit massique à travers la section tubulaire à haute pression (52, 52') au débit massique à travers la section tubulaire à basse pression (54, 54') est effectuée à l'aide des capacités thermiques spécifiques d'un réfrigérant dans l'hypothèse d'un réfrigérant liquide dans la section tubulaire à haute pression (52, 52') et d'un réfrigérant gazeux dans la section tubulaire à basse pression (54, 54').
  12. Procédé selon l'une des revendications 9 à 11, caractérisé par l'étape supplémentaire :
    c) détermination d'un débit massique (112) à travers la section tubulaire à basse pression (54, 54') à partir d'un refoulement du compresseur (22).
  13. Procédé selon l'une des revendications 9 à 12, caractérisé par l'étape supplémentaire :
    d) détermination (114) d'un débit massique à travers le deuxième ensemble évaporateur (32) à partir du rapport du débit massique à travers la section tubulaire à haute pression (52, 52') au débit massique à travers la section tubulaire à basse pression (54, 54').
  14. Procédé selon l'une des revendications 9 à 13, caractérisé par l'étape supplémentaire :
    e') commande de l'appareil frigorifique (10) en fonction du rapport du débit massique à travers la section tubulaire à haute pression (52, 52') au débit massique à travers la section tubulaire à basse pression (54, 54').
EP21731989.6A 2020-06-22 2021-06-08 Dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration et procédé d'actionnement d'un dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration Active EP4168723B1 (fr)

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DE102020207648.0A DE102020207648A1 (de) 2020-06-22 2020-06-22 Kältegerät mit einem Saugrohr-Wärmetauscher und Verfahren zum Betrieb eines Kältegeräts mit einem Saugrohr-Wärmetauscher
PCT/EP2021/065288 WO2021259630A1 (fr) 2020-06-22 2021-06-08 Dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration et procédé d'actionnement d'un dispositif de refroidissement doté d'un échangeur de chaleur à tube d'aspiration

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JP2008232569A (ja) * 2007-03-22 2008-10-02 Daikin Ind Ltd 冷凍装置
CN103958986B (zh) * 2011-11-29 2016-08-31 三菱电机株式会社 冷冻空调装置
DE102012218345A1 (de) * 2012-10-09 2014-04-10 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit zwei Verdampfern
DE102012220526B3 (de) * 2012-10-18 2014-01-23 Eberspächer Climate Control Systems GmbH & Co. KG Verfahren zur Flammabbrucherkennung bei einem brennstoffbetriebenen Heizgerät, insbesondere Fahrzeugheizgerät
DE102013113221B4 (de) * 2013-11-29 2024-05-29 Denso Automotive Deutschland Gmbh Innerer Wärmetauscher mit variablem Wärmeübergang
CN108139120B (zh) * 2015-10-21 2020-04-17 三菱电机株式会社 空调装置
DE102016202565A1 (de) 2016-02-19 2017-08-24 BSH Hausgeräte GmbH Kältegerät mit mehreren Lagerkammern
DE102016202564A1 (de) * 2016-02-19 2017-08-24 BSH Hausgeräte GmbH Kältegerät mit mehreren Lagerkammern
CH715229A1 (de) * 2018-08-02 2020-02-14 V Zug Ag Kühlgerät mit mehreren Temperaturzonen.

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EP4168723A1 (fr) 2023-04-26
US20230296293A1 (en) 2023-09-21
DE102020207648A1 (de) 2021-12-23
CN115917224A (zh) 2023-04-04
CN115917224B (zh) 2026-03-03
WO2021259630A1 (fr) 2021-12-30

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