WO2021259630A1 - 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
WO2021259630A1
WO2021259630A1 PCT/EP2021/065288 EP2021065288W WO2021259630A1 WO 2021259630 A1 WO2021259630 A1 WO 2021259630A1 EP 2021065288 W EP2021065288 W EP 2021065288W WO 2021259630 A1 WO2021259630 A1 WO 2021259630A1
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WO
WIPO (PCT)
Prior art keywords
evaporator
pressure pipe
pipe section
group
low
Prior art date
Application number
PCT/EP2021/065288
Other languages
German (de)
English (en)
Inventor
Andreas BABUCKE
Niels Liengaard
Original Assignee
BSH Hausgeräte GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by BSH Hausgeräte GmbH filed Critical BSH Hausgeräte GmbH
Priority to US18/011,600 priority Critical patent/US20230296293A1/en
Priority to EP21731989.6A priority patent/EP4168723B1/fr
Priority to CN202180044025.XA priority patent/CN115917224A/zh
Publication of WO2021259630A1 publication Critical patent/WO2021259630A1/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—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
    • F25B2400/05—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 invention relates to a refrigeration device with a refrigerant circuit that has a compressor, a first evaporator group with at least one first evaporator and 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, one of the first evaporator group and the second evaporator group downstream low-pressure pipe, and a suction pipe 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 thermally conductive manner.
  • the intake manifold heat exchanger has three temperature sensors at three positions from a group of positions at the inlet and at the outlet of the low-pressure pipe section, and at the inlet and at the outlet of the high-pressure pipe section.
  • a refrigeration device is in particular a household refrigeration device in which normal household quantities of food are stored in different compartments at different temperatures and possibly undergo a temperature treatment. With evaporators that are operated at different temperatures, storage compartments can be kept or operated at different temperatures.
  • 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 is operated at low temperatures and the second evaporator or the evaporators of the second evaporator group optionally at a temperature lower than the ambient temperature or at 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 lines, each with at least one evaporator.
  • An important application is that in which there is only one evaporator in one or in both branches.
  • the invention is described for the purpose of simplifying the description with regard to the first evaporator and the second evaporator. Those skilled in the art will recognize the generalization to the strands.
  • suction pipe and low-pressure pipe are used synonymously and the terms suction pipe heat exchanger and internal heat exchanger are also used synonymously.
  • the parallel evaporators typically each have a controllable throttle point, in particular an expansion valve at the inlet and outlet of the evaporator.
  • an expansion valve is mentioned as a representative of a controllable throttle point.
  • the pressure in the evaporator can be influenced by the valve positions in such a way that the associated compartment is cooled to different degrees.
  • the evaporator groups are viewed as strands of the refrigerant circuit. It is advantageous to group the evaporators in such a way that in a first evaporator group there are only evaporators that operate storage compartments below ambient temperature, and in a second evaporator group there are only evaporators that operate storage compartments either below or above ambient temperature.
  • 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 also by 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.
  • the gas content and subcooling are not accessible for the device control, so that 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 are known at the inputs and outputs of the internal heat exchanger. If four Temperatures at the inlets and outlets of the internal heat exchanger are known, the calculation is simplified.
  • a third evaporator which follows the parallel evaporators and is traversed by the entire mass flow of the refrigerant, and whose suction pipe leads directly into the suction pipe heat exchanger, it is possible to set the temperature of the third evaporator as the temperature at the inlet of the suction pipe branch use or replace a temperature sensor at the inlet of the intake manifold with the temperature sensor in the third evaporator if there is no heat transfer between the third evaporator and the intake manifold.
  • the evaporation temperature in the third evaporator and the suction gas temperature at the outlet of the internal heat exchanger can be used to determine the suction gas density and, with the speed of the compressor, the conveyed mass flow and thus the total mass flow.
  • This method thus also provides the absolute value of the mass flow flowing through the first evaporator branch from the ratio of the mass flows and the total mass flow.
  • the mass flow through the second evaporator branch then results from the difference to the total mass flow. In the event that the second If the evaporator branch has only one evaporator, the mass flow through this evaporator is thus determined.
  • 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 in 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 first and second evaporators arranged in parallel 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 thermally conductive manner.
  • This increases the energy efficiency. It should be noted, however, that the additional intake pipe heat exchanger cannot be used for mass flow determinations if there are no essentially single-phase flows.
  • 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 directly connected to the inlet of the intake pipe heat exchanger.
  • the refrigerant temperature in the third evaporator and at the inlet of the intake manifold heat exchanger is the same.
  • the temperature sensor for the temperature at the inlet of the intake manifold of the heat exchanger can therefore also be arranged in the third evaporator. This is particularly advantageous in the case of 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 refrigerant directly upstream of the third evaporator.
  • the fourth evaporator can advantageously be assigned to a cooling compartment or a cold storage compartment which is supplied by gaseous refrigerant from the preceding freezer compartment evaporator. This enables very good energy efficiency.
  • the compressor is a permanently running compressor with a 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 cooling compartment, a cold storage compartment or a freezer compartment.
  • the invention also relates to a method for determining a ratio of mass flows in a refrigeration device with a refrigerant circuit which has a compressor, a first evaporator group with at least one first evaporator and 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 a second evaporator, a low-pressure pipe downstream of the first evaporator group and the second evaporator group, and a suction pipe 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 thermally coupled.
  • the intake pipe heat exchanger has 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, and the method is carried out with the method steps a) determining temperatures at three positions from the group of positions; b) Determination of a ratio of a mass flow through the high pressure pipe section to a mass flow through the low pressure pipe section using the determined temperatures.
  • thermodynamics can be used to determine the ratio of the refrigerant mass flows from the temperatures at the inputs and outputs.
  • Another application of thermodynamics can be used to determine the ratio of the refrigerant mass flows from just three temperatures at the inputs and outputs.
  • One embodiment of the method contains the further method step of determining temperatures at all positions from the group of positions.
  • the fourth temperature can either be determined from a further sensor or be well estimated using thermodynamics.
  • Another embodiment of the method includes the further method step of determining a mass flow through the low-pressure pipe section from a delivery of the compressor.
  • the flow rate is a function of the speed, the stroke volume, the degree of delivery and the suction gas density.
  • the suction gas density is a function of the evaporation temperature of the evaporator upstream of the suction tube heat exchanger and the temperature at the gas outlet of the suction tube heat exchanger.
  • the degree of delivery is a function of the condenser pressure and the evaporator pressure.
  • Another 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 determined from the ratio of the mass flows and the conveyed mass flow. This has the advantage that an otherwise difficult to determine mass flow through the second evaporator group can be absolutely determined.
  • Another embodiment of the method contains the further method step of controlling the refrigeration device on the basis of 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.
  • Another embodiment of the method contains the further 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.
  • the refrigeration device can thus advantageously be controlled with improved energy efficiency.
  • FIG. 1 shows a schematic representation of a refrigeration device according to the invention
  • FIG. 2 shows a schematic representation of the refrigerant circuit of a refrigeration device according to the invention with parallel evaporator branches;
  • FIG. 4 shows a schematic representation of the refrigerant circuit of a refrigeration device according to the invention with parallel evaporator branches and an evaporator following in series;
  • FIG. 5 shows a schematic representation of the refrigerant circuit of a refrigeration device according to the invention with parallel evaporator branches and a further evaporator following in series;
  • FIG. 6 shows a flow diagram of an embodiment of the method according to the invention.
  • Fig. 1 shows a refrigerator representative of a refrigeration device 10 according to the invention with a cooling compartment door 12 to a cooling 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 cooling 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 which 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 which can be configured in different configurations 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 parallel to the first evaporator group 26 with a second evaporator 34.
  • the compressor is a variable speed speed controlled compressor.
  • the compressor is designed to work 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 which controls the flow of refrigerant into the evaporator 28, is arranged upstream of the first evaporator 28 in the direction of flow.
  • An expansion valve 38 which controls the refrigerant outflow from the first evaporator 28, is arranged downstream of the first evaporator 28 in the direction of flow.
  • Expansion valves 40 and 42 are also arranged upstream and downstream of the further evaporator 30 of the first evaporator group 26.
  • further evaporators of the first evaporator group could be parallel to the first Evaporator can be arranged in order to provide its own evaporator for further storage compartments.
  • the evaporators 28, 30 of the first evaporator group 26 are assigned to storage compartments which can be cooled to temperatures below the ambient temperature.
  • the first evaporator 28 is assigned to a refrigerated compartment
  • the further evaporator 30 of the first evaporator group 26 is assigned to a simple flexible compartment with a variable temperature, so that this compartment can optionally be operated as a further refrigerated 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 upstream and downstream of the evaporators, which allow an evaporation pressure of the refrigerant 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 embodiment shown in FIG. 2, only a single evaporator, the second evaporator 34, is present in the second evaporator group 32.
  • An expansion valve 44 which controls the flow of refrigerant into the evaporator 34, is arranged upstream of the second evaporator 34 in the flow direction.
  • An expansion valve 46 which controls the refrigerant outflow from the second evaporator 34, is arranged downstream of the second evaporator 34 in the direction of flow.
  • the second evaporator 34 of the second evaporator group 32 is assigned to a flexible 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 upstream and downstream of 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.
  • the arrangement shown in FIG. 2 with the evaporators 28, 30 and 32 corresponds to an embodiment of the refrigeration device 10 from FIG. 1, the evaporators 28, 30 and 32 being assigned to the storage compartments 15, 17 and 16.
  • the refrigerant circuit 20 has a line system with pipelines which connect the described elements of the refrigeration circuit 20 to one another.
  • the refrigerant circuit 20 has a high pressure region between the outlet of the compressor 22 and the expansion valves 36, 40 and 44.
  • the refrigerant circuit 20 has a low pressure region between the valves 36, 40 and 46 and the input of the compressor 22.
  • the assignment 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, then in this operating state it has the function of a condenser 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 also has an intake 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 thermally conductive manner.
  • the intake pipe heat exchanger 50 has four preferred positions for temperature sensors, namely position 56 at the inlet of high pressure pipe section 52, position 58 at the outlet of high pressure pipe section 52, position 60 at the inlet of low pressure pipe section 54 and position 62 at the outlet of low pressure pipe section 54. These positions for temperature sensors are preferred because during operation of the refrigeration device in the heat exchanger 50, due to the heat exchange between positions 56 and 58, a maximum temperature difference of the refrigerant of the high-pressure pipe section 52 occurs 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 ratio of the mass flow through the evaporator 34 to the total mass flow can thus be calculated.
  • the refrigerant 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 by considerations from thermodynamics. All four temperatures are then known again and the ratios of mass flows can be determined as in the embodiment described above.
  • the evaporators of the first evaporator group 26, here the evaporators 28 and 30, are provided exclusively 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 provided for flexible compartments with an extended temperature range, such as the flexible compartment 16 from FIG. 1. Since the Evaporator of the second evaporator group 32 can be operated not only as an evaporator but also as a condenser, the refrigerant is fed to the second evaporator group 32 via a branch 64 of the high-pressure pipe 48 which is not involved in an intake pipe heat exchange. Therefore, the second evaporator group can receive refrigerant which is approximately the same as the temperature of the condenser 24.
  • the improvement in energy efficiency made possible by the intake pipe heat exchange is utilized in that the refrigerant which is supplied to the first evaporator group is additionally cooled by the intake pipe heat exchange.
  • the condenser 24 has a fan 66.
  • the fan 66 has the task of avoiding excessively high condenser temperatures and it 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 will.
  • the evaporators 28, 30 and 34 have fans 68, 70 and 72. These fans can be used both 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, each with an expansion valve in front of and an expansion valve after each evaporator.
  • Fig. 3 shows schematically the intake pipe heat exchanger 50, also called the inner heat exchanger or intake pipe 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 direction of flow of the refrigerant is indicated by arrows 74 and 76 .
  • the intake pipe 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 high pressure pipe section 52, position 58 at the outlet of high pressure pipe section 52, position 60 at the inlet of low pressure pipe section 54 and position 62 at the outlet of the low-pressure pipe section 54.
  • a coordinate line 77 is given by way of example, with end points 78 and 79 of a route over which a heat exchanger takes place in the intake manifold heat exchanger 50. With the aid of the coordinate line 77, a temperature profile within the intake manifold heat exchanger 50 can be determined with the aid of thermodynamics.
  • FIG. 4 schematically shows a refrigerant circuit 80 of a refrigeration device of an embodiment of the invention in an embodiment with a different arrangement of evaporators compared to the embodiment in FIG. 2. Therefore, the differences from FIG. 2 are essentially described.
  • the first evaporator group 26 ′ only has the first evaporator 28 and the second evaporator group 32 only has the second evaporator 34.
  • the expansion valves already described are again arranged upstream and downstream of the evaporators 28, 34.
  • an intake pipe heat exchanger 50 ' is arranged at the same point with respect to the first evaporator group.
  • the refrigerant circuit has a third evaporator 82 between the first and second evaporator groups 26 ', 32 arranged in parallel 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.
  • the refrigerant circuit 80 has an optional further internal heat exchanger 84 in which a further pipe section 81 of the low-pressure pipe 49 ′ and a refrigerant pipe section 83 are coupled in a thermally conductive manner at the outlet of the first evaporator 28.
  • the further internal heat exchanger 84 does not provide any information about a mass flow distribution that the refrigerant is two-phase at the outlet of the evaporator 28.
  • the suction gas then sees an isothermal heat source, so to speak, in the further inner heat exchanger 84.
  • the refrigerant circuit 80 is suitable for a refrigeration device 10 according to FIG. 1.
  • the evaporator 28 is in turn a cooling compartment 15
  • the evaporator 34 is a flexible compartment with an extended temperature range 16
  • the evaporator 82 is a simple flexible compartment, which can be used, for example, as a cold storage compartment or can be operated 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 to which a particularly cold compartment is assigned.
  • the evaporator 82 is assigned to 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, temperature and pressure are known for the entire refrigerant mass flow, and from this the suction gas density there can be determined with a temperature sensor at the end of the low-pressure pipe section, position 62 '. This in turn enables the absolute total mass flow to be determined with the aid of the compressor speed via the delivery of the compressor.
  • the entire mass flow of refrigerant required by the compressor 22 flows through the low-pressure pipe section 52 of the intake pipe heat exchanger 50. The total mass flow can then be determined from the delivery of the compressor 22.

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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)

Abstract

La présente invention concerne un dispositif de refroidissement (10) doté d'un circuit de refroidissement (20, 80, 90) comprenant un compresseur (22), un premier ensemble évaporateur (26) comprenant au moins un premier évaporateur (28) et ayant un tube à haute pression (48) raccordé en amont du premier ensemble évaporateur (26), un second ensemble évaporateur (32) raccordé en parallèle au premier ensemble évaporateur (26) et au moins un deuxième évaporateur (34), un tube à basse pression (49, 49') raccordé en aval du premier ensemble évaporateur (26) et du second ensemble évaporateur (32), et un échangeur de chaleur à tube d'aspiration (50, 50') dans lequel une section tube à haute pression (52, 52') du tube à haute pression (48) et une section tube à basse pression (54, 54') du tube à basse pression (49, 49') sont accouplées de manière thermoconductrice. L'échangeur de chaleur à tube d'aspiration (50, 50') comporte trois capteurs de température en trois positions à partir 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 tube à basse pression (54, 54'), et au niveau de l'entrée et de la sortie de la section tube à haute pression (52, 52'). Le dispositif de refroidissement et le procédé associé permettent de déterminer un rapport entre le débit massique de liquide de refroidissement vers le premier ensemble évaporateur et le débit massique total du liquide de refroidissement.
PCT/EP2021/065288 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 WO2021259630A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US18/011,600 US20230296293A1 (en) 2020-06-22 2021-06-08 Cooling device with a suction tube heat exchanger and method for operating a cooling device with a suction tube heat exchanger
EP21731989.6A EP4168723B1 (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
CN202180044025.XA CN115917224A (zh) 2020-06-22 2021-06-08 具有吸入管热交换器的制冷器具和用于运行具有吸入管热交换器的制冷器具的方法

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
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
DE102020207648.0 2020-06-22

Publications (1)

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WO2021259630A1 true WO2021259630A1 (fr) 2021-12-30

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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

Country Status (5)

Country Link
US (1) US20230296293A1 (fr)
EP (1) EP4168723B1 (fr)
CN (1) CN115917224A (fr)
DE (1) DE102020207648A1 (fr)
WO (1) WO2021259630A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012218345A1 (de) * 2012-10-09 2014-04-10 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit zwei Verdampfern
DE102016202565A1 (de) 2016-02-19 2017-08-24 BSH Hausgeräte GmbH Kältegerät mit mehreren Lagerkammern
EP3604988A1 (fr) * 2018-08-02 2020-02-05 V-Zug AG Appareil de réfrigération avec une pluralité de zones de température

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012218345A1 (de) * 2012-10-09 2014-04-10 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit zwei Verdampfern
DE102016202565A1 (de) 2016-02-19 2017-08-24 BSH Hausgeräte GmbH Kältegerät mit mehreren Lagerkammern
EP3604988A1 (fr) * 2018-08-02 2020-02-05 V-Zug AG Appareil de réfrigération avec une pluralité de zones de température

Also Published As

Publication number Publication date
EP4168723A1 (fr) 2023-04-26
US20230296293A1 (en) 2023-09-21
DE102020207648A1 (de) 2021-12-23
CN115917224A (zh) 2023-04-04
EP4168723B1 (fr) 2024-05-01

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